DE19634991A1 - Vibratory compacting system in concrete-block-making machine - Google Patents

Abstract

The table (140) is supported via springs (210,218) from the machine frame (102) or foundation. It is actuated by motor-driven rotary eccentric weights (144,144'), and forms a first mass, against which a second one, incorporating a baseplate (120), a mould box (124) and a ballast body (128,130), acts. During the upstroke of the first mass an impulse is imparted to it by the second one. In the rest position, the latter bears against impact ribs (104) on the machine frame or foundation. The value of the impulse transmitted is adjusted by an actuator (202), dependent on the resultant spring constant of all springs involved, the movement of the springs between the table and frame, the pre-loading force of all supporting springs involved, the additional force accelerating or retarding the first mass, and the speed of rotation. The resultant centrifugal force is set to a maximum value necessary to allow adjustment of the impact intensity at the top part of the adjustment range.

Description

The invention relates generally to compaction systems of stone molding machines that equipped with at least one motion generation system working with rotating unbalances are, from whose oscillating movements shock processes are derived, with which ultimately the actual one Compaction work is done. The motion generation systems used have one Combination of the following features:

• - A vibrating table with the mass m _s is supported by springs with the resulting spring constant C _RT against the foundation of the compression system or against organs to be equated with it.
• - The resiliently supported oscillating table is connected to at least one pair of imbalance bodies rotating in opposite directions and synchronously with an angle of rotation Kreis and with the angular frequency ω and producing a directed unbalance force F _u = f (ϕ) with the maximum value F _{u, m} . The unbalance forces are dependent in a known manner on the product M _{R *} ω², with M _R as the physical quantity of the resulting centrifugal moment (also called a static moment). The directional oscillatory movements of the mass m _s that can be generated by the alternating forces F _u = f (ϕ) have the “nominal” amplitude A _s , which is defined by the relationship A _s = M _R / m _s .
• - The vibrating table, whose mass m _{s is} regarded as an impacting mass, has special abutment surfaces with which, together with the abutment surfaces of the mass system to be butted, joints are formed at which the impacts derived from the oscillating movement of the oscillating table take place with it definable impact speed Δv as the speed difference of both impact surfaces.
• - The unbalance bodies are driven by a motor-generated drive torque, with the help of this among other things, the impact work given to the outside through the shocks is transferred.
• - The mass m _a pushed by the impacting mass m _s is the mass of a mass system composed of several partial masses of different organs. As a rule, the part masses of the molded box, the load ram (with connected organs), the molded material (concrete) and - if available - the base plate arranged under the molded box are to be counted as part of the pushed mass m _a .

In the genus of compression systems to which the invention relates, the previously defined is intended Movement generation system together with other structural features of the compression system be able to use the two shock processes defined below, either alone or in a mixed manner carry out:

• - With the "bumper strip method" _, two different impact points with their associated different impact speeds Δv can be defined for the impacted mass m _a : At one impact point, the downward-moving mass m _a (e.g. with the underside of the assigned base plate) encounters an impact speed Δv₂ against bumpers, which are supported directly and with a rigid construction against the foundation. At the other point of impact there is an impact with the impact speed Δv 1 between the mass m _a and the upwardly oscillating mass m _{s of} the vibrating table, which initially lingers on the baffle bars at a corresponding height. During the oscillation period of the oscillating table with the oscillation angle ϕ = 2 _* π, both shocks (normally) occur once.
• - In the "counter-impact method" there is only one impact point for the formation of impact processes, with the mass m _{s of} the vibrating table colliding with the mass m _a of the impacted mass system during its upward movement with the impact speed Δv₃ once per oscillation period.

In order to operate the two defined shock processes in a more effective manner, u. a. two here in particular special processes worth mentioning are used:

• - With the method known from DE-OS 44 34 687 of the measurement of a shock phase angle β _bump can be determined whether the compression process with influencing intensity of the bumps is kept at a prescribed level, or, in which Measures the intensity deviates from a predetermined value.
• - With a method known for example from DE-PS 41 16 647 of changing the resulting centrifugal moment M _R even during the rotation of the unbalance bodies by adjusting the relative position of 4 unbalance bodies to one another, the intensity of the impacts and thus also their effect with respect to Compression can be influenced in a targeted manner.

The latter method belongs to the genus of compression systems to which it was based preferred invention relates. In this type of compression systems with which the state the technology is characterized, the already defined movement generation system is characterized by the Adjustment of one or more actuators affects that the intensity of the perform the shocks changed and thus the compression effect is affected. The application of this special The procedure is not limited to a change in the intensity of the shocks when switching Production from one concrete block to another, but also extends to the Compaction process for one and the same concrete block. It can e.g. B. make sense, the intensity of the Impacts at the beginning of a main compaction with an intensity value of e.g. B. 150% to begin with continuously reduce this value to 100% during the compression process.

In general, the present invention has the task of influencing the known "impact intensity" solution process "or the related state of the art (explained further below) improve. The critical examination of the state of the art will be more successful if this is done beforehand analysis used in the development of the invention and also applicable to critical observation instrumentarium is explained. It is part of the essence of the present invention that in the Development of the inventive solution based on such theoretical approaches  On the part of the manufacturers of concrete block machines apparently not in the design of too verbes compression compaction systems were used.

With regard to this, it is assumed that, on the one hand, the statements of impact theory should be used to predict the compression effectiveness of the impact processes (which was already indicated in OS 44 34 687, for example), and on the other hand during the check of the complex "shock generation + vibration generation" the consequences should be drawn from the so-called impulse theorem. What this means in practice will be explained in Fig. 1a and 1b using the example of a vibrator excited with unbalanced forces. Although the relationships described here initially only relate to the baffle bar method, it can be expected that the knowledge obtained can also be used when carrying out the counterblow method.

The structure and mode of operation of a compression system according to the prior art are described with reference to FIG. 1 a. Cheek-shaped baffle strips 104 are formed on a device substructure or machine frame 102 which is set up on the foundation 100 and which terminate at the top with horizontally lying abutting surfaces 106 which, with its mass fraction belonging to the mass m _a, hits the base plate 120 with its lower abutment surface 122 during its downward movement and can then also rest if necessary.

The mass m _{a also} includes the partial masses of the molding box 124 which is firmly connected to the base plate (shown in this way for the sake of simplification), the molding mass 126 and the load-bearing stamp 128 with the stamp plate 130 . A spring 132 , which is supported indirectly against the foundation 100 , symbolizes all spring forces, which can ultimately act on the base plate 120 .

Between the device base 102 and the base plate 120 , the spring table 140 , which is supported by compressive and tensile springs 142 with the resulting spring constant C _RT against the foundation 100 , is arranged, to which the mass m _{s is} assigned, which symbolizes the sum of all those mass fractions whose weight forces must be supported by the springs 142 in the idle state of the vibrating table. Two unbalance bodies 144/144 ', driven by drive motors M1 / M2 (not shown) and provided with a resulting (manually or mechanically adjustable) centrifugal torque M _R , are fixedly connected to the oscillating table 140 via bearings and rotate in opposite directions and mirror-image synchronously with the angular frequency ω. The unbalance body 144/144 'and the vibrating table 140 essentially represent the vibrating vibrator, which in the absence of gravitational acceleration could perform its vibrating function even without the springs 142 .

When swinging down the vibrating table forms a gap 152 between the top surface 150 acting as a thrust surface of the vibrating table and the bottom thrust surface 122 of the base plate, which gap is reduced again during the subsequent upward swinging until a "shock 1" at the impact speed Δv 1 takes place at the impact points , the mass m _a an impulse I 1 is communicated. Driven by the impulse I 1, the mass m _a performs an upward movement, in the course of which a second gap is formed between the abutting surfaces 106 of the impact bar and 122 of the base plate. As soon as in the downward movement of the mass m _a this second gap assumes the value zero, there is a renewed "shock 2" initiated with the impact velocity Δv₂, this time between the mass m _a and that in comparison with the mass m _a much larger mass m _{F of} the foundation.

The movements carried out in the case of the impacts 1 and in the execution of the oscillating movement of the mass m _s and the forces which have been implemented with regard to the explanation of the “shock generation and oscillation generation” by means of the pulse set are common in FIG. 1b The abscissa axis of time t = ϕ / ω is shown in diagram form. Here, with an assumed constant value for the angular frequency ω, the time axis t can also be replaced by the oscillation angle ϕ (= ω _* t), with the associated time stamps then having to be replaced by corresponding oscillation angles. In order to be able to create a comparison basis for the comparative consideration of impact processes with different impact intensities, the movement of the vibrating table 140 or of the mass m _s shown in the middle part of FIG. 1 _{b should} run in such a way that the impact 1 occurs at the moment when the Mass m _s has assumed its highest vibration speed v _{s, max} = A _{s *} ω. The height of the time axis t corresponds to the height of the abutment surface 122 or 106 in FIG. 1a.

The “lower” vibration path of the vibration table 140 is represented by the curve pieces 160 lying under the time axis t, with A _s as the nominal amplitude. The course of the "upper" vibration path of the vibration table after the impact 1 is characterized by the curve pieces 162 provided with a smaller amplitude A _k , it being assumed in a simplified manner that there is no longer any contact between the impact points on the entire curve piece 162 , or that the rush hour is negligibly small. In addition, in order to adapt to typical practical conditions, it is assumed that the size ratio A _s / A _k corresponds to a ratio q = 2/1.

The rest position of the vibrating table 140 at an angular frequency ω = zero is characterized in the present case by the fact that the abutment surface 150 bears against the abutment surface 122 of the base plate with a certain prestress generated by the springs 142 . The spring preload F _V arises according to the relationship F _V = C _{RT *} s _v [1]. Where s _{v is} the spring preload. The time event of the start of the shock 1 is characterized by the time stamp t₂ and the time event of the swinging under the rest position of the vibrating table during its downward movement is characterized by the time stamp t₁.

Before the forces shown in Fig. 1b, which are only important for the considerations when applying the statements of the momentum theorem, are to be made here a few comments about the role of the other forces actually attacking the mass m _s :

Weight force F _G of mass m _s and spring force F _{F, st} from the static deflection: Under the influence of the weight force F _G , the spring 142 is compressed to a certain extent when the vibrator is at rest (static deflection), a spring force being generated, which speaks to the weight force F _G. These two forces are always present in the same size even when the vibrating table is swinging. However, since both forces are always of the same magnitude and oppositely directed, they can be completely disregarded in the further considerations for the normal case.

Centrifugal forces or unbalance forces: The impulses generated by the unbalance forces act with changing direction in always the same size only on the mass m _s of the vibrating table. These impulses therefore remain in the "system of mass m _s ". For this reason, the unbalance forces can also be disregarded when interpreting the pulse rate for the intended purpose. The unbalance forces are of interest here only with regard to the vibration amplitudes influenced by them.

"External impulse forces": Only those (external) impulse forces from impulses that the mass m _s exchanges with other external organs are relevant for the approach used here between the mass m _s (of the vibrating table) and the mass m _a (the Base plate etc.) exchanged impulses. For this reason, only the "external momentum forces" are mentioned in Fig. 1b.

. For the preparation of resonant trails and forces in Figure 1b, the following should be noted: It is assumed for simplicity that the phase shift between the unbalance exciter forces and the self-adjusting Schwingwegverlauf be always 180 °. The directions of the forces are entered so that they represent the direction of their action on the mass m _s . The shock impulses are therefore downward (negative) and the spring force impulses are upward (positive). The curves for vibration paths and forces are each shown twice, with a solid line and a broken line. The courses shown with a full line are intended to describe a state when applying a first value (e.g. 100%) for the resulting centrifugal moment M _R. The courses shown with the broken line are intended to describe a state when using a second, larger value (eg 150%) for the resulting centrifugal moment M _R. First, the situation described by the full lines is described:

In the upper part of FIG. 1b, the time profiles 170 of the impact forces developed between the masses m _s and m _a during impact 1 are recorded. These are forces with very high maximum values H _I , which are only developed during the very short time difference between times t _A3 minus t₂. These impact forces result from the impact processes of the vibrating table with the base plate. A pulse I _{a is} emitted to the mass m _a , of which a first sub-pulse I _{a, m} communicates a kinetic energy to the mass m _a [which gives this mass its own movement (upwards)] and a second sub-pulse I _{a , v is converted} into deformation energy and friction energy in the system of mass m _a .

