EP0865327B1 - Adjusting device for an unbalance vibrator with adjustable centrifugal moment - Google Patents

Description

The invention relates to an adjusting device for adjusting the relative setting angle β of Imbalance vibrators with at least two pairs of partially unbalanced bodies that can be adjusted against each other. A special type of adjustment device is in the patent DE 40 00 011 or in the PCT / EP90 / 02239. For the subsequent description of the present invention simplifying the terms used in the last-mentioned publication of the partial unbalance body and the assigned to them partial centrifugal forces (or partial centrifugal force vectors), and the "pair" of partial unbalance bodies accepted. In contrast to the publications cited above, the relative positioning angle β subsequently defined in such a way that the value β = 0 ° of a zero oscillation amplitude and the Value β = 180 ° corresponds to a maximum vibration amplitude.

The relative setting angle β is theoretically defined between the partial centrifugal force vectors of the individual partial unbalance bodies of a "pair" of partial unbalance bodies. In practice you can use the relative setting angle β also define the partial unbalance body between features (e.g. geometric features) Pair, if the position of the center of gravity of the eccentric mass is known. The labeling "MR" is used for the reaction moments "MR", which with every unbalance revolution around the Rotation angle µ = 2π occurs twice as alternating moments on the shafts of the partial unbalance bodies [These alternating moments have a Sinoid course with two minimum and two maximum values per revolution of the partial unbalance body].

The average and unidirectional reaction moments that are calculated can by integrating MR over the rotation angle µ = 2π and then dividing the Integration values through 2π are called "MRQ". As the skilled person e.g. from the patent DE 40 00 011 can derive "these average reaction moments MRQ have an effect on one set relative positioning angle 0 ° <β <180 ° in such a way on the partial unbalance bodies of a pair that the Reaction moments MRQ of the one type accelerate the rotation of the partial unbalance bodies of the one type want and that the reaction moments MRQ of the other type the rotation of the partial unbalance body of the want to delay another kind. With a 4-shaft unbalance vibrator, this mode of action leads to each a motor assigned to only one shaft so that at an idle with a set relative angle 0 ° <β <180 ° working vibrator two motors in one motorized way and two Motors must work in a regenerative manner. At this point it is pointed out that for the term "unbalance moment" other terms such as e.g. "static Moment "are known.

The invention is particularly dedicated to the unbalance vibrators with a predetermined direction of vibration, which e.g. are used as ramming vibrators and in which at least four unbalanced shafts or partial unbalance bodies are present, which are rotatable in corresponding bearings of the vibrator frame are arranged. With these vibrators there is every unbalanced shaft or each unbalanced body a separate motor assigned without the interposition of a transmission. The serves Motor at the same time as a drive motor for the implementation of the useful power or friction power (screed friction and bearing friction with the ramming vibrator) and as an adjustment motor. Through this type of energy supply for the Partial unbalance bodies can be dispensed with otherwise customary gear transmissions. Hereby arise several advantages at the same time. Because of the dispensability of gear drives, these vibrators are said to be hereinafter referred to as "gearless vibrators with adjustable unbalance moment".

The motors that are used with the invention can be hydraulic motors, which normally can work both as motors and pumps, act or also around electric motors. The hydraulic motors are driven by the volume flow of one Fluid medium (e.g. hydraulic oil), whereby the volume flow must be generated by one or more Pumps that are driven by one or more engines (e.g. diesel engine).

The closest prior art to the invention is characterized by the publication DE-OS 43 01 368 with the configurations shown in Figures 1 and 4: In Figure 1 is a hydraulic operated "gearless vibrator" with adjustable unbalance moment shown with the first Partial unbalance bodies associated with first motors 103 and 104 and the second partial unbalance bodies associated second motors 107 and 108. The first two motors are parallel and supplied with the same inlet pressure by one generated by the adjustable pump 114 Volume flow. The two second motors are each connected to a first motor by means of a Series connection connected. It is a so-called open circuit of the fluid medium.

The adjustment range for the adjustment of the unbalance torque is limited to an angle 0 ° ≤ β ≤ 90 °. The vibrator shown is provided with the ability to mirror the synchronous movement To be able to maintain the angle of rotation of the partial unbalance bodies of the same type, even under the influence of disturbing forces to be expected in general, but at least in the adjustment range at which the maximum unbalance torque is adjustable. This ability is seen as derived from the Effects of those alternating moments which are generated by the reaction moments MR and which is also responsible for the development of the average reaction moments MRQ are. In the cited publication nothing is said about the behavior of the stability of the mirror image Synchronous running of the partial unbalance bodies of the same type each time a different one is conceivable Type of control for the angle β for an adjustment range 90 ° ≤ β ≤ 180 °. Upon closer examination The configuration shown can be used to demonstrate that when working with the maximum Unbalance moment (which is more the normal case in the intended field of application of the invention) Taking into account the "total pressure" the first engines more than two and a half times as much as that second motors. The "total pressure" is the one for the life of the motors decisive sum of inlet pressure and outlet pressure at the engine.

In addition to the extremely asymmetrical load on the motors, the vibrator shown has a additional disadvantage to consider that in order to achieve comparably large resulting unbalance moments the partial unbalance moments of the partial unbalance bodies are dimensioned larger than normal have to. This leads to unnecessarily increased bearing forces and reaction torques MRQ.

In the vibrators described with FIGS. 1 and 4, methods for influencing the Motors used to set a predetermined relative pitch angle β, with which in fact an adjustment range from β = 90 ° to β = 180 ° cannot be developed. As will be shown later, suffer the processes described above include that they are not the most important in practice Influencing the bearing friction performance and the useful performance was taken into account.