In the lower part of Fig. 1b, the time profiles 180 of the spring forces of the springs 142 are ben ben. It can be seen that the absolute value of the forces is composed of the constant spring preload force F _V and those forces which, in addition to the forces already built up in the springs 142 during the rest position of the oscillating spring, in the deformation of the springs as a result of the course of the curve due to the cure 160 marked movements of the vibrating table arise. Since it can be assumed in a simplistic manner that the movement curve 160 consists of two arc pieces following a sine function (with the two different amplitudes A _s and A _k already defined _above ) with the zero crossings t 1 and t 2 (with t 2 minus t 1 = π / ω), and since the resulting spring constant C _{RT of} all springs 142 can be regarded as constant over the entire deformation path, curve 180 is also composed of two arc pieces, each following a sine function, namely (based on the amplitudes A _s and A _k ) with the force amplitudes F _A and F _k . The ratio F _A / F _k is 2/1. The course of the two arc pieces contained in curve 180 , representing the spring force F _F = f (t), can therefore be described with: F _F1 (t) = F _{A *} sin (ω _* t) for one arc and with F _F2 (t) = 0.5 _* F _{A *} sin (ω _* t). The total spring force therefore results for the section with the F _A amplitude: F _{Σ A} (t) = F _V + F _F1 (t) [2a] and for the section with the F _k amplitude to: F _{Σ k} (t) = F _V - F _F2 (t) [2b].

Since, according to the agreement, the interest is directed exclusively to those impulses which the oscillating or impacting mass m _s exchanges with the neighboring organs, the impulse theorem comes in the general form:

to use. The force integral S _I on the left side of the equation is known as the "force shock", while the right part is the so-called "movement quantity" or the "pulse" I _s .

The pulse set [3] can be applied separately for the positive and negative forces acting on the mass m _s . The force surges formed by the negative forces of the shock impulses (above in FIG. 1b) over the period of a period are to be called "shock force surges" S _IS . The force surges formed by the positive forces of the springs 142 (bottom in FIG. 1b) over the period of a period are to be called "spring force surges" S _IF .

In terms of the development of the invention, the following interesting conclusions can be drawn from [3]:
⇒ Since it is a periodic vibration of the vibrating table, which is essentially also repeating in the form of the path, the two force surges, which are formed from the positive and negative forces during the integration time Δt = 2π / ω of a period can be the same in their amounts. In other words: | S _I | = | S _{I, S} | - | S _{I, F} | = 0. This means that when using the same scales in FIG. 1b, the hatched areas within the curves 170 of the shock-force surges in the upper part of the figure must be exactly as large as the hatched area of the spring-force shock below the curve 180 im lower part of the picture.
⇒ The intensity of the compression effect depends on the height H _{I of} the shock pulses or also on the size of the hatched area within curve 170 . If there is a change in the size of the shock pulse, the hatched area below curve 180 must also be increased analogously to this. In the prior art, a change in the shock pulses is brought about by a change in the nominal vibration amplitude A _s . In Fig. 1b, the situation marked by broken lines represents a situation in which, compared to the situation drawn with solid lines, the resulting centrifugal moment M _R was increased, which is equivalent to an increase in the center of the picture in Fig shown. 1b oscillations gamplitude A _s and A _k.

The enlargement of the "shock-force shocks" S _{I, S} formed by the enlarged shock pulses (top in FIG. 1b) contrasts with an increase in the "spring-force shocks" S _{I, F} formed by the spring force pulses (bottom in FIG. 1b) . It can be seen that the increase in the "spring force surges" S _{I, F was brought} about not only by an increase in the amplitude F _A '<F _A , but also by an increase in the pretensioning force F _V '<F _V. Both changes can of course be seen as a result of the increase in the nominal vibration amplitude A _s .
⇒ It is now the "basic idea" of the present invention to reverse the old operating principle defined by the 3 components, according to which a changed resulting centrifugal moment M _{R changes} both the "shock-force impulses" S _IS and the "spring-force impacts" S _IF , and to move according to the changed new principle of action, after which one has to change the "spring force shocks" S _IF while keeping the resulting centrifugal moment M _R , thereby indirectly also the "shock force shocks" S _IS , or the between Vibration table and base plate to change exchanged shock pulses. According to the inven tion, the measures taken for this purpose at the "spring force surges" S _{IF are} intended to replace the measures required in the prior art for adjusting the resulting centrifugal torque M _R. For the "spring force shocks" to be manipulated in the sense of this statement, both the spring force shocks S _{I Σ} according to formula [7] and the spring force shocks S _{IF, Σ} according to formula [8] come into question.
⇒ The possibilities for changing the size of the "spring force shock" S _IF can be determined after carrying out an integration in order to determine the size of the "spring force shock" S _IF according to the regulation of the pulse set according to formula [3]:

With a view to Fig. 1 shows that the "spring-force shock" S _IF has to be determined over the forces of the springs 142, whereby the "spring-force shock" S _IF the (hatched) area under the curve 180 in Fig. 1b (below) corresponds to the time difference t₂ minus t₁ = Δt = 2π / ω. If the expression P (t) in formula [3] is replaced by F _{Σ A} (t) according to formula [2a] and F _{Σ k} (t) according to formula [2b], the impact S _{IF, Σ is} :

In the considerations made so far, it was always assumed that the force impulses only act on the mass of the vibrating table via springs. In a more general consideration of the case, additional forces F _z = f (t) are also possible, which can act as external forces on the mass m _{s of} the vibration system. Such forces come into consideration: damping forces or additional driving forces which can act on the mass m _s in both directions of oscillation.

Under the simplifying assumption that the additional force F _z is a constant force [instead of a generally also permissible time-dependent additional force F _z = f (t)] and when using the power surge component I obtained from this additional force by forming the time integral _z = ± F _{z *} 2 π / ω [5] is expanded [4] to the general power surge formula:

S _{I, Σ} = I _s ′ = F _A / ω + F _{V *} 2π / ω ± F _{z *} 2 π / ω [6].

Since the maximum deformation of the springs 142 during the swinging movement downward is supposed to be proportional to the nominal (lower) amplitude A _s , F _A = C _{RT *} A _s . Together with [1], the power surge S _{I, Σ} from formula [6] is given the general form:

S _{I, Σ} = I _s ′ = C _RT (A _s + 2π s _v ) / ω ± F _{z *} 2 π / ω [7],

and the power surge S _{IF, Σ} from formula [4] takes the form:

S _{IF, Σ} = I _s = C _RT (A _s + 2π s _v ) / ω [8].

Unless it is assumed for simplification that the impact time t _A3 - t₂ towards the value zero, can the right side of the equation [3] (with the definition of the mass m _s output pulse I _{s) s} m for a given constancy of mass for the relationships assumed in FIG. 1b are simplified to:
m _s v _{s, max} - m _s v _{s, e} = m _{s *} Δv _s . [9]. Here, v _{s, e means} the speed assumed by mass m _s at the end of pulse 170 ( FIG. 1b, top) at time t _A3 . From Fig. 1b it can be clearly seen that the value m _{s *} Δv _s can be equated in value with the value of the impact force shock S _IS . This means:

S _IS = m _{s *} Δv _s [9a].

If the initial velocity assumed by the impacted mass m _a at the end of pulse 170 ( FIG. 1b / top) at time t _{A3 is} Δv _a , then the product m _{a *} Δv _{a represents} that partial pulse I _{a, m} which of the energy from which the mass m _a transmitted pulse I _a net in deformation and friction energy over previous pulse part I _{a, v} remained. With the definition of a loss factor "q" (with values from 0 to 1), because of the equality of I _s and I _a , the relationships I _{a, v} = q _* I _a = q _* I _s [9b] or I _{a, m} = (1 - q) I _a = (1 - q) I _s [9c]. Both partial pulses I _{a, v} and I _{a, m} behave in proportion to the pulse I _a transmitted to the mass m _a (which is decisive for the compression effect). For further considerations, however, the partial pulse I _{a, m} = m _{a *} Δv _{a should be used} as a measure of the compression effect in the form of the relationship I _s = I _a = m _{a *} Δv _a / (1 - q) [9d] step.

Since the relationship | S _IS | = | S _IF | was defined (neglecting the sign) with [6] + [9] or with [8] + [9] and using the relationship [9d] from the impulse theorem according to equation [3]:

S _{I, Σ} = I _s ′ = C _RT (A _s + 2π s _v ) / ω ± F _{z *} 2π / ω = m _{s *} Δv _s = I _a ′ = m _{a *} Δv _a / (1 - q) [10],

S _{IF, Σ} = I _s = C _RT (A _s + 2π s _v ) / ω = m _{s *} Δv _s = I _a = m _{a *} Δv _a / (1-q) [11].

A useful piece of information for estimating a reasonable upper value for the resulting spring constant C _RT results from the requirement that the natural frequency of the oscillatable system supported by the springs 142 with the mass _ms with a lowest excitation angular frequency of ω _u by at least the factor 2 should be above the resonance frequency ω _{o of} the system. Expressed with the frequency ratio η = ω _u / ω _o [16], this requirement is: η 2. [17].

One can derive a law which, for a model according to FIG. 1, indicates the insertion path s _{o of} the springs 142 due to the dead weight of m _s (static deflection), the resonance frequency f _{o of} this system has been reached. The corresponding relationship is: s _o = 0.248 / f _o ² [18] with s _o in m and f _o in Hz. If f _u = 40 Hz is used for the lowest excitation frequency, then the maximum permissible resonance frequency with [ 16] and [17]: f _o = 20 Hz. With [18] one finds: s _o = 0.6 mm [19]. If, on the other hand, the deflection path is chosen to be s _real = 1 mm, as can usually be found in practice, the resonance frequency drops to 15.7 Hz and the frequency ratio increases (at f _u = 40 Hz) to the value η = 2.6. For the so-called insulation efficiency ζ = 100 (η² - 2) / (η² - 1) [20] with η = 2.6: ζ = 83%.

With the formulas [7] and [8] or [10] and [11] is a general solution for assessing one of the "Impact 1" required to carry out the exchange of predetermined impulses given.

For the known compression systems with directional unbalance vibrators as force exciters, which are part of the prior art and in which the impact intensity is adjusted by adjusting the nominal amplitude A _s , the following interesting considerations can be made from formula [8]:
From the expression I _s = C _RT (A _s + 2π s _v ) / ω contained in formula [8], it can be seen that, starting from an equality of values of A _s and s _v , the value of the expression I _{s is} much faster increases with a percentage increase in the value of the size s _v relative to the size A _s , than vice versa. What this means in practice is explained using the following example of an amplitude doubling:
In the event that there is a doubling of the nominal amplitude A _s , according to the model of FIG. 1 _, the movement quantity m _{s *} v _{s, max} and thus also the could be due to the relationship "v _{s, max} = A _s ω" Transmittable pulse I _{a, ü are} also doubled. However, this could only be put into practice if [8] doubling A _s also doubled the value of the power surge I _s .

As can be seen, [8] [assuming the approximate condition s _v = 1 _* A _s (p = 1)], a doubling of the value of A _s results in an increase in the power surge by a factor of Q _2A = (7.28 + 1) / 7.28 = 1.14. The factor Q _2A = 1.14 is called the "amplitude doubling efficiency factor".

The "amplitude doubling efficiency factor" Q _2A can be defined not only for the case s _v = _* A _s , but also for any assignments s _v = p _* A _s . For this more general case, the factor Q _2A from formula [8] is calculated from the ratio of the pulse I _{s, d} resulting from an amplitude doubling to the pulse I _{s, n} resulting from an unchanged amplitude:

Examples

For the case p = 1 already discussed above, Q _2A = 8.28 / 7.28 = 1.14. For the case p = 0.5, Q _2A = 1.24 is obtained. This means that if the amplitude value A _s is doubled, a 14% increase in the transmissible pulse I _{a, ü} = I _{s can be} achieved in the case of p = 1 and a 24% increase in the case of p = 0.5.

Although a variation of the pretensioning path which can be influenced via the machine control is not provided in the compression systems according to the prior art which work according to the pulse compression method, it is nevertheless useful for comparison purposes, analogously to the "amplitude doubling efficiency factor" Q _2A, a "biasing _doubling efficiency factor Q _2p "to define with what chem the effect of doubling the preload s _v can be estimated. The factor Q _2p derives similar factor Q _2A from z. B. Formula [8] from:

Examples

A doubling of the pretensioning path s _v results in an increase of 86% with p = 1 and a 92% increase with p = 2, the deliverable impulse I _{a, ü} = I _s .

The formulas [7], [8], [10], [11] and [22] can still be used to list the following Derive remarks with which the state of the art can be further characterized  and with which the limits of controllability of the intensity of the shock waves of the known compaction systems are shown:

Remark 1: From formula [7] it follows (with s _v ≈ A _s ): If (with the value for ω remaining constant) the doubling of the nominal vibration amplitude A _{s is} also to be achieved, the transmittable pulse I _{a, ü should be} achieved at the same time and additionally an increase in the spring preload F _V and / or the additional force F _{Z is} required.

Note 2: From formula [7] it follows (with s _v ≈ A _s ): If, starting from a basic setting with a nominal amplitude A _{s, o} , the amplitude is changed by the value ΔA _s , and approximately the same Ratio ΔA _s / A _{s, o} resulting change in the transmittable pulse I _{a, ü} expected, the spring preload force F _V (or the spring preload path s _v ) or the additional force F _Z must be adjusted individually for each value of ΔAs.

Note 3: From formula [8] or [22] it follows that if you change the amplitude with a spring preload of s _v 2 A _s from a basic setting with an amplitude A _{s, o} , it is practically impossible to change one achieve _a remarkable increase in the transmittable pulse I _{a, ü} , because according to formula [22] and with p = 2 the "amplitude doubling efficiency factor" Q _2A with Q _2A = 1.07 approaches the value 1.

Note 4: From formula [22] it follows: The dimensioning of the values for C _RT has to be done with the principle of amplitude change within the relatively narrow limits described as follows: Already with a reduction of the value of the spring constant C _{RT in} such a way that the required spring preload s _v assumes a value greater than s _v 1.5 A _s (p = 1.5), the "amplitude doubling efficiency factor" Q _2A drops to a value below 1.09 value. With such low "efficiencies" of the consequences of the amplitude enlargement, a dimensioning limit should be reached, since one must also note that an increase in the nominal amplitude A _s results in a linear increase in the bearing forces. Assuming a value for the amplitude A _s of A _s = 1 mm, this would correspond to a limit deflection value of s 1.5 mm, which according to [18] means f _o = 13 Hz and assuming a lower operating frequency of 40 Hz would lead to a frequency ratio of η = 3.1. According to [20], this would correspond to an insulation efficiency of η = 88%.

With an increase in the value of the resulting spring constant C _RT the influence of the _real generated by the vibration amplitude A growth of the force pulse S _{I, Σ,} and the value for the required Federvorspannweg rises s _v lowers. The implementation of this statement in practice results in an increase in the impact intensity, which is to be welcomed, with a consistently high resulting centrifugal moment M _R , because of the increase in the power surge S _{I, Σ} . At the same time, an increasing value for the spring constant approaches the permissible limit of approximation to the resonance frequency. As was deduced previously, the compression ratio η = 2 (not to be undershot if possible) for a lowest operating frequency of f _u = 40 Hz results in a deflection path of S _real = 0.6 mm that should not be undercut, which must be compared with the usual deflection of approx. 1 mm in practice, which already corresponds to a value of η = 2.6 at an operating frequency of 40 Hz.

Note 5: According to the requirement of the impulse set for equivalence of the expressions describing the power surge S _{I, Σ} and the movement size, it is for an enlargement of a given "basic setting" of the values of the parameters for C _RT , A _s , s _v , ω , and F _Z (corresponding to a basic setting S _{I, Σ , M of} the power surge) and with an optimally adapted "basic setting" of the resulting centrifugal torque (with the necessary minimum value M _RM ) practically achieved transmittable pulse I _a over the Amount ΔI _{a, ü} necessary that both the power surge S _{I, Σ} and the pulse I _a = m _s Δv _{s must be} increased by a factor of 1 + ΔI _{a, ü} / I _{a, ü} = λ.

A bumper system according to Fig. 1 is satisfied naturally in each case, the condition of the formula [3] or [7] or [10]. The impact system automatically adjusts the values for Δv _s by shifting the phase angle of the excitation force relative to the oscillating movement of the mass m _s . The impact system only automatically provides the required Δv _s value if the drive motors are able to supply the system with the required minimum amount of energy per revolution and if a minimum value for the resulting centrifugal torque M _{R is} set. Assuming that the engine power is always sufficient, the shock system implements the equality requirement from formula [3] or [7] or [10] as follows:

• - The transmittable pulse I _{a, ü} is determined by the value of the set power surge S _{I, Σ} , provided that the centrifugal torque M _R has the sufficient minimum size M _RM . If the centrifugal moment is less than M _RM , the centrifugal moment itself determines the value of the transmittable pulse I _{a, ü} with its value (for a given value for S _{I, Σ} ). If the centrifugal torque is greater than M _RM by an excess amount ΔM _R , the excess amount ΔM _{R is} ignored and the value of the transmittable pulse I _{a, ü} is proportional to the value of S _{I, Σ} .
• - The transmittable pulse I _{a, ü} is determined by the value of the centrifugal torque M _RM , provided that the value of the power surge S _{I, Σ has} the sufficient minimum size S _{I, Σ , M.} If the value of the power surge S _{I, Σ is} less than S _{I, Σ , M} , (with the centrifugal torque remaining the same) the transmittable pulse I _{a, ü} depends on the (smaller) value of the power surge S _{I, Σ} . If the power surge S _{I, Σ} is greater than S _{I, Σ , M} by an excess amount ΔS _{I, Σ} , the excess amount is ignored and the transmittable pulse I _{a, ü} is proportional to the value of the centrifugal torque M _RM .

From the findings previously made, it can be deduced that there are at least the following two options for bringing about the change in the transmittable pulse I _{a, ü} by the amount ΔI _{a, ü} :

• a) There is a vibration velocity v _s enhancing enlargement of the basic setting of the resultie leaders Fliehmomentes M _R and the nominal resonant amplitude A _s made such that the pulse I _s = m _s △ v _s due to the increase potential for △ v _s λ by a factor of magnification capable is, and at the same time an increase in the power surge S _{I, Σ is} also made by the factor λ. [If an increase in S _{I, Σ is} not already caused by the increase in A _s itself, an enlargement of one of the other controllable parameters, e.g. B. an increase in the spring preload s _{v made} such that there is an overall increase in the power surge S _{I, Σ} by the factor λ].
• b) The transferable pulse I _{a, ü} is to be determined by the size of the power surge S _{I, Σ} : In the basic setting for the transmission of the transferable pulse I _{a, ü} , the values of the power surge parameters are C _RT , s _v , ω and F _Z (and thus also the value S _{I, Σ , M of} the power surge) is set to a value proportional to the value of the pulse I _{a, ü} . The resulting centrifugal torque is equipped with an excess value ΔM _R with respect to the required minimum value M _RM (M _R = M _RM + ΔM _R ), so that the relationship applies: M _R = M _RM + ΔM _R = M _R λ. When transmitting the transmittable pulse I _{a, ü} with the basic setting of the power surge parameters (or with the basic setting of the power surge S _{I, Σ , M} ), the excess value ΔM _{R is} not taken into account as if it were not present. It is not activated, so to speak.

To increase the transmittable pulse I _{a, ü} by the factor λ, the value of one or more power surge parameters is increased from the basic setting in such a way that the power surge S _{I, Σ} by the factor λ to the size S _{I, Σ} = S _{I, Σ , M *} λ has grown. With this setting _, the power surge S _{I, Σ is} able to activate the excess value ΔM _{R of} the centrifugal torque, as a result of which the transmittable pulse is increased by the amount ΔI _{a, ü} .

Note 6: When the transmittable pulse I _{a, ü is increased} by increasing the resulting centrifugal moment M _R while keeping the values for the resulting spring constant C _RT and for the spring preload s _v constant, the required simultaneous increase in the power surge S _{I, erfolgt is} only achieved by the effect of an increased amplitude. As already shown in connection with the discussion of formula [22], the efficiency Wirkungs of influencing the power surge by changing the centrifugal torque M _R (or amplitude A _s ) is poor. Already at that setting in such compression systems, in which the value of the spring preload s _v corresponds at least to the value of the nominal amplitude A _s (i.e. at p = 1), the percentage ratio ξ of the increase in the power surge is ΔS _{I, Σ} to increase the Centrifugal torque ΔM _R : ξ = 14%.

This poor efficiency ξ is disadvantageous in practice in view of the consequences to be drawn with an increase in the centrifugal torque M _R. On the other hand, the method according to "Note 5, point b)" for z. B. s _v = 2 A _s (p = 2) have a favorable efficiency of ξ <90% {calculation according to formula [23]}, if in this method the enlargement of the portable pulse I _{a, ü} by changing the power surge S _{I, Σ} the power surge S _{I, Σ is formed} with a relatively large value for the spring preload s _v (at, for example, s _v = 2 A _s ) and (correspondingly) a relatively low resulting spring constant C _RT .

Note 7: An advantageous method of adjusting the impact intensity can be defined (as is done in the present invention), the adjustment within a whole (for the impact intensity) predetermined adjustment range to any given values of the impact intensity exclusively by changing the size of the power surge S _{I, Σ} takes place, being based on note 5b over the entire adjustment range with a "surplus value" of the centrifugal torque M _R , and of the surplus value of the surplus value portion required for the respectively specified shock intensity by a corresponding setting the value of the power surge S _{I, Σ} "activated".

This requires a fixed setting of the value of the centrifugal torque M _R at the same time the setting of a high value for M _R or a high value for the nominal amplitude A _s , since the excess value is to be measured with reference to the greatest required shock intensity. According to the term (A _s + 2π s _v ) in the formula [7], this also means that due to the influence of the nominal amplitude A _s on the value of the power surge S _{I, Σ} it is also a high value for the power surge S _{I , Σ is} set, which in turn automatically activates a high percentage of excess value, which in turn results in the setting of a high impact intensity. This is in contradiction to the requirement to want to set arbitrary shock intensities with the change in the power surge S _{I, Σ} .

It is therefore necessary in this case to reduce the influence of the nominal amplitude A _s on the size of the force shock S _{I, Σ} as much as possible. This can be done in two different ways:

• a) In the expression contained in [7] (A _s + 2π s _v ), the proportion of the link 2π s _v compared to the link A _{s must be} increased considerably, which at the same time requires a considerable increase in the spring preload travel s _v . Because of the relationship (the spring preload force F _{V, which is} not necessarily increased in this process) F _V = C _{RT *} s _v , increasing the value of the spring preload travel s _v also requires a lowering of the value for the resulting spring constant C _RT . An increase in s _v should at least correspond to a ratio of s _v 1.5 A _s but optimally a ratio of s _v 2 A _s or greater.
• b) according to formula [7], an excessive influence on the power surge S _{I, Σ} can be reduced again by the nominal amplitude A _s by using an additional force F _{Z provided} with a negative indicator.

Note 8: As was stated in note 4 above, in compression systems in which the impact intensity is controlled by adjusting the centrifugal torque M _R , there is a lower limit (s _v = 1.5) with regard to the possible reduction in the value of the resulting spring constant C _RT mm), which is determined by practical considerations. The maximum insulation efficiency of ζ = 89%, which is also limited by the lower limit value, can be seen as a parameter that still needs to be improved.