The following publications are of interest for describing the general state of the art:

Patent DE 40 00 011: What is remarkable is a closer examination of the circuit shown resulting fact that the throttling shown in Figure 1 of the flow through motor 116 Volume flow with the help of the pressure relief valve 124 can not lead (starting from a Position in which the resulting unbalance moment has the value zero) the relative positioning angle β to change in such a way that the resulting unbalance moment increases. To really get this effect it would be necessary to be able to use the function of element 124 to that a pressure increase takes place between the input and output of the engine 116 while at the same time Motor 114 between inlet and outlet a decrease in pressure takes place. For fulfillment the desired function should also be realized in this case, the condition that the Input from engine 1 14 measurable pressure is greater than the pressure measurable at the input of engine 116. This requirement alone (inevitably with the same large volume flows through both motors) is not achievable, since both volume flows are taken from a common source (122). Figure 1 in fact, it serves rather to describe the terms used.

Patent DE 41 16 647: Here an adjustable gearless vibrator with electric motors is shown, each motor is assigned its own electronic control device. It exists for every engine a measuring device by means of which the relative angular position of all partial unbalance bodies relative to one another can be measured continuously. The angle of rotation of a first partial unbalance body is as The reference position is defined and the angles of rotation of the remaining three partial unbalance bodies are called relative Angle measured with respect to the first partial unbalance body. With this solution, the individual Regulation of the angle of rotation of each partial unbalance body achieves that in addition to the adjustment of the Given the relative positioning angle β, the mirror-image symmetrical angle of rotation position at the same time is maintained between the partial unbalance bodies of the same type. This solution is not only not suitable for use with ramming vibrators due to the enormous effort involved. The one shown The solution is a good example of the variety with which the 4 motors can be loaded adjustable gearless vibrator can be done.

DE-OS 44 07 013: This document contains a reference to the use in gearless Vibrators. However, the corresponding remark on page 6, lines 3 to 8 only provides information to technical details that are already known from DE-OS 43 01 368. It is also noted the fact that claim 3 does not relate to gearless vibrators. Already the preamble of this claim excludes the application to gearless vibrators because the Rotors of the adjustment motors are each to be connected to more than one partial unbalance body. In addition, one can infer from the characterizing part of claim 3 (first feature) that the adjustment motors cannot be drive motors at the same time.

DE-OS 44 25 905 provides a contribution to a state of the art as it was later published: Here, a solution is described with the help of which, in particular in the case of gearless vibrators which one can adjust the resulting unbalance moment with additional measures Can force synchronous running from that relative angle of rotation which is definable between the partial unbalance bodies of the same kind. This contribution does not give any indication of the solution of the existing Task with the present invention, but he points to the problem of compliance with the Synchronous running of the relative rotation angle between the partial unbalance bodies of the same type.

It is the object of the present invention, the state described by DE-OS 43 01 368 Improve technology for use with gearless vibrators using hydraulic motors or are driven by electric motors and the resulting unbalance moment are adjustable. The goal of the improvement is to achieve 4 goals: at least if it has been achieved Setting the resulting resulting unbalance moment and maximum adjustable for the solution found with the delivery of high useful output (in the case of ram vibrators via the ram plank in the Soil) should at least at a set maximum unbalance moment (which in practice the most of the work is) a load of all four motors of the same size can be achieved. In addition it should be possible to use hydraulic motors in compliance with this condition use the pumps to be used in both open and closed circuits. The The use of closed circuits can bring advantages, for example, through the possible ones Type of circuit. For example, when using open circuits it may be advantageous to to be able to select a larger number of pump types.

Furthermore, with the improvement, the overdimensioning necessary in the prior art Partial unbalance moments of the part unbalance bodies are avoided (avoidance of unnecessarily large ones Bearing forces). This requires the possibility of setting relative positioning angles also in the range β = 90 ° to β = 180 °. After all, the desired solution is also to create an uncomplicated and Robust vibrators enable what is the property of the parallel in the invention Reflection applied to two motors.

With regard to ensuring the maintenance of the given relative adjustment angle β and the relative angle of rotation between the partial unbalance bodies of the same type, the task is as follows: The necessary relative angle of rotation must be securely held, at least for that adjustment range of the relative -Position angle β, in which a maximum can be set for the resulting unbalance moment, because a significant working range of the vibrator is seen in this adjustment range. In the event of asymmetry of the mirror-image synchronous relative rotation angles (which are present between the partial unbalance bodies of the same type), cross vibrations which are not permitted are generated. The improvement by the solution according to the invention is also expected to be able to continuously drive through that angular range which lies between the relative actuation angle β = 0 ° and that relative actuation angle β _max at which the maximum unbalance torque is set.

An essential element of the improvements that are required with the task and with the inventive solution are now achievable based on the discovery of the significant disadvantage of the extreme asymmetrical loading of the motors, as is the case in the prior art (according to DE-OS 43 01 368) arises. In practice, this leads to a frequently necessary exchange of motors and / or necessary oversizing of the motors and thus also increases the effort. When evaluating the graphs from FIGS. 5 and 6 of DE-OS 43 01 368 and from FIG DE-OS 44 07 013 does not yet give any indication of the asymmetrical loads. A good It is possible to assess the loads on the motors by adding (superposition) the Reactive powers and active powers that act on the motors. This principle is getting closer described in connection with FIG. 2 of the present invention.

The solution to the problem is defined in the independent claims 1 to 4. Further advantageous Further developments of the invention are described in the subclaims.

When searching for the solution to the task, it was necessary to consider several criteria at the same time according to the task at hand. This fact is mentioned again below: Symmetrical loading of the motors at least with the maximum unbalance torque set and the vibrator's ability to move through the angular range from β = 0 ° to β = 180 °: With reference to the principle of superposition mentioned in the description of FIG. 2 of the present invention, the skilled reader should develop an idea of the circumstances, such as with a gearless vibrator according to the cited state the technology (Figure 1 in DE-OS 43 01 368) the extremely asymmetrical loads on the motors come about in detail.

The representation of the course of the differential pressures or the differential torques or the differential powers according to the diagrams in Figure 2, when using the Superposition principle and taking into account the special type of configuration of Pumps (in the case of a hydraulic solution) and motors represent a necessary one first inventive step in the development of the inventive solution. Only on this In this way two "tools" or "aids" are created, with the help of which both disadvantageous loading of the motors in the prior art as well as the favorable loading who can assess engines in the inventive solution.

It is first reminded of the existence of the following principle of action: The mechanical reactive power which has to be introduced into the motor-driven motors and which is passed on to the shafts of the partial unbalance bodies of the one type (as a power corresponding to the product from reaction moment MRQ times angular frequency ω), is transformed in a first conversion step into the "power of the kinetic energy" of the vibrating mass (this mass is also called "dynamic mass" m _dyn ). In a second conversion step, the "power of the kinetic energy" is transformed again into a mechanical reactive power, which has to be released again by the waves of the partial unbalance bodies of the other type (as a power from the reaction moment MRQ times ω). This power is emitted by the waves with a first part as the friction power of the bearings and with a second part as the power which is converted from the generator-operated motors into a generator power and which must be delivered by these motors.

The application of the superposition principle in the graphic representation of the Relationships (which will be described in detail later) clearly explain the Mode of operation of the generator-operated motors in two different ones Working areas: In the working area, which is described in Figure 2 by the partial curve N'-L'-M ', the generator-operated motors (114 and 1 16 in Figure 1) can deliver a generator power to the outside. In the work areas, which are described in Figure 2 by the two partial curves F'-N 'and M'-E'-D', one must mechanical power are supplied to the generator-operated motors, and in the example of the hydraulic solution, via the volume flow through it is passed through, in which case these motors must work by motor.

Since it must be possible to curve KB in the range F'-N'-L'-M'-E'-D '(in the diagram below to drive through in Figure 2), it is necessary that the generator operated Motors in this area can be operated both as a generator and as a motor have to. This necessary mode of operation cannot be derived from the teaching of Claim 3 of DE-OS 44 07 013, in which also two circuits of Motors and pumps are provided for a different type of vibrator, and in which is required (in the first feature of the characterizing part) that a generator Reactive power in an engine of one type is generated while one reactive motor power is generated in a motor of a different type. With such a One could not, for example, operate in the working area M'-E 'of the curve KB work.

The invention therefore also includes those means by means of which the adjustment of the relative setting angle β from the value β = 0 ° to the value β = 180 ° can take place continuously. The nature of the effect of these funds can, by the way, only be explained on the basis of the diagrams in FIG.

In contrast to the solution according to DE-PS 41 16 647, in which each motor has its own Measuring device for the angle of rotation of the partial unbalance body and its own control device for the Is assigned, the solution according to the invention uses, for the sake of simplicity, a principle at which it is not necessary to measure the angle of rotation µ of a single partial unbalance body, but only the relative setting angle β, and at which the two motors of a group together and in parallel switched to be supplied with drive power. However, this requires that the mirror image symmetrical synchronous relative rotation angle µ between partial unbalance bodies of the same type (a group) is maintained through the use of other means.

Preservation of the mirror-image synchronous relative rotation angle between partial unbalance bodies of the same

Type: An additional possibility for better stability of the relative rotation angle µ between the partial unbalance bodies of the same type was created, which is at least effective in the area of the relative positioning angle β _max = 180 °, at which the resulting unbalance moment has the maximum gets adjustable value. This created possibility of keeping the relative angle of rotation between the partial unbalance bodies of the same type stable is also based on the phenomenon that motor torques of the same size occur on all motors with an angle value set according to the inventive solution in the angle range β _max = 180 ° . In principle, the working point β = 180 ° represents an unstable point at which the relative rotation angle µ is reduced or increased when a disturbance torque MD _S appears which influences the synchronous relative rotation angle µ, and if in this case no suitable device for regulating the relative angle of rotation exists.

In comparison to the situation in the range of an angle value β = 0 °, this lability property is generally reduced according to the invention by the following facts: With the relative setting angle β = 180 °, two equally large torques are in equilibrium: the driving torque MD _A , which is developed by the motors, and the braking torque MD _B , which arises from the delivery of active power. The effect of the disturbance torque MD _S is proportional to the ratio MD _S / MD _A or to the ratio MD _S / MD _B. It follows from this that the tendency to become unstable is reduced, in particular when additional output is provided (in addition to bearing friction). An additional advantage is that (as can be shown) a self-regulating effect occurs with the generator-operated motors, with a trend towards self-regulating to the value β = 180 ° (see also the course of the curves near the points E and E 'in Figure 2). Because of the energetic coupling of the movements of the partial unbalance bodies of one type and the other, the self-regulating effect thus also influences the synchronous relative rotation angles of the motor-operated motors. A prerequisite for this mode of operation is that the relative setting angle β is the subject of a control or regulation, which is prescribed according to the teaching of the invention. The alternating torques MR = f (µ) also play a significant part in maintaining the mirror-image synchronous rotation angle µ. The statement made in DE-OS 43 01 368 in column 6, lines 36 et seq., According to which, in order to avoid other synchronization means, the automatically acting internal forces (due to the dynamic mass that moves along) are in principle only smaller in the range of a relative setting angle β than 90 ° can be corrected as follows: The effect of the alternating torques MR = f (µ) to support the synchronism of the mirror image of the rotating part of the unbalance body of the same kind, increases when the relative setting angle β = 90 ° is exceeded in the direction of β = 180 ° not only not, but on the contrary still too. This can also be explained as follows using the diagrams in FIG. 5 of DE-OS 43 01 368:

While the alternating torques MR = f (µ) mainly act in one direction of rotation in the range β <90 ° (with which a deviation of a partial unbalance body from the synchronous position µ can only be corrected in one direction), the value β = changes with increasing Value of the angle β aimed at 180 °, the mode of action of the alternating torques MR = f (μ) such that their positive and negative angular momentum components become equal [the course of the curve MR = f '(β = 180 °) is symmetrical to the axis µ]. Thus, for the alternating torques MR = f (µ) in the range β = 180 °, the particularly favorable effect on the angular synchronous operation also used in the context of the present invention results, such that both angular deviations + Δµ and angular deviations -Δµ from the The target angular position µ _should be able to be compensated for by the alternating torques MR = f (µ).

Suitability for open and closed circuits: In contrast to the vibrator according to the prior art, with the hydraulic solution in the configuration of pumps and motors according to the invention, either an open or a closed circuit can be implemented. When deciding on an open circuit, only the following must be observed for the circuit in which the motors can be operated as a generator: It must also be installed in the pipeline between the motor output and pump input: Either a controllable throttle for change the throttling effect or another power conversion element, in which the hydraulic power is converted into another power when the pressure in the volume flow is reduced.

In the event that the angular range β = 0 ° to β = 180 ° is traversed, and that a controllable throttle is used to control the angle in an open circuit an output is converted into heat and thus destroyed. The implemented heat output is proportional to the differential pressure before and after the throttle. But this is no particular disadvantage with the ramming vibrators, which are intended for the Use of the invention. In such a case, most of these vibrators If the adjustability of the centrifugal torque is only used as follows:

When adjusting from the rotation frequency zero to the working rotation frequency the vibrator is driven with an imbalance torque with the value zero. With This method avoids the excitation of resonance frequencies in the ground, which are below the operating frequency. An adjustment of the unbalance moment from that Zero value to the maximum value (and vice versa) only occurs when the rotation frequency is set to a working frequency.

The invention is explained in more detail with reference to two drawings: Figure 1 shows in schematic form and in the manner of a hydraulic plan for the hydraulic Solution variant the configuration of pumps and motors of a gearless vibrator according to the invention. In Figure 2, two diagrams are shown with which the Ratios of the differential pressures or the differential torques of the motors (the Adjustment device according to the invention shown in Figure 1) are shown during operation in a range of the relative positioning angle β = 0 ° to β = 360 °. If, however, in FIG. 2 in both diagrams, the size plotted with the ordinate axis is only as Torque ΔMD interpreted are also those when using electric motors occurring conditions described.

1 shows (with a symbolic representation of the 4 partial unbalance bodies by 4 corresponding circles) two partial unbalance bodies of one type 102, 104 and two partial unbalance bodies of the other type 106, 108, which can rotate (in a manner not shown) about their axes, which are supported in bearings in the vibrator frame. Each partial unbalance body is connected to its own hydraulic motor, by means of which it can be driven or braked for the purpose of adjusting the relative setting angle β and through which the partial unbalance body is supplied with the power which is subsequently lost in the form of bearing friction power, and which flows in part in the form of useful power, for example given to the pile driver, into the ground after this part of the power has previously been transferred to the oscillating dynamic mass m _dyn by means of the bearing forces.

The adjusting device for the relative setting angle β shown in FIG. 1 is for operation in the area β = 0 ° to β = 180 ° defines what should be indicated by the arrows shown, what effects and Symbolize directions. The partial unbalance bodies of one type 102, 104 are the motors 110, 112 assigned to one type and the partial unbalance bodies of the other type 106, 108 are the motors 114, 1 16 assigned to the other type. The respective direction of rotation of the motors and the partial unbalance body is shown by arrows with the sign ω. The motors of the same type are in parallel connected to a closed hydraulic circuit of one type 118 or the other type 120, whose volume flow is generated by a respective assigned pump P1 of the one type or pump P2 of a different kind.

The drawn (positive) relative positioning angle β = 90 ° is derived from a base position β = 0 °, at which has the total resulting unbalance moment zero.

in contrast to the hydraulic circuit of one type, the motors and the pump P2 of the Hydraulic circuit of a different kind generate pressure differences in both directions. That means that the Motors can work both as motors (motor) and as pumps (generator) and that Pump P2 can work both as a pump (generator) and as a motor (motor).

Both pumps are connected to a common diesel engine via a DM Drive device 122. The drive device could be a common shaft or a Distributor gearboxes. Both pumps are symbolized by arrows 126 and 128, equipped with adjusting devices for adjusting the delivery volume, so that with the help of these pump adjustment devices in their synchronous change the Volume flows and thus the rotational frequencies of the motors within specified limits can be changed.

In the hydraulic circuit of the other type, a component 130 is installed, which is flowed through by the volume flow of the return line 120 and which is capable of Throttle volume flow in a predetermined manner and thereby a predetermined pressure in the supply line in front of its entrance. The amount of pressure built up in this way can be specified by means of an electrical control device, which the Component 130 influences via an electrical line 132.