Note 9: A limit on the desirable for the purposes of a better vibration isolation against the foundation lowering the value of the spring constant C _RT does not exist when parameters for an adjustment of the shock intensity is not the nominal as adjusting the amplitude A _s, but the Federvor Tension s _v or the additional force F _{Z is} selected.

Note 10: It is noteworthy that the power surge S _{I, Σ} is inversely proportional to the frequency ω. On the other hand, in the expression in [10] or [11] for the pulse I _s , the angular frequency ω should be approximately proportional. This means that with a growing value of ω the pulse I _s (which is also decisive for the level of the value of the transferable pulse I _{a, ü} ) also grows (or could grow), provided that the force shock S _{I, Σ also increases} ω would grow with it. The power surge S _{I, Σ} is not only increased together with the growing ω, but even reduced in a manner proportional to the reverse of ω.

From this, various practical applications for controlling the impact intensity can be derived. For example, {z. B. according to the formula [7] or [10]} may also be useful to change one or more of the parameters A _s , s _v or F _Z when changing the compression frequency. The resulting control options for the impact intensity are of particular importance when the possibility of influencing the nominal amplitude A _s (e.g. for cost reasons) is not available. Then there is the possibility of controlling the shock intensity (which can be carried out in comparison to the amplitude control with less expensive means) in addition to the practiced change of ω by simultaneously changing the parameters of the spring preload force F _V (or the spring preload path s _v ) and / or the additional force F _Z. In yet another application, the variable angular frequency ω can also be used alone to change the power surge and thus also to change the shock intensity.

Note 11: When carrying out measures to change the impact intensity, the actual goal must be to change the size of the pulse I _s = m _s Δv _s or I _a = m _a Δv _a / (1 - q). Consequently, in an effort to control or regulate the impact intensity, the pulse I _a or I _{s must be} the controlled variable. The pulse I _{s is} best suited for the necessary measurement of the controlled variable. Since the mass m _{s is} constant, the controlled variable I _{s is represented} by the (easily measurable) value Δv _s .

In the targeted influencing of the impact intensity according to predetermined values, in the method of influencing the impact intensity by influencing the power surge S _{I, Σ} or by influencing one or more of the parameters determining the power surge, C _RT , s _v , F _Z and ω one Control or regulation of the pulse I _s also take place indirectly by controlling or regulating the power surge parameters defined in this case as control variables, but only on the condition that the condition described below is fulfilled.

In order to be able to transmit a specific pulse I _a , a certain minimum value for the power surge S _{I, Σ} and a certain minimum value for the pulse I _s must also be set {in accordance with [7] or [10]}. In the event that the values for the power surge S _{I, Σ} and for the pulse I _{s are not} adjusted within the intended adjustment range in the associated size, but only the values for the power surge S _{I, Σ} , it must be ensured that the fixed values for the pulse I _s correspond at least to the maximum values required for the intended adjustment range.

The size of the pulse I _s is determined (with constant mass m _s ) by the set values of the resulting centrifugal moment M _R. As a result, when the compression system is operated with the impulse parameters set at the lower range limit and thus when operating at the lower limit of the adjustment range of the pulse I _s, the centrifugal torque M _R has a non-activated or unnecessary "excess value" .

Note 12: The force-time integrals of the additional forces "± F _Z π / ω" introduced in formulas [7] or [10] are derived from braking or driving forces which simultaneously extract or supply energy to the system. This has an effect not only on a corresponding additional output or reduced output to be output by the motors, but also on the phase position of the rotating centrifugal force vector of the resulting centrifugal force. As a result of this, the “excess values” of the resulting centrifugal torque M _{R that} are necessary under certain circumstances and mentioned in the remarks 5b) and 11 can be influenced. The necessary "excess values" can be partially or completely compensated for by the amount of energy withdrawn or supplied (per revolution), ie made unnecessary.

Remark 13: In a simplifying manner it was assumed that the impact of the mass m _s against the mass m _a at the time of the greatest vibration velocity v _{s, max} (in FIG. 1b at time t₂) was seen, whereby for the mass m _a transmissible pulse I _{a, ü} an optimum is reached and a ratio of the force amplitudes F _A / F _k = 2/1 was assumed. This ideal case cannot be achieved as a permanent setting on a compression system without engaging a control method that preserves this optimal case (e.g. as described in DE-OS 44 34 687). Rather, with conventional compression systems in practice, it must be expected that there will be a shock situation at a significantly lower vibration speed, whereby the ratio F _A / F _k as 4/3 or F _k / F _A as 0.75 can be set.

If you take into account how easily (and especially with regard to the absolute size of s _v , namely in the range of a millimeter) due to tolerances and wear that occur, or due to a corresponding setting rule, the case can occur that the preload travel s _{v of} the springs can assume a value of s _v = 75% of the nominal vibration amplitude A _s , one recognizes the problem that arises with this: Even with a value of s _v = 0.75 A _s , the possible ratio F _k arises / F _A = 0.75 the situation that the distance "h" in Fig. 1b / below and thus the entire biasing force F _{V takes} the value zero.

If one tries in this constellation to increase the amplitude A _s in order to increase the impact intensity, the distance "h" takes on a negative value, which corresponds to an expansion (instead of compression) of the springs ( 142 in FIG. 1a). At the same time, this also means that the increase in the force shock S _{I, Σ which is} hoped for with an increase in the amplitude A _s occurs only to a very weakened extent.

The lower the ratio s _v / A _s , the more serious this disadvantage.

The above considerations again show how little scope there is in varying the ratio s _v / A _s downwards and how great the risk is of reaching the range of negative values of "h".

The doctrine to be drawn from the considerations made states that one can avoid the described problem, provided that, unlike practice, the springs are designed in such a way that the preload force F _V (which can still retain its conventional value) results from the product of a reduced resulting spring constant C _RT and at the same time an enlarged preload path s _{v of} the springs. To use all negative predictors off should therefore the preload s _v s _v, at least 2 A _s and s _v 2 mm, more preferably 3 s _v A _s and s _v 3 mm Betra gene. As indicated by the patent claim 5 or the comments on this, there are additional advantages with this increase in the preload s _v .

The teaching drawn from the application of the pulse set with the regulation for increasing the pretensioning path s _{v of} the springs therefore represents an independent invention in itself, which can not only be applied to the impact intensity to be changed via the power surge S _{I, Σ} Compression systems, but also on conventional compression systems working with shock compression in order to improve their working methods and their safety or to keep the product quality constant.

Before the general state of the art is discussed in more detail below, it should be pointed out ben that, in addition to the two methods cited at the beginning, namely baffle molding method and counter impact method, a third method is introduced in practice, which is called "vibrating vibrator to proceed ".

In this method, the top of the vibrating table ( 140 ) always remains in contact with the bottom of the base plate ( 120 ) during the vibration, so that at least the bottom of the base plate vibrates practically synchronously with the vibrating table. A compression effect as a result of impacts that are brought about, such that a butt joint is formed with butting surfaces that cyclically move away from one another and then collide again, can at most only occur if an impact point is either between the molding compound ( 126 ) and the base plate ( 120 ) , or between the molding compound and the underside of the stamp plate ( 130 ) (see Fig. 1a).

Such a "vibrating vibration method" naturally works with completely different principles of action than they are used in the type of compression systems to which the invention relates In particular, such methods are not used by experts from the point of view of impact theory be 45632 00070 552 001000280000000200012000285914552100040 0002019634991 00004 45513.

When considering the general state of the art one has to consider that in the application shock vibration systems on concrete block machines are very complex processes and that it with regard to the possible influence on the compression result, a large number, the expert known adjustable parameters, which generally influence each other in many ways. The so far Control measures that become known are differentiated from manufacturer to manufacturer theories or philosophies. It may well happen that a certain adjustment measure in connection with a certain parameter under the boundary conditions of a measure combination took an improvement and under the conditions of other combinations of measures provides a deterioration in the process result.

It is therefore only possible to a limited extent as a first combination of features known per se obvious for an accomplished inventive step of producing a second combination of to consider known features, if not at the same time the theory being pursued is compared becomes. When determining the state of the art, it is e.g. T. not possible to become known Feature combinations to determine the theory being pursued.

The general state of the art, which also includes the technique of the compression systems which cannot be adjusted in terms of their impact intensity during the rotation of the unbalances, does not include the analysis of the technical relationships of various influencing factors using the pulse set. Well that the person skilled in the following specific effects are known may be provided. The compaction processing result (may vary depending on still other factors, such as Auflastmasse, tamper head, mass _s m, shapes mass, mold pressing pressure, concrete mass, resulting centrifugal moment M _R , angular frequency of the excitation forces and natural frequencies of different vibration systems) are influenced in a positive or negative manner by varying the values of the resulting spring constant C _RT and / or the spring preload s _v :

• - With the variation of the parameter C _RT , the person skilled in the art has relatively narrow limits in the state of the art, as was already discussed under "Note 4".
• When using a spring preload path s _v , according to the prior art, such an adjustable value range of the associated resulting spring constant C _{RT is} assumed, as would also be used if spring preload is not provided. The range of values used when using a spring preload essentially comprises values between s _v = zero and s _v = A _s (A _s = nominal vibration amplitude). Too high a bias voltage (while maintaining the conventional value for C _RT ) leads to the fact that when the impact 1 is carried out, the impact speed Δv 1 decreases again while the gap 152 is being reduced (in FIG. 1 a), the intensity of the impact 1 initially again is reduced. If the spring preload travel s _V or the spring preload force F _v is increased further, the formation of a shock 1 no longer occurs, but a transition to the previously described “vibration-vibration method” takes place, in which the impact surface of the vibration table no longer differs from the impact surface of the base plate separates.

If one considers the state of the art in that special type of compression systems to which the invention relates preferably, one has to look at those compression systems in which the movement generation system is adjusted in this way by adjusting actuators during the rotation of the unbalance body that the intensity of the impacts to be carried out is changed:
The apparently obvious prior art could be presumed in the teaching of DE-OS 30 04 642. Here it says on page 3, line 21 ff .: "While pouring the concrete mass into the molds, it is advantageous to work with a lower vibration force than during the main compaction process, ie after the load has been reduced to the mold content. This possibility is through different start-up of the vibration device given ".

It should be noted in this regard: The cited description of the action is to be connected with that of this Publication assumed "compression philosophy", which is not disclosed.

According to the statements in this document, the object of the invention described there is the task to enable a simple and time-saving changeover to a different type of concrete block to reduce the amount of time necessary to change the mold lock pressure settings, for the height adjustment of the form locking bracket, for the pressure of the load device and for the Shorten unbalance weights. Obviously, the innovation that can be achieved with the stroke adjustment a compression effect can be produced, in which at the same time also the parameters "Mold lock pressure", "Load device pressure" and "Size of unbalance weights" influence taking part. It is not recognizable what contribution the innovative innovation in detail to Compression effect delivers.

Furthermore, according to the introduction to the description ("As a result" in line 10, page 2) the form ver locking pressure, the height adjustment of the form locking bracket, the pressure of the load device and the size of the unbalance weights can therefore also be changed so that "the vibration device constantly May have contact with the supporting device for the concrete block molds "(lines 9 and 10, page 2) this characteristic, the invention explained there should refer to the "oscillating Vibration method ", which works very differently than that of compression systems which the present invention relates. This assumption is supported by the information (lines 22 to 25, page 3) that the "vibration force" (and not impact force) should be reduced, and by specifying other characteristics, the enumeration of which takes up too much space would.  

In the already cited, closest prior art, the intensity of the impacts to be carried out is changed in that the resulting centrifugal moment M _R and thus the nominal vibration amplitude A _{S are} adjustable. With regard to the way in which this adjustment takes place, there are a large number of known design variants, of which the most advanced and powerful is described in DE-PS 41 16 647.

A first disadvantage with the known compression systems according to the closest prior art is that it and especially the preferred and most powerful variant according to DE-PS 41 16 647 are also very expensive and at the same time technically very complex, the technical effort the availability of the machines is also known to be determined.