In the event that a vibrator reactive power is supplied to the motors 114, 116, that these can or must work as a generator then arises in front of the component 130 a pressure that is directly related to the simultaneous the effect of the pressure set relative setting angle β. Provided with the product the pressure and the volume flow do not give the maximum vibrator reactive power can be exceeded by influencing the throttle pressure as desired directly affect the reactive power generated by motors 114, 116 of the other type, and thus also indirectly the relative setting angle β.

Arrows are drawn on the circular symbols for the partial unbalance bodies, to which the characters MRQ are assigned. With the directions of the arrows Effective direction of the average reaction moments MRQ is displayed. You can see that in the case of the partial unbalance bodies of one type 102, 104, the direction of action of MRQ is opposite to the direction of rotation (symbolized with ω). This means that in order Maintaining the angular frequency ω and the set relative setting angle β die Motors of the one type 110, 112 an opposite torque in the motor type must have a value that is equal to the value of MRQ, and without a corresponding output from the vibrator being output.

The reaction moments act on the partial unbalance bodies of the other type 106, 108 MRQ in the direction of rotation. In this case, if the motors of the other type 114, 116 would not produce a braking torque of the same size as that Magnitude of the resulting reaction moments MRQ, however in the opposite direction MRQ, or if in this case the motors of the other type are not in one regenerative type an externally initiated torque in hydraulic power would convert, this would result in an acceleration of the angular frequency ω, or, this would increase the relative positioning angle β (which in the example shown has the value β = 90 °).

In the configuration according to FIG. 1, not all of the components that are otherwise included are shown belong to the complete adjustment device and which the specialist can also imagine can. In this context, it is only mentioned that the participation of a tax or control device is assumed, with the aid of which a predetermined relative setting angle β can be set. If a control device is to be provided, the Relative positioning angle β does not necessarily have to be the controlled variable itself. In principle it is enough such a solution in which the relative setting angle is influenced only indirectly, wherein however, it must be a known function of the actual controlled variable. If the relative setting angle β even the immediate control variable when using a control device to be, one has to provide a measuring device with which the relative setting angle β can be measured. In this case it can be a measuring device such as they e.g. in DE-OS 44 07 013 in connection with the figure 2 shown there is.

Two diagrams are shown in FIG. 2, of which the upper diagram with the characteristic curve KA describes certain states on motors 110, 112 of one type and the lower one Diagram with the characteristic curve KB certain states on the motors 114, 116 of the others Art describes. In both diagrams, the relative setting angle β is on the abscissa axis plotted, while the values of the ordinate axis are interpreted as different variables that can be derived from each other as different variables are provided: the differential pressure Δp at the motors, the differential torque ΔMD (proportional to Δp) on the motors and the differential power ΔP (proportional to Δp) of the motors.

The range shown for the angle β comprises 360 °. It can be seen that at β = 0 ° or β = 360 ° and at β = 180 ° there is a change between a motor operation (abbreviated "mot.") and a generator operation (abbreviated "gen."). The motor and the generator areas are marked with double arrows with the designations "mot." and "gen." featured. The characteristic curves KA and KB result from the superposition or addition of different variables, what in the example the diagram variable "differential torque ΔMD" is explained in more detail. The characteristic curves KA and In this case, KB represent the torques that act on the motors.

In the upper diagram, the broken line D-E-F shows the torque curve which the entire friction power is generated. The entire friction work comprises two components: The a component is indicated by the broken line D-K-F, which is the friction torque of the Bearing friction represented with a size corresponding to the distance A-D. The bearing friction has over the whole angular range a constant size. The other component, which in point D and in point F has the value zero and at point E (at β = 180 °) its maximum value (corresponding to the distance K-E), represents the course of the useful work torque, which for the useful work (= predominantly Friction work of the pile plow) is required. The linear curve of the useful torque is a simplification of the non-linear course of useful torque in practice. The The simplification shown is based on the assumption that the useful torque is roughly proportional to the size of the vibration amplitude, which is also known to be related to the size of the angle β changed.

The magnitude of the reaction torque MRQ, which is dependent on the angle β, runs according to FIG broken line A-H-B-J-C. The reaction moment MRQ has a sinusoidal shape Course with the amplitude corresponding to the distance G-H at β = 90 °. Through the Superposition of the values of the characteristic curve for the reaction moments MRQ and the values of the Finally, the characteristic curve for the torques for the entire friction work results Characteristic curve KA. Due to the fact that the reaction moment MRQ at β = 0 ° (or at β = 360 °) and at β = 180 ° has the value zero, represent the Values of the characteristic curve KA in the points β = 0 ° (= 360 °) and β = 180 ° exclusively Friction work torques.

Since the maximum values for the friction work torques (corresponding to the distance B-E) and for the reaction moments MRQ (corresponding to the distance G-H) approximately are shown to scale for the work that is done with real ramming vibrators high rotational frequencies of the partial unbalance bodies are also produced in the Practice for the range β = 90 ° to β = 180 ° a special angular range from the point M. to up to the point N, at which torque ΔMD acting as a generator also starts the engines of one kind are needed.

The characteristic curve KA is drawn for the operation of a ramming vibrator with high Load from the useful work, which is transferred from the pile to the earth. With a small proportion of useful work, point E moves downwards in the direction of point K. When the ramming vibrator is idling (without touching between Pile and earth) and the useful work is zero, point E coincides with that Point K together. It is also mentioned that the size of the maximum value of the Reaction torque MRQ (distance G-H) varies both with the size of the dynamic Mass, which also includes the mass of the pile, as well as the depth of the Penetration of the pile into the ground, or with the size of the submitted work.

The curve of the characteristic curve KB in the lower diagram results from the superposition of all Torque profiles similar to the characteristic curve KA, but with the difference that in the Range β = 0 ° to β = 180 ° the reaction moment MRQ has a negative course can, while the friction work torques here also appear exclusively positive. When comparing the two characteristic curves KA and KB it is remarkable that the angle β = 180 ° the torques ΔMD, which load the motors of one and the other type, of the same size and positive in both cases, which means a purely motor load of the motors is given.

Of particular interest for the present invention is when using the vibrator Ramming vibrator the operation of the gearless ramming vibrator in the mode of operation according to Figure 1 in the entire range of the angle β from β = 0 ° to β = 180 °. Before that actual ramming work begins, the vibrator is first set with the relative positioning angle β = 0 ° ramped up to an operating frequency which is above the ground resonance frequency lies. Only then is the adjustment device used for the Piling predetermined angles β (in most cases to the value β = 180 °) set. When keeping constant or changing the relative setting angle β must on the motors of one type the differential torques according to the characteristic curve KA and at the same time, the differential torques on the motors of the other type according to the characteristic KB must be set.

It is an interesting effect that is also exploited in the context of the invention that it to keep a predetermined angle β constant or to change the Angle β in a predetermined manner is sufficient, the required differential torque Δ MD (or the required differential pressure Δp) only for motors of one type adjust. It is in the nature of the adjustment device chosen that in this case the engines of the other kind automatically and automatically the necessary Ratios of the differential torques ΔMD (or the differential pressure Δp) according to the set the other characteristic in each case.

When driving through the angular range β = 0 ° to β = 180 ° you can with a Operating mode, which corresponds to the characteristic curves KA and KB, with respect to the motors of the another type (114, 116) according to the characteristic curve KB recognize the following behavior: At Starting the adjustment at β = 0 °, the motors are operated with a motor Differential torque ΔMD corresponding to the distance C'-F '. By reducing the Differential torque down to zero is initially achieved on the characteristic curve KB to the point N '. From here on, the angle β must be increased further regenerative differential torque are generated until the point M 'is reached. Thereafter, with a further increase in the angle β in the motors of the other type again and in an increasing manner an engine differential torque ΔMD be generated.

In principle, the effect of the generator reaction torque is MRQ on the partial unbalance bodies of the other type always present in the entire range of the angle β of β = 0 ° to β = 180 ° (according to the characteristic C'-J'-B '). It has been shown that this always acting regenerative reaction torque automatically to overcome the friction work torque is being used. Deriving the friction work torque from that regenerative reaction torque can occur from the angle β = 0 ° to that angle, which is assigned to the point M '. With a further increase in the angle β must the motors of the other type also generate a motor torque.

For example, in the angular range between the points M 'and B', where the size of the total friction work torque has the value S1 + S2, the torque part S2 of derived from the reaction moments, while the torque part S1 from motor Torques of the motors of the other type is derived.

When driving through the angle range β = 0 ° to β = 180 ° using a Adjustment device according to the teaching of the patent claim, it is sufficient at the start of the value β = 0 ° on, reduce the delivery volume of pump P2 by a small amount. For the Characteristic curve KB then applies, for example, to the area from point F 'to L' that (under Participation of the leakage bypass volume flow in the motors and in the pump) in the Pipeline 140 is first reduced until the point N 'is reached (until down to the system filling pressure) and that from point N 'to point L' the pressure in of pipeline 142 is continuously increased (starting at point N 'with the system filling pressure). Because of the given coupling of pumps P1 and P2 over the common one Drive device 122 has the reduction in the delivery volume of pump P2 same effect as if the delivery volume of pump P1 had been increased. Only from for this reason, the pressure in the pipeline 144 increases. It is obvious that the The reverse process also works: an increase in the delivery volume of the pump P2 with the same effect as a reduction in the delivery volume of pump P1 causes the angle β to decrease in the angle range β = 0 ° to β = 180 °.

It can be seen that when using a control or regulating device with the change of the delivery volume on a pump in two directions, the regulation of the angle β a predetermined value can be made. Of course, the same effect can can also be achieved if the delivery volume in both pumps at the same time changed in different directions.

When driving through the angular range β = 0 ° to β = 180 ° and when using an adjusting device according to claim 2, it is sufficient, starting at the value β = 0 °, by increasing the throttle resistance with the help of the adjustable throttle element 130 and by increasing the pressure in the pipeline 142 (by this measure), first to reduce the original motor-driven differential torque ΔMD corresponding to the distance C'-F ', and then, after arriving at the value zero at point N', with a further increase in the throttle Effect to generate a negative differential torque. In order to further increase the angle β after arriving at the angle β _L (which is assigned to the point L '), the pressure generated in the pipeline 142 by the throttling effect must be reduced again.

The above-described influencing of the relative setting angle β with the aid of the generation of a pressure at the output of other types of motors by using a throttle in the return line Pump P2 can advantageously be supported or changed by parallel or alternatively taken Influencing measures. These measures include, for example: the removal of a small one Bypass volume flow from the main volume flow, which the pump P2 at its outlet leaves, or the increase in the delivery volume of pump P1 by adjusting the pump P1 or by adding a small bypass flow to the main flow, which is the Pump P1 leaves at the outlet.

When using a throttle element in a return line (for example 142) to a pump for the purpose Generating a regenerative mode of operation of the correspondingly assigned motors is neither on the input of the pump of one type still at the input of the pump of the other type through the Return flow volume pressures generated. For this reason it is possible in any case that Hydraulic circuits can also be operated as open circuits.