A second disadvantage of the variants according to the closest prior art follows from the practice of dimensioning the values for the spring constant C _RT, which is forced to be practiced:

• - The spring constants C _{RT used} , with their necessarily relatively high values, lead to unsatisfactory insulation efficiencies ζ when isolating the high excitation forces to be introduced into the foundation.
• - With their relatively high values for C _RT or low values for the frequency ratio η, the springs used lead to an unfavorably close proximity of the operating frequency f to the resonance frequency f _o . At values of η = 2-3, at the usual operating frequencies, feedback can also occur between the other vibratable mass systems of the compression system and the vibrating vibrating table.

A third disadvantage with the known compression systems with the possibility of influencing the Shock intensity by changing the value of the resulting centrifugal moment is that it about a very poor efficiency ξ the effect of a change in centrifugal torque on a shock change in intensity. As a result, relatively large increases in centrifugal torque are required, which u. a. leads to the generation of disproportionately high storage forces. See also "Note 6".

The task for the invention is to evaluate the teachings of the pulse set for the Genre of the compression systems that can be changed with regard to their impact intensity relates to an improvement their previous performance standards. The aim is to improve

• a) to contribute to the fact that the technical effort to be made in terms of improved availability of the system and in the sense of a reduction in manufacturing costs, and / or the possibility open up that
• b) the values of the insulation efficiency ζ or the frequency ratio η and the efficiency ξ the impact intensity change can be raised.

The solution to the problem is defined in independent claims 1 to 4 and 25, their common Statement in the application of the "basic idea of the invention" defined above exists. More before partial embodiments of the invention are given in the subclaims.

The basic ideas of the invention are derived from the previously developed formulas of the pulse set. Although the assumptions made to derive these formulas, e.g. B. according to the assumption of the vibration path according to FIG. 1b, the reality with regard to the detection of the real values of the sizes concerned does not exactly meet, they nevertheless provide the basis for an approximate estimate of what happens in practice. However, the basic statements and readable trends are correct. Accordingly, the basic principles of the invention can also be described as follows: The pulse set, in the form of equation [10], teaches that

• - Provided that such a large value for the engine power and for the centrifugal torque M _R or for the amplitude A _{s has} previously been set as the first condition, with the aid of which a sufficiently large pulse I _{s can be} generated for the oscillating mass m _s , of which at If the desired pulse I _a = m _a Δv _a / (1 - q) can be delivered, a second condition is required in order to be able to actually transmit the pulse I _a during the shock: This second condition means that it is necessary to transfer the Desired pulse I _{a of} a "force shock" S _{I, Σ} corresponding to the size of the pulse I _a and provided with a very specific value (as it were to support the pulse I _a on the other side of the vibrating table with the vibration mass m _s ).
• - In principle it does not matter which combination of the parameters C _RT , s _v , F _Z or ω (with A _s = constant) gives the required value of the expression from [10]: C _RT (A _s + 2π s _v ) / ω ± F _{Z *} 2π / ω is reached.

The invention is defined for a very specific constellation of all participating organs of the Ver sealing system, namely the constellation existing at the main compression, which is marked is due to the attached mass with preload.

In independent claim 1, the Er obtained by including the pulse set Knowledge applied to the sub-task, that well-known and proven, but very expensive agile technique of influencing the impact intensity, e.g. B. according to DE-PS 41 16 647 by Verstel the resulting centrifugal moment during the rotation of the unbalance body by a cost to replace cheaper and more robust technology or to reproduce it in a different way, the tried and tested Principles are retained and the impact intensity is within a range specified by adjustment limits Adjustment range can be adjusted to any given range values.

When achieving the object according to the invention according to claim 1, three features play a special role Role:

• - The adjustment of the impact intensity should be effected within the specified adjustment limits solely by changing the value of the power surge S _{I, Σ} . The change in the value of the power surge S _{I, Σ} can be changed by changing one or more of the power surge parameters
• - resulting spring constant C _RT ,
• - spring preload s _v (or spring preload F _V ) or
• - Additional forces F _Z
• - angular frequency ω

be made, the additional forces are characterized in that they are part of during their of the vibration path definable effective path either withdraw energy from the vibration system, which is discharged to the outside, or to supply the oscillating system with energy which is supplied from the outside becomes.

The notes in "Note 5" are important for the following statements:

• - In contrast to the known compression systems, in which the resulting centrifugal torque M _{R has} to be set to a very specific value in order to set a certain impact intensity, the resulting centrifugal torque M _{R is} (at least) to that increased value M _RM + ΔM _R in the invention (in note 5), which is required for the maximum impact intensity required at the upper range limit of the specified adjustment range.
• - For everyone within the specified adjustment range below the maximum possible impact intensity The resulting centrifugal moment has excess values.
• With regard to the shock intensity that can be generated, these excess values are not noticeable as long as as they are not activated.

It is now the task of the controllable power surge S _{I, Σ} to activate the part required by its respectively set value from the excess value of the centrifugal torque, ie to adapt the phase angle of the excitation force, based on the oscillating movement, in such a way that the motor Antriebseinrich device pro Rotation of the unbalance body that energy is removed, which must be released with each impact, depending on the impact intensity. Since the value of the power surge S _{I, Σ} can be changed continuously, the impact intensity can consequently also be adjusted continuously.

Of course, there is also the requirement that the driving motor or motors do this drive torque required for the unbalance body.

In independent claim 2, the findings from formula [10], such as z. B. are also expressed in the comments 1, 2 and 5a), used to improve those known compression systems me, in which a change in the impact intensity is carried out by a feasible adjustment of the resulting centrifugal moment M _R during the rotation of the unbalance bodies.

Accordingly, an adjustability of the resulting centrifugal torque M _R (adjustability of the nominal vibration amplitude A _s ) which can be carried out using known means is combined with the instruction, in addition to that which results from the expression "C _{RT *} A _S / ω" in formula [10] Power surge component to add a second power surge component, which by corresponding adjustments to one or more of the power surge parameters "resulting spring constant C _RT ", "preload force F _Z " (or spring preload path s _v ) and "additional force F _Z "can be generated.

In independent claim 3, the fact that the power surge S _{I, Σ is influenced} inversely proportional by the angular frequency ω, is applied to the compression systems in which the resulting centrifugal torque M _R is fixed at a constant value, and where only the angular frequency ω is variable. Accordingly, the influence of ω on the power surge S _{I, Σ is to} be compensated for by a corresponding change in the opposite direction of one or more power surge parameters C _RT , s _v and F _Z or in such a way that a certain predeterminable control variable, e.g. B. the speed difference Δv _s or Δv _a determining the pulse I _s is adjusted to a predeterminable value. (see also remark 10). The independent claim 3 can also be interpreted in such a way that the required transferable pulse I _{a, ü is} adjustable with the existing setting of arbitrary values of one or more of the abovementioned surge parameters by setting a correspondingly predetermined value for the angular frequency ω.

In independent claim 4, the teaching that can be gathered from formula [10] is implemented that the variable impact intensity can be regulated well by varying the force impact parameters. In claim 4, a control device is provided for a compression system equipped with a directional oscillator with a constant resulting centrifugal moment M _R (that is to say with a constant nominal amplitude A _s ), by means of which the adjustment of one or more of the values of the force shock S _{I, Σ} co-determining parameters C _RT , s _v , F _Z and ω a control or regulation of a predeterminable physical quantity can be carried out. The physical quantities can be those that are directly related to the impact intensity to be changed, such as. B. the size Δv _{s of} the pulse I _s = m _s Δv _s or the size Δv _{a of} the pulse I _a {= m _{a *} Δv _a / (1 - q)}. As a physical variable to be controlled, however, it is also possible to provide a variable which is indirectly related to the impact intensity to be changed, such as, for. B. the size defined in DE-OS 44 34 687.5 of the impact phase angle β _impact or a functionally related size. The dimensioning of the value of M _R to be assumed here with a certain excess value has already been explained in connection with claim 1, or also in "Notes 5 and 11".

A special meaning of this solution for the impact phase angle β _impact named in DE-OS 44 34 687 can be explained as follows: In the mentioned DE-OS it is shown that the impact phase angle β _impact when using an imbalance Richtschwinger force-excited movement generation system and with a constant value for the centrifugal moment M _{R can} also be controlled only by changing the angular frequency ω of the unbalance body. Since in this control method a control of the value of the transmittable pulse I _{a, ü is} inevitable, the application of the teaching in claim 4 represents the prerequisite still to be created in order to implement the special teaching from the mentioned DE-OS in practice to be able to.

In claim 5, the teaching is defined, the value of the spring preload s _v from s _v = A _s (which corresponds to the prior art) to at least s _v = 2 A _s , but better to s _v 3 A _s (or even higher) ) and at the same time lower the value of the resulting spring constant C _RT , measured at the state of the art, to at least 50%, but better still to below 33%. In the present invention, this results in an almost unlimited design latitude in the directions shown (in contrast to the prior art, as described in "Note 4"). At the same time, the following improvements are achieved with these minimum dimensions or open dimension directions:

• - The value of the frequency ratio η is increased,
• - The value of the insulation efficiency ζ is increased (see "Note 8").
• - The efficiency ξ of the impact intensity change is increased (see "Note 6"), and
• - The dimensioning proposals also include the one described in "Remark 7a" serious practical hindrance to the inventive principle (which, moreover, the possibility it is satisfactorily eliminated.

Since in the conventional compression systems which have been customary and become known to date and which work with the resulting centrifugal moment M _R which cannot be adjusted during the rotation of the unbalance bodies, an adjustment of the spring preloading path greater than 1.5 mm is not customary and while maintaining the usual spring constant C _RT cannot be successful either, a conventional compression system that works successfully with a spring preload s _v greater than or equal to 2 mm indicates a value for the spring constant C _RT that is at the same time lowered, and thus indicates the use of one of the teachings of the present invention.

With the dimensions prescribed by claim 5, the spring preload F _V = C _{RT *} s _v [1] should not be changed per se. All that is changed is the way in which they are generated or the ratio of the values of C _RT and s _v . In principle, the following applies: A compression system implemented according to the invention can be continuously improved in several respects by continuously increasing the value of s _v while simultaneously reducing the value of C _RT . The dimensioning trend recommended here is surprisingly in contrast to the statement made in "Note 4" (in paragraph 2) with regard to a possible increase in the impact intensity in compression systems according to the prior art.

With the dimensions "s _v 2A _s " prescribed in accordance with claim 5, those improvements should also be achievable which serve for a more uniform transmission of the forces of the force shock S _{I, Σ} over all the oscillating springs ( 142 ) involved. It is the same improvement, for which the features of claims 6, 7 and 8 are provided exclusively.

In claims 6, 7 and 8, the invention is developed as follows: It is a problem with a vibrating table, which is generally supported by at least 4 springs, the forces of the impact shock S _I [With its change, the impact intensity over the entire surface of the base plate seen the same effect is to be changed] in equal proportions over all involved vibration springs. The desired equality is disrupted by a variety of factors, such as: B. thereby

• - that the individual springs have different spring constants despite the same size,
• - That the organs against which the springs are supported in different ways due to wear or Forces or heat are deformed or deformable,
• that the height settings of the springs are also determined by tolerances in mechanical production,
• - That by the necessary power surge adjustment device even when adjusting Adjustment tolerances are generated.

In the present invention, these problems are solved differently according to the teaching of claims 6, 7 and 8:
In the first variant of the solution according to claim 6, the instruction is given either for the force impulse forces, in which the force impulse forces derived from a spring deformation with the size F _e per spring are supported against the foundation by mechanical organs, either the force impulse forces to produce with only one centrally attached spring, or to dimension the spring preload s _v as large as possible, at least to s _v 2 A _s S, but better to s _v 3 A _s or even larger, in order to make the springs "softer" and thus the spring forces F _e developed by them to be independent of the property tolerances influencing the spring force. At the same time, the value of the spring constant C _RT must be reduced proportionally with the increase in s _v . Of course, this demand for a reduction in the value of the spring constant C _RT also supports the suggestion made in "Note 6" to improve the insulation efficiency ζ.