Starting from the relative positioning angle β = 0 ° = 360 ° in point C (in the upper diagram), the Relative positioning angle β = 180 ° can also be achieved by changing the range of the relative positioning angle β in negative sense, namely from β = 360 ° through β = 270 ° to β = 180 °. As can be seen from Fig. 2 If this is the case, the operation of the motors of one and the other is reversed of another type. With such a procedure, the throttle element 130 is then in the return flow volume the pipe 146 of pump P1.

The technical teaching of independent claims 1 and 2 is based on the exemplary embodiment according to Figure 1, which in principle is a (particularly important) further development of the Description of Figure 2 disclosed main idea of the invention. Independent claims 3 and 4 describe the technical teaching from the main idea set out in Figure 2 when used in Connection with hydraulic or electric motors. Claims 3 and 4 do not require any special explanatory description. For the practical execution of one with electric motors operated vibrator, you can also use the arrangement according to FIG. 1 if you are in FIG. 1 presents the following modifications as given:

Motors 110, 112 and 114, 116 are electric motors and lines 144, 146 and 140, 142 represent the electrical leads to the motors. Component 130 is omitted. The symbols for the Pumps P1 and P2 each represent an electrical control device with which the motors can be varied Speeds and forced to develop variable torques in different directions can be. At least on the motors 114, 116, a negative torque can also be generated be developed while using a positive torque on the motors 110, 112 at the same time reached.

Claims (16)

1. Adjusting device for an unbalanced mass vibration generator having the following features:

   at least two pairs of unbalanced mass sub-members (102,106; 104,108) are provided which are drivable in rotation about an associated shaft and of which the vectorial sum of the component centrifugal force vectors gives the resultant centrifugal force vector, the action of which causes the mass of the vibration generator to execute directional vibrations,

   associated with each unbalanced mass sub-member is a component unbalanced mass moment, which can be regarded as a vector, and the vectorial sum of all of the component unbalanced mass moments gives the resultant unbalanced mass moment, which is proportional to the resultant centrifugal force vector,

   each pair is formed by an unbalanced mass sub-member of one kind (102; 104) and an unbalanced mass sub-member of another kind (106; 108), and a relative-position angle β is definable between the component centrifugal force vectors of the unbalanced mass sub-members of a pair at least for one clearly defined rotational position of the two unbalanced mass sub-members,

   each unbalanced mass sub-member of the one kind and of the other kind is provided with its own motor of one kind (110,112) and of another kind (114,116), respectively, and the rotor of each motor is so connected to its unbalanced mass sub-member that a torque can be transferred from the rotor to the unbalanced mass sub-member (and vice versa),

   at least one control means or one regulating means is provided for directly or indirectly setting a predeterminable value for the relative-position angle β or a predeterminable value for the amplitude of the vibration travel x or of a time derivative x' or x" thereof, one limit of the range of predeterminable values corresponding to a minimum resultant centrifugal force vector and the other limit of the range of predeterminable values corresponding to a maximum resultant centrifugal force vector,

   characterized by the combination of the following features:

   a) the hydraulic motors of the one kind (110,112) are connected in parallel to their own hydraulic circuit of one kind, the hydraulic motors of the other kind (114,116) are connected in parallel to their own hydraulic circuit of another kind, and each hydraulic circuit of the one and of the other kind includes at least one pump of its own of one kind (P 1) and of another kind (P2), respectively,

   b) the working point for the maximum settable resultant unbalanced mass moment, definable by the magnitude set for the relative-position angle β, can also be selected for a relative-position angle β greater than β = +90°, such as, for example, for a relative-position angle in the region of, or of exactly β = ±180°,

   c) a measuring means is provided for measuring the actual value of a control variable (for example amplitude, speed or acceleration of the vibratory movement, or the angle β itself), by which the magnitude of the relative-position angle β is directly or indirectly influenced and the actual value of the control variable is ascertained for processing by the control means or regulating means,

   d) the range of adjustment of the relative-position angle β from approximately β = 0° to approximately β = ±180° can, at least during operation of the vibration generator without the delivery of an effective output, be passed through with the motors of the one kind (110,112) operating purely in motor mode and with the motors of the other kind (114,116) operating alternately in generator and motor mode,

   e) the hydraulic output generated by means of the increase in pressure in the volumetric flow between the inlet and the outlet of the motors of the other kind (114,116) when the motors of the other kind (114,116) are operating in generator mode is substantially converted, between the inlet and the outlet of the pump (P2) of the other kind, into a corresponding motor output delivered by the pump (P2), the pressure in the volumetric flow simultaneously falling,

   f) each pump (P1, P2) is provided with a connection (122) to at least one drive motor (DM), via which connection drive output can be supplied to or derived from the pump (P1, P2).
2. Adjusting device according to the precharacterizing clause of claim 1, characterized by the combination of the following features:

   a) the hydraulic motors of the one kind (110,112) are connected in parallel to their own hydraulic circuit of one kind, the hydraulic motors of the other kind (114,116) are connected in parallel to their own hydraulic circuit of another kind, and each hydraulic circuit of the one and of the other kind includes at least one pump of its own of one kind (P1) and of another kind (P2), respectively,

   b) the working point for the maximum settable resultant unbalanced mass moment, definable by the magnitude set for the relative-position angle β, can also be selected for a relative-position angle β greater than β = ±90°, such as, for example, for a relative-position angle in the region of, or of exactly, β = ±180°,

   c) a measuring means is provided for measuring the actual value of a control variable by which the magnitude of the relative-position angle β directly or indirectly influenced (for example amplitude, speed or acceleration of the vibratory movement, or the angle β itself), and the actual value of the control variable is ascertained for processing by the control means or regulating means,