It is assumed here that most of the force deviations ΔF _e from the force impulse force F _e to be transmitted in the same size per spring result from length deviations Δl. So: ΔF _e = Δl _* C _Fed (with C _Fed as the spring constant of the individual spring). In contrast, the nominal force impulse force F _{e is} defined by the spring preload s _v to: F _e = s _v C _Fed . If the ratio ΔF _e / F _{e is formed} , the result is: ΔF _e / F _e = Δl / s _v , or ΔF _e = F _{e *} Δl / s _v . [22]. As a result, the force deviation ΔF _e becomes smaller the larger the spring preload travel s _v is given for a given Δl.

In the second and third solution variants according to claims 7 and 8, the uniformity of the loading impact of the vibrating table by the force impulses ensures that the work spaces the adjusting elements which drive the power shock springs with an equally large pressure of one which drives them Pressure fluids are supplied.

In claim 9, a special type of power surge adjustment device is presented (see also Fig. 2). Here a combination of the mode of action of two different types of springs is carried out:
In addition to the power springs of the power adjustment devices, a second type of spring with position springs is used. The position springs with their very low spring constants only serve to support the weight of the vibrating table, while at the same time they can also take on tasks for the horizontal positioning of the vibrating table. Here, for. B. 4 compression or thrust springs are used, which can have an adjustable mounting arrangement, so that in the event that no other forces directed via the power springs attack the vibrating table, the vibrating table in a predetermined spatial position is aligned in such a way that, in the case of rotating imbalances, the abutting surface of the vibrating table is aligned parallel to the abutting surface of the mass to be bumped m _a and (based on a specific phase of the course of the oscillating movement) with a predetermined parallel distance.

For practical use, it is important that the build-up and breakdown of the force impulses and also the switching on and off of the surge operation can be carried out quickly. Together hang is hereby emphasized that the compression system according to the invention operated in this way should be that also between the compression processes to be finished one after the other Concrete blocks, which are created by filling the mold box in succession, the unbalance bodies should be able to rotate continuously at a predetermined speed, even at a very high speed, without that there are bumps against the base plate.

For this purpose, it is provided according to claim 10 that the power surge adjusting device by means of the feasible lifting function between the periods of the compression processes for behind Concrete blocks manufactured by one another lower or raise the average center of gravity GE of the vibrating table is able to perform such that it prevents an impact or can be brought about.

The shift to be carried out in such lifting or lowering operations means a displacement of the mass m _{s of} the vibrating table with respect to its average center of gravity and thus essentially determines the achievable times for switching the shock processes on and off. The bigger problems arise when trying to shorten the times for turning off the bumps.

The shortening of the turn-off time, it requires, after a further embodiment of the invention according to claim 11, that not only the force of gravity, but a further, additional force to the downward motion of the mass m _s is made available. The additional force is to be derived directly or indirectly from forces developed by the actuators of the power surge adjustment device, for which two different solutions are provided:
According to claim 12 it is provided to use the combination of two types of springs described in claim 9. When the surge mode is switched on, the position springs which support the gravity of the mass m _{s are} first relieved and then pre-tensioned in the opposite direction (upwards). This preload is caused by forces which are additionally conducted via the power shock springs and are generated by the actuators. As soon as a reduction of the forces generated in the power springs is carried out when the surge mode is switched off, the additional forces created in the position springs by the pretension come into play in that they contribute to accelerating the mass m _s during its downward movement.

In claims 14 and 15 it is shown that an adjustment of the value of the power surge also by generating forces which slow down or accelerate the oscillating movement can be led. The generation of braking forces is particularly simple and advantageous. For Generation of braking forces can be two cooperating power coupling devices, each with the Vibration table or connected to the machine frame, so influenced that during the Vibrating movement of the vibrating table forces are generated between them, which influences the force shock sen.

It can be frictional forces, or else hydraulic damping forces which, for. Belly can be generated using the principle of electrically controllable viscosity. With a hy drastic damping by throttling a delivery volume derived from the oscillating movement stromes can generate directional throttle pressure by using check valves respectively.

A particularly advantageous use of the invention results according to claim 16 when the counterblow method is used. In this case, the shock loading of the foundation is reduced in a special way: In addition to avoiding the introduction of impacts via the impact bar into the foundation, in this case there is the advantageous effect that, according to the invention, the mass m _a of the vibrating table against that Foundation supporting springs can be executed with very low spring rates.

Claim 20 describes (see FIG. 3) a special type of directional vibrator equipped with 4 unbalanced bodies, each unbalanced shaft being driven by its own motor. This type of drive has the advantage that the drive power does not have to be carried out via gears. When two groups are formed, each with two oppositely synchronous and self-synchronizing imbalance bodies, the synchronous and synchronous running of both groups with respect to the direction of vibration is ensured by means of a forced synchronization, whereby only two unbalance shafts from different groups have to be synchronized.

In claim 21, the note given in "Remark 12" is implemented: Accordingly, for compression systems which are designed according to the teaching of one of claims 1 to 4, the excess portion can be dispensed with in part or in whole in the case of resulting centrifugal moments to be dimensioned with an excess value will be provided, provided that the impact of the impact of the power surge using additional forces F _{Z is} involved.

In independent claim 25, one with the "bumper strip principle or with the counterblow principle" working method according to the invention presented.

In method claim 26 , the role of the power surge as a manipulated variable in the control of predetermined other physical quantities, such as. B. the speed difference Δv _{s of} the pulse I _s = m _s Δv _s , or the impact phase angle β _{impact shown} .

The invention is explained using an example of an embodiment with features according to claims 7, 9, 10 and 13 in FIGS. 2 and 3. FIG. 2 schematically shows a compression system which represents a further development of that shown in FIG. 1a. For this reason, elements marked with numbers 1a in Fig are simplicity already in Fig.. 2 marked with the same numbers listed records again, the elements unless exercising the same functions. All elements in FIG. 2 which are provided with new functions in comparison to FIG. 1a are provided with identification numbers <200.

In FIG. 2, 102 has two hydraulically operated Differenti are used alkolben 202 in the device base or the machine frame, which divide the respective cylinder into an upper working chamber 206 and a lower working space 204. An upper compression spring 212 (= return spring) and a lower compression spring 210 (= power shock spring) are mounted on the extended piston rod 208 in such a way that the forces which develop during their deformation are supported on the one hand against the piston rod and on the other hand against a plate 220 , which is part of a frame-shaped vibrating table 140 .

Two springs 218 (= position springs) with very low values for the spring constant serve to support the weight and at the same time provide spatial guidance for the vibrating table 140 .

The two upper working spaces are connected via a pressure compensation line 230 and connected via a line 270 to a directional valve 254 , which in turn has a connection to a controllable or regulatable pressure source 256 for the pressure p2. The two lower workrooms are connected via a pressure compensation line 240 and connected via a line 272 to a directional control valve 250 , which in turn has a connection to a controllable or regulatable pressure source 252 for the pressure p1.

The situation shown in FIG. 2 corresponds to that basic position of the system in which the surge mode is switched off. The unbalanced bodies 144/144 'rotating in opposite and synchronous directions are still in rotation and set the vibrating table 140 in a directional vertical oscillating movement with the real amplitude A _real . In the phase shown in FIG. 2, in which the vibrating table 140 has reached the highest point of its oscillating movement, there is a distance 280 between the abutting surface 150 of the vibrating table and the abutting surface 122 of the base plate 120 .

The differential pistons 202 are also in their basic position and are hydraulically clamped immovably. In the illustrated top position of the vibrating table 140 , which is brought about by the unbalance vibrator, the upper compression springs 212 are not deformed and are not loaded. The lower compression springs 210 have a low deformation with a provided low spring constant C _ks . The operation of the compression system according to Fig. 2 is as follows:
In order to switch from the basic position shown to the compression mode, the surge mode is switched on. This takes place in that after switching over the valve 254 in such a way that the line 270 is connected to the output R, the valve 250 is brought into the switching position in which a connection is established between the pressure source p1 and the line 272 . As a result, the differential pistons 202 move upward and, as the distance 280 is continuously reduced, the lower compression springs 210 are deformed . The upper compression springs remain undeformed.

The deformation of the lower compression springs 210 , and thus also the resulting size of the "resulting" spring preload path s _v and the size of the preload force F _V , is proportional to the set pressure p1. The power surge S _{I, Σ} which is reached after the upward movement of the differential pistons 202 has ended and which is proportional to the level of the pressure p1 determines the size of the transmittable pulses I _{a, ü} , provided that this is due to the mass m _{s of} the vibrating table and the resulting centrifugal moment M _R certain pulses I _s allow this.

During the compression process, the impact intensity can be changed in a predetermined manner by varying the pressure p1. The initiated compression process is ended by switching off the surge mode. For this purpose, after switching valve 250 in such a way that line 272 is connected to output R, valve 254 is also switched to the position in which there is a connection between pressure source 256 and line 270 . This results in pressurization of the upper working spaces 206 , forcing the differential pistons 208 to move downward.

The downward movement first relieves the pressure on the lower compression springs 210 and then on the deformation of the upper compression springs 212 . The spring force generated in this way gives the vibrating table 140 an acceleration which acts in addition to the acceleration due to gravity, with the aid of which a desired rapid increase in the distance 280 occurs.

At this point, the statement valid for all possible embodiment variants of the invention is made that the term spring preload travel s _v used in the present description is defined according to [1] by the relationship: s _v = F _V / C _RT . The spring preload force F _{V is} the force which is supported as a force generated by spring deformation against the mass m _s of the vibrating table on the one hand and against the machine frame or the foundation on the other hand during the impact operation. Because of the possible large number of springs involved, the spring preload force F _{V represents} a “resulting” force. As can be seen in FIG. 2, the resulting spring force F _{V can} also arise from the fact that with increasing pressure load on one spring 210, other springs 218 simultaneously be relieved. It can be shown that a resultant spring constant C _RT can also be defined in this case, so that a change ΔF _{V of} the spring preload force is generated with a stroke ΔH performed by the differential pistons 202 during the impact operation to: ΔF _V = ΔH C _RT .

In the case of the example shown in FIG. 2, the spring preload path s _{v could} also be defined as follows:
With the base plate 120 removed, the differential pistons 202 are raised by an amount that adjusts the desired spring preload F _V , in such a way that the abutting surfaces 150 of the vibrating table are higher by the amount s _v than the height of the abutting surfaces 122 of the base plate that collide with the vibrating table 120 when the base plate is placed (as shown) on the baffle strips 104 .

In Fig. 3, a with 4 unbalanced shafts 302 to 305 directional Unwuchtvi brator 300 is shown with its drive device, as he stems at the vibrating table 140 of the compression system according to FIG. 2 instead of the two unbalanced bodies 144 shown there, driven by two motors / 144 ′ could be appropriate. In order to avoid gearbox problems, each of the 4 unbalanced bodies is driven by its own three-phase motor 322 to 325 per 312 to 315 . The unbalanced shafts are received in bearings 330 , via which they transmit their centrifugal forces to a vibrating table 335 , which, for. B. could be identical to the vibrating table 140 in FIG. 2.

The unbalance bodies are combined into two groups 312/313 and 314/315 , the unbalance bodies of each group rotating in opposite directions and synchronously and, after the motors have started after self-synchronization has been carried out, form a constant maximum resulting centrifugal torque M _R / 2. It can be seen from the direction of rotation indicated by arrows 340 , 342 that the directions of rotation in the right group are reversed in comparison to the left group.

A mechanical forced synchronization is provided between the two inner unbalance bodies, which is implemented by two toothed belt wheels 340 , 342 and a toothed belt 345 that wraps around both toothed belt wheels. The forced synchronization created in this way ensures that the two self-synchronizing groups in turn run synchronously with one another. Under normal circumstances, the belt drive therefore has little or no power to transfer from one group to another.

When installing the toothed belt transmission, care must be taken that the two unbalance bodies 313 and 314 are given a relative position offset by 0 °, so that both groups are also synchronized with regard to their direction of oscillation.

It goes without saying that the inventive principle can also be achieved by other variants of connecting gears ben can be embodied. Because of the low power to be transmitted, it can alternatively be pre-read hen that only one of the two unbalanced shafts of different groups relative to the other its rotational movement is corrected by electrical means. This correction can be done easily with the help of a phase of an asynchronous three-phase current by means of direct current application Torque generated braking torque take place. Instead of two synchronized groups, three could be or more groups can be provided for synchronization.

Claims (28)

1. compression system for the compression and molding of molding compositions in mold recesses from mold boxes to moldings on concrete block machines in the main compression phase,

• - With a support springs ( 210 , 218 ) with a resulting spring constant C _RT against the machine frame ( 102 ) or against the foundation supported vibrating table ( 140 ) with the mass m _s , with which mass m _s with impacts with a second mass m _a pulses I _s (= m _{s *} Δv _s ) can be delivered to the second mass, the size of the pulses influencing the achievable compression result and the speed difference Δv _{s being} the difference in the speeds of the mass m _s before and after the impact .
• - With a connected to the vibrating table, working with the angular frequency ω unbalance vibrator ( 144 , 144 ') with a maximum resulting centrifugal torque M _R for generating directional vibrations with the nominal vibration amplitude A _s = M _R / m _s .
• with a motorized drive device for supplying drive power for the rotatable unbalanced bodies,
• - With a mass system with the total mass m _a composed of partial masses of different organs, which is able to take over a transferable impulse I _{a, ü} [= m _a Δv _a / (1 - q)] from the mass m _s and whereby to organs provided with partial masses belong to at least one base plate ( 120 ), one molding box ( 124 ), one concrete block-concrete quantity and one load body ( 128 , 130 ),
• with a transfer of the transferable impulse I _{a, ü} during a shock, which the vibrating table mass m _s executes during its upward swinging movement against the mass m _{a of} the mass system,
• - With an adjustment device for adjusting a manipulated variable influencing the level of the impact intensity, with which adjustment the values of the impact intensity can be set to predeterminable values within a predeterminable adjustment range or value range, characterized by the combination of the following features:
• a) The mass m _a can be placed on baffle strips ( 104 ) which are supported against the machine frame ( 102 ) or against the foundation, which at the same time defines the lowest spatial position of the base plate at which the joints between the masses m _a and m _s are essentially executed,
• b) an adjustment of the value of the transferable pulse I _{a, ü} and thus an adjustment of the shock intensity is brought about by adjusting an actuator ( 202 ) or at least one actuator adjusting the values of one or more power surge parameters as there are:
• - Resulting spring constant C _{RT of} all support springs involved,
• - spring preload s _v as a measure of deformation of springs clamped between the vibrating table on the one hand and the machine frame or foundation on the other,
• - spring preload F _{V of} all support springs involved,
• - Additional force F _Z as a force accelerating or decelerating the mass m _s , the energy converted by the additional force F _Z during its effective path being withdrawn and removed from the kinetic energy of the oscillation system of the oscillating table vibrating with the mass m _s or being supplied by an external feed ,
• - angular frequency ω,
• c) the resulting centrifugal torque M _R is permanently set to a maximum value which is required in order to be able to set the maximum necessary value of the impact intensity at the upper limit of the predetermined adjustment range.

2. Compression system according to the preamble of claim 1, characterized by the combination of the following features:

• a) The unbalance vibrator ( 144 , 144 ') is provided with at least two groups of unbalanced bodies, the angular position of which is assumed in the rotation relative to one another is the manipulated variable, with the adjustment of which the values of the resulting centrifugal torque M _R , the nominal amplitude A _s and the impact intensity are adjusted.
• b) the adjustment of the value of the transferable pulse I _{a, ü} , and thus the adjustment of the shock intensity, is in addition to the effect of the adjusted nominal amplitude A _s on the adjustment of the shock intensity additionally effected by means of actuating an actuator ( 202 ) or at least one control of the adjustment of the values of one or more power surge parameters, as there are:
• - Resulting spring constant C _{RT of} all support springs involved,
• - spring preload s _v as a measure of deformation of springs clamped between the vibrating table on the one hand and the machine frame or foundation on the other,
• - spring preload F _{V of} all support springs involved and
• - Additional force F _Z as a force accelerating or decelerating the mass m _s , the energy converted by the additional force F _Z during its effective path being withdrawn and removed from the kinetic energy of the oscillating system of the oscillating table oscillating with the mass m _s or being supplied by an external feed ,

3. compaction system for the compression and molding of molding compounds in mold recesses from mold boxes to moldings on concrete block machines in the main compaction phase,

• - With a support springs ( 210 , 218 ) with a resulting spring constant C _RT against the machine frame ( 102 ) or against the foundation supported vibrating table ( 140 ) with the mass m _s , with which mass m _s with impacts with a second mass m _a pulses I _s = m _s Δv _{s can be} delivered to the second mass, the size of the pulses influencing the achievable compression result and the speed difference Δv _{s being} the difference in the speeds of the mass m _s before and after the impact.
• - With a connected to the vibrating table, working with the angular frequency ω unbalance vibrator ( 144 , 144 ') with a maximum resulting centrifugal torque M _R for generating directional vibrations with the nominal vibration amplitude A _s = M _R / m _s
• with a motorized drive device for supplying drive power for the rotatable unbalanced bodies,
• - With a mass system with the total mass m _a composed of partial masses of different organs, which is able to take over a transferable impulse I _{a, ü} [= m _a Δv _a / (1 - q)] from the mass m _s and whereby to organs provided with partial masses belong to at least one base plate ( 120 ), one molding box ( 124 ), one concrete block-concrete quantity and one load body ( 128 , 130 ),
• with a transfer of the transferable impulse I _{a, ü} during a shock, which the vibrating table mass m _s executes during its upward swinging movement against the mass m _{a of} the mass system,
• - With an adjusting device for adjusting the angular frequency ω of the rotation of the unbalance bodies to predeterminable values of ω. characterized by the combination of the following features:
• a) The resulting centrifugal moment M _R is fixed,
• b) in the case of values ω = ω (t) which can also be predetermined in their time behavior, the values for the transferable pulses I _{a, u can be} influenced by adjusting the values by means of the actuation of an actuator ( 202 ) or at least one actuator of one or more surge parameters, as are:
• - Resulting spring constant C _{RT of} all support springs involved,
• - spring preload s _v as a measure of deformation of springs clamped between the vibrating table on the one hand and the machine frame or foundation on the other,
• - spring preload F _{V of} all support springs involved and
• - Additional force F _Z as a force accelerating or decelerating the mass m _s , the energy converted by the additional force F _Z during its effective path being withdrawn and removed from the kinetic energy of the oscillating system of the oscillating table oscillating with the mass m _s or being supplied by an external feed ,
• c) At least one predeterminable physical quantity can be measured by means of appropriate measuring devices, the following being possible to be measured:
• - The change in speed Δv _s or Δv _a , as the difference in the vibration speed of the mass m _s or m _a before and after the impact,
• the impact phase angle β _impact according to a definition given in DE-OS 44 34 687,
• - Physical quantities which are functionally related to the change in speed Δv _s or Δv _a or to the impact phase angle β _impact according to the definition given in DE-OS.
• d) A control or regulating device is provided, with the aid of which one or more of the measurable physical quantities are controlled or regulated according to predeterminable values by adjusting the value of one or more of the power surge parameters with a constant or variable angular frequency ω.

4. Compression system according to the preamble of claim 1, characterized by the combination of the following features:

• a) The resulting centrifugal torque M _R is permanently set to a maximum value which is required in order to be able to set the maximum necessary value of the impact intensity at the upper limit of the predetermined adjustment range,
• b) an adjustment of the value of the transferable pulse I _{a, ü} , and thus an adjustment of the shock intensity, is brought about by adjusting the values of one or more power surge parameters by actuating an actuator ( 202 ) or at least one actuator, than there are:
• - Resulting spring constant C _{RT of} all support springs involved,
• - spring preload s _v as a measure of deformation of springs clamped between the vibrating table on the one hand and the machine frame or foundation on the other,
• - spring preload F _{V of} all support springs involved,
• - Additional force F _Z as a force accelerating or decelerating the mass m _s , the energy converted by the additional force F _Z during its effective path being withdrawn and removed from the kinetic energy of the oscillating system of the oscillating table oscillating with the mass m _s or being supplied by an external feed ,
• - angular frequency ω.
• c) Predeterminable physical quantities can be measured by means of appropriate measuring devices, the following being suitable as quantities to be measured:
• - The change in speed Δv _s or Δv _a , as the difference in the vibration speed of the mass m _s or m _a before and after the impact,
• the impact phase angle β _impact according to a definition given in DE-OS 44 34 687,
• physical quantities which are functionally related to the change in speed Δv _s or Δv _a or to the impact phase angle β _impact according to a definition given in DE-OS 44 34 687,
• - the angular frequency ω
• d) A control or regulating device is provided, by means of which one or more of the measurable physical quantities are controlled or regulated according to predeterminable values by adjusting the value of one or more of the power surge parameters.

5. Compression system according to one of claims 1 to 4, characterized in that

• a) either the value of the resulting spring constant C _{RT of} all the supporting springs involved is set such that it corresponds to a deflection path of s _o = 2 mm or greater, the deflection path s _{o being} defined by the deflection path of all (at the spring preload F _V in shock operation with the resulting spring constant C _RT involved) support springs when loaded with the weight of the mass m _{s of} the vibrating table,
• b) or that by the relationship s _v = F _V / C _RT definable spring preload s _v when performing the surge mode is set such that it with s _v 2 A _{s is} twice the value of the nominal vibration amplitude A _s or a larger value than 2 A _s , the spring preload s _{v being} set by the deformation of support springs ( 210 , 218 ) clamped between the vibrating table ( 140 ) on the one hand and the machine frame ( 102 ) or foundation on the other during shock operation and involved in the formation of the spring preload force F _v , and where C _{RT is} the resulting spring constant of all of the support springs involved in the generation of the spring preload force F _V during the impact operation,
• c) or that at the same time the deflection path s _{o is} approximately set to s _o = 2 mm or greater and the spring preload path s _{v is} either approximately set to s _v 2 A _s or greater or to s _v 2 mm.
• d) or that the spring preload s _{v is} set to 2 mm.

6. Compression system according to one of claims 1 to 5, characterized in that for the adjustment of the power surge a power surge adjusting device is provided with the following features:

• a) For the generation of the spring preload F _V a centrally acting or several individually acting power springs ( 210 ) are provided on the power adjustment device, which between the spring forces in the vibration table ( 140 ) introducing first support points and between the spring forces in the Machine frame ( 102 ) or second support points leading into the foundation,
• b) the adjustment of the values of the spring preload force F _V and the adjustment of the spring preload travel s _v is effected by adjusting the distance between the first and second support points,
• c) the adjustment of the distance between the first and second support points is effected by the adjustment of the distance between the second support points and the machine frame or the foundation,
• d) the spring forces delivered to the second support points are guided via mechanically operating adjusting gates, which adjusting members are involved in adjusting the distance between the second support points and the machine frame or the foundation,
• e) if two or more power shock springs are provided, the spring preload path s _v used during the shock operation is set to a value of s _v = 2 A _s or greater.

7. Compression system according to one of claims 1 to 5, characterized in that for the adjustment of the power surge a power surge adjusting device is provided with the features listed below:

• a) For the generation of the spring preload F _V a centrally acting or several individually acting power springs ( 210 ) are provided on the power adjustment device, which between the spring forces in the vibration table ( 140 ) introducing first support points and between the spring forces in the Machine frame ( 102 ) or second support points leading into the foundation,
• b) the adjustment of the values of the spring preload force F _V and the adjustment of the spring preload travel s _v is effected by adjusting the distance between the first and second support points,
• c) the adjustment of the distance between the first and second support points is effected by the adjustment of the distance between the second support points and the machine frame or the foundation,
• d) the spring forces delivered to the second support points are guided via adjustment elements ( 202 ) driven by a pressure fluid, which adjustment elements are involved in adjusting the distance between the two support points and the machine frame or the foundation,
• e) if two or more power shock springs ( 210 ) are provided, the uniformity of the loading of the vibrating table by the power shock forces is ensured in that the working spaces of the adjusting members ( 202 ) are supplied with an equal pressure of the pressure fluid.