   d) the range of adjustment of the relative-position angle β from approximately β = 0° to approximately β = ±180° can, at least during operation of the vibration generator without the delivery of an effective output, be passed through with the motors of the one kind (110,112) operating purely in motor mode and with the motors of the other kind (114,116) operating alternately in generator and motor mode,

   e) the hydraulic output generated by means of the increase in pressure in the volumetric flow between the inlet and the outlet of the motors of the other kind (114,116) when the motors of the other kind (114,116) are operating in generator mode is substantially converted into another kind of output by the action of an output transducer element (130), the pressure in the volumetric flow between the inlet and the outlet of the output transducer element (130) simultaneously falling, which output is not returned, or at least not returned directly, to the pump of the one kind (P1), the hydraulic output being convertible by the output transducer element (130) into an output of a different physical form (for example conversion into a heat output when the output transducer element is in the form of a throttle),

   f) each pump (P1, P2) is provided with a connection (122) to at least one drive motor (DM), via which connection drive output can be supplied to or derived from the pump (P1, P2).
3. Adjusting device for an unbalanced mass vibration generator having the following features:

   at least two groups of unbalanced mass sub-members (102,104; 106,108) are provided which are drivable in rotation about an associated shaft, the mass of the unbalanced mass vibration generator being forced to execute directional vibrations by the resultant action of the centrifugal forces of all of the unbalanced mass sub-members (102, 104, 106, 108),

   each group of unbalanced mass sub-members (102,104; 106,108) comprises two unbalanced mass sub-members (102,104; 106,108) which, during vibratory operation, rotate synchronously in opposite directions with mirror-symmetrical angles of rotation,

   each unbalanced mass sub-member (102,104,106,108) is provided with its own hydraulic motor (110,112,114,116), the rotor of which is connected to its unbalanced mass sub-member (102,104; 106,108) in such a manner as to transfer a torque,

   a relative-position angle β definable between two unbalanced mass sub-members (102,104; 106,108) belonging to different groups, that angle being adjustable by influencing the hydraulic motors (110,112; 114,116),

   a hydraulic drive and control means (126,128) is provided for generating the volumetric flows through the hydraulic motors (110,112; 114,116) and for generating hydraulic pressures at least at the inlets of the hydraulic motors (110,112; 114,116),

   at least one control means or one regulating means is provided for directly or indirectly setting a predeterminable value for the relative-position angle β or a predeterminable value for the amplitude of the vibration travel x or of a time derivative x' or x" thereof, one limit of the range of predeterminable values corresponding to a minimum resultant centrifugal force vector and the other limit of the range of predeterminable values corresponding to a maximum resultant centrifugal force vector,

   characterized by the combination of the following features:

   a measuring means is provided for measuring the actual value of a control variable (for example amplitude, speed or acceleration of the vibratory movement, or the angle β itself) by which the magnitude of the relative-position angle β directly or indirectly influenced, and the actual value of the control variable is ascertained for processing by the control means or regulating means,

   by means of the hydraulic drive and control means (126,128), it is possible to establish at an identical timepoint in the two groups of hydraulic motors (110,112; 114,116) pressure gradients, measurable between the inlets and outlets of the hydraulic motors (110,112; 114,116), having signs that differ from group (110,112) to group (114,116) and, in the case of that group in which the hydraulic motors (114,116) are switched into a generator mode (pump mode) when the pressure gradient set is positive, the pressure gradient, in passing through a range of adjustment from a relatively small resultant static moment to a maximum resultant static moment, is adjustable in alternation from a positive value to a negative value,

   at least when the preferred direction of vibration of the vibration generator is maintained, the values of the pressure gradients in the hydraulic motors of a group (110,112; 114,116) are identical in terms of direction and the average magnitude,

   a predeterminable value for the relative-position angle β or a predeterminable value for the amplitude of the vibration travel x or of a time derivative x' or x" thereof can be set by influencing the values of the pressure gradients in the hydraulic motors in terms of magnitude and direction using the control means or regulating means.
4. Adjusting device for an unbalanced mass vibration generator having the following features:

   at least two groups of unbalanced mass sub-members (102,104; 106,108) are provided which are drivable in rotation about an associated shaft, the mass of the unbalanced mass vibration generator being forced to execute directional vibrations by the resultant action of the centrifugal forces of all of the unbalanced mass sub-members (102, 104, 106, 108),

   each group of unbalanced mass sub-members (102,104; 106,108) comprises two unbalanced mass sub-members (102,104; 106,108) which, during vibratory operation, rotate synchronously in opposite directions with mirror-symmetrical angles of rotation,

   each unbalanced mass sub-member (102,104,106,108) is provided with its own electric motor (110,112; 114,116), the rotor of which is connected to its unbalanced mass sub-member (102,104, 106,108) in such a manner as to transfer a torque,

   a relative-position angle β is definable between two unbalanced mass sub-members belonging to different groups (102,104; 106,108), that angle being adjustable by influencing the motors (110,112; 114,116),

   an electric drive and control means is provided for generating the currents flowing through the motors (110,112; 114,116),

   at least one control means or one regulating means is provided for directly or indirectly setting a predeterminable value for the relative-position angle β or a predeterminable value for the amplitude of the vibration travel x or of a time derivative x' or x" thereof, one limit of the range of predeterminable values corresponding to a minimum resultant centrifugal force vector and the other limit of the range of predeterminable values corresponding to a maximum resultant centrifugal force vector,

   characterized by the combination of the following features:

   a measuring means is provided for measuring the actual value of a control variable (for example amplitude, speed or acceleration of the vibratory movement, or the angle β itself) by which the magnitude of the relative-position angle β directly or indirectly influenced, and the actual value of the control variable is ascertained for processing by the control means or regulating means,

   the two motors