8. Compression system according to one of the preceding claims 1 to 5, characterized in that for the adjustment of the power surge a power surge adjusting device is provided with the features listed below:

• a) For the generation of the spring preload force F _V and for the realization of the spring preload path s _v , a centrally acting adjusting member (e.g. hydraulic piston 202 ) or several individually acting adjusting members (e.g. hydraulic piston 202 ) are provided on the power surge adjusting device, which are driven by a pressure fluid,
• b) the working spaces of the adjustment members are connected to one or more fluid pressure accumulators serving as power springs, a pressure accumulator containing an energy-storing member in the form of an enclosed gas volume or in the form of one or more spring elements,
• c) the adjustment of the values of the spring preload force F _V or the spring preload path s _v is brought about by a change in the pressure of the pressure fluid,
• d) if two or more adjusting elements are provided, the uniformity of the loading of the vibrating table is ensured by the adjusting elements in that the working spaces of the adjusting gans are supplied with an equal pressure of the pressure fluid.

9. Compression system according to one of claims 6, 7 or 8, characterized in that in addition to the springs of the power shock adjusting device designated as power springs ( 210 ), a second type of spring of position springs ( 218 ) is provided, the task of which essential position-positioning of the vibrating table ( 140 ) is, in which the vibrating table by the position springs with the shock mode switched off and possibly with the simultaneous participation of power springs of the power shock adjusting device with rotating unbalanced bodies of the unbalance vibrator predetermined position of the vibrating table is aligned in such a way that the abutting surfaces ( 150 ) of the vibrating table are parallel to the abutting surfaces ( 122 ) of the mass to be bumped m _a and (based on a certain phase of the course of the oscillating movement) with a predetermined parallel distance. 10. Compression system according to one of claims 6 to 9, characterized in that a lifting function can be carried out by means of the power surge adjusting device, with which the definable average position of the center of gravity in the rotation of the unbalance body of the unbalance vibrator is displaceable in such a way that

• a) when taking a lower position, a shock contact of the shock surfaces of the vibrating table and the base plate takes place only together with a slight shock operation or is completely ruled out, with which the power shock forces in the power springs are substantially or completely reduced and with which the switching off of the Rush mode has occurred, and that
• b) when an upper position is reached, there is a full contact of the impact surfaces and thus the activation of the impact operation is brought about, and that
• c) after activation of the surge operation by further actuation of the power surge adjustment device, an adjustment of the values of the power surge can be carried out, the limit case of the non-adjustment of the values being provided for the further actuation to adjust the values.

11. Compression system according to claim 10, characterized in that in order to accelerate the downward movement of the vibrating table ( 140 ), which acts to deactivate the surge operation, a downward-acting additional force is used, which is preferably generated directly or indirectly by the actuators ( 202 ) of the power surge adjusting devices Forces is derived. 12. Compression system according to claim 10 or 11, in connection with a power surge adjusting device according to claim 9, characterized in that when the surge mode is switched on, the position springs ( 218 ) are first relieved and then in the opposite direction by means of the power springs and forces directed to the vibrating table are preloaded with additional forces, these additional forces being used as acceleration forces for the downward acceleration of the mass m _s of the vibrating table ( 140 ) when the surge mode is switched off. 13. Compression system according to claim 10, characterized in that one or more return springs ( 212 ) are provided, which can be supported on the one hand against the vibrating table ( 140 ) and on the other hand against such organs ( 208 ) by the actuators ( 202 ) Power surge adjusting device are moved up and down when the surge mode is switched on and off, deformations of the return springs being generated when the surge mode is switched off, and the spring forces caused by the deformations are used for the downward acceleration of the vibrating table. 14. Compression system according to one of the preceding claims, characterized in that an adjustment of the power surge parameter "additional force F _Z " is made in addition to the adjustment of other power surge parameters or as the only adjusted power surge parameters by a power surge adjusting device of the second kind, which is defined by the combination of the following features:

• a) An upper power coupling device connected to the vibrating table can be coupled to a lower power coupling device connected to the machine frame or to the foundation, such that coupling forces that can be predetermined in terms of their size by an actuating signal are coupled from one power coupling device to another whose relative movement derived from the oscillating movement of the oscillating table can be transmitted to one another,
• b) the coupling forces can either be transmitted only during the upward movement or only during the downward movement or both during the upward movement and during the downward movement,
• c) the product of the coupling force and the relative path corresponds to an energy which is withdrawn from the vibration system of the vibration table,
• d) at least the coupling force that can be transmitted in one direction of movement is used as a contribution to the power surge to be changed.

15. Compression system according to one of the preceding claims, characterized in that an adjustment of the power surge parameter "additional force F _Z " in addition to the adjustment of other power surge parameters or as a sole adjusted power surge parameter is carried out by a power surge adjusting device of two types, which is defined by the combination of the following features:

• a) An upper drive member connected to the vibrating table can be coupled to a lower drive member connected to the machine frame or to the foundation, such that during the downward movement or during the upward movement or both during the downward movement and during the upward movement of the upper drive member between the two Forces are transmitted through which energy is supplied to the vibration system of the vibration table,
• b) the magnitude of the forces transmitted between the two drive elements can be controlled or regulated by an actuating signal,
• c) at least the coupling force switched in one direction of movement is used as a contribution to the power surge to be changed.

16. Compression system according to one of the preceding claims, characterized in that the system constellation is optional

• - for a batten molding process or
• - for a counter strike procedure or
• - is set up for a method with a predeterminable transition from one method to another, and in the case of setting up the system constellation for a method with a predeterminable transition the lifting function of the power surge adjusting device is used to bring about the transition.

17. Compression system according to one of the preceding claims, characterized in that the Values of several power surge parameters in order to bring about a predetermined power surge are immediately changeable. 18. Compression system according to one of the preceding claims, characterized in that the Impact intensity and at the same time the angular frequency ω of the unbalance body rotation is adjustable. 19. Compression system according to one of claims 6 to 18, characterized in that the movements of the adjusting elements of the power surge adjusting device are controlled or regulated in coordination with the oscillating movement of the oscillating table in such a way that

• a) the first shock carried out after switching on the surge operation is provided with a predetermined impact intensity,
• b) and / or that the last impact carried out when the surge operation is switched off is provided with a predetermined impact intensity.

20. Compression system according to one of the preceding claims, characterized in that a special directional vibrator is provided, which is defined by the combination of the following features:

• a) Four unbalanced shafts ( 302 to 305 ), each with at least one of its own unbalance bodies ( 312 to 315 ) are each driven by its own drive motor ( 322 to 325 ),
• b) two groups ( 302/303 ; 304/305 ) of two counterbalance and synchronous and self-synchronizing imbalance shafts are provided,
• c) a forced synchronization is effected in such a way that both groups run synchronously and in the same direction in the direction of vibration,
• d) the forced synchronization is only established between two unbalanced shafts ( 303 , 304 ), namely between an unbalanced shaft of one group and an unbalanced shaft of the other group.

21. Compression system according to one of the preceding claims, characterized in that in the case of a resulting centrifugal moment M _R to be dimensioned with an excess value, the excess portion is partially or completely dispensed with, a force impact portion resulting from the use of additional forces F _{Z being} formed in the formation of the power surge is involved. 22. Compression system according to one of the preceding claims, characterized in that the spring preload F _V is essentially defined by the sum of all spring forces acting in the direction of vibration of such springs which are clamped between the vibrating table on the one hand and the machine frame or the foundation on the other, minus the for supporting the weight of the vibrating table from these springs. 23. Compression system according to one of the preceding claims, characterized in that the spring preload s _{v is} defined by the relationship s _v = F _V / C _RT , with F _V as the spring preload force as defined in claim 22 and with C _RT as the resultant spring constant of all springs involved in the generation of the spring preload F _V when the surge mode is switched on. 24. Compression system according to one of claims 6 to 8 in conjunction with claim 10, characterized in that adjusting members ( 202 ) of the power surge adjusting device for the generation of spring biasing forces F _V and at the same time for the generation of a lifting function for the on-off movement for the Shock operation is provided, and / or that support springs ( 218 ) involved in the generation of the spring preload force F _V are subjected to a deformation for the oscillating table ( 140 ) which is identical to the lifting movement of the lifting function. 25. Method for operating a compression system for the compression and molding of molding compounds in mold recesses from molding boxes to moldings on concrete block machines in the main compression phase using a baffle molding method and / or a counter-impact method,

• - With a support springs ( 210 , 218 ) with a resulting spring constant C _RT against the machine frame ( 102 ) or against the foundation supported vibrating table ( 140 ) with the mass m _s , with which mass m _s with impacts with a second mass m _a pulses I _s = m _{s *} Δv _{s can be} delivered to the second mass, the size of the pulses influencing the achievable compression result and the speed difference Δv _{s being} the difference in the speeds of the mass m _s before and after the impact.
• - With a connected to the vibrating table, working with the angular frequency ω unbalance vibrator ( 144 , 144 ') with a maximum centrifugal torque M _R for generating directional vibrations with the nominal vibration amplitude A _s = M _R / m _s .
• with a motorized drive device for supplying drive power for the rotatable unbalanced bodies,
• - With a mass system with the total mass m _a composed of partial masses of different organs, which is capable of transferring a transferable impulse I _{a, ü} (proportional to the product m _a Δv _a ) from the mass m _s and to the masses provided with partial masses Organs belong to at least one base plate ( 120 ), a molding box ( 124 ), a quantity of concrete block concrete and a load body ( 128 , 130 ),
• with a transfer of the transferable impulse I _{a, ü} during a shock, which the vibrating table mass m _s executes with its mass m _{a of} the mass system during its upward oscillating movement,
• - With an adjustment device for adjusting a manipulated variable influencing the level of the impact intensity, with which adjustment the values of the impact intensity can be set to predeterminable values within a predeterminable adjustment range or value range, characterized by the combination of the following features:
• a) the resulting centrifugal torque M _R is permanently set to a maximum value which is necessary in order to be able to set the maximum necessary value of the impact intensity at the upper limit of the predetermined adjustment range,
• b) an adjustment of the value of the transferable pulse I _{a, ü} , and thus an adjustment of the shock intensity, is brought about by the actuation of an actuator ( 202 ) or at least an actuating means of the adjustment of the values of one or more impulse parameters , as there are:
• - Resulting spring constant C _{RT of} all support springs involved,
• - spring preload s _v as a measure of deformation of springs clamped between the vibrating table on the one hand and the machine frame or foundation on the other,
• - spring preload F _{V of} all support springs involved,
• - Additional force F _Z as a force accelerating or decelerating the mass m _a , the energy converted by the additional force F _Z during its effective path being withdrawn from the kinetic energy of the oscillating system of the oscillating table oscillating with the mass m _s and removed or supplied from outside by a feed ,
• - angular frequency ω.

26. The method according to claim 25, characterized by the combination of the following features:

• a) One or more predeterminable physical quantities are measured by means of appropriate measuring devices, the following being possible to be measured:
• The change in speed Δv _s or Δv _a , as the difference between the vibration speed of the vibrating table mass m _s or the impacted mass m _a before and after the impact,
• the impact phase angle β _impact according to a definition given in DE-OS 44 34 687,
• physical variables which are functionally related to the change in speed Δv _s or Δv _a or to the impact phase angle β _impact according to a definition given in DE-OS,
• - the angular frequency ω
• d) A control or regulating device is provided, with the aid of which one or more of the measurable physical quantities are controlled or regulated according to predeterminable values by adjusting the value of one or more of the power surge parameters.

27. compression system for carrying out a method according to one of claims 25 or 26, characterized by the addition of any combined features of claims 5 to 24. 28. Compression system according to one of claims 1 to 4, characterized in that the exchange of compression surges between the mass m _s of the vibrating table and the impacted mass m _{a can be carried out} according to the baffle molding method and / or the counter-impact method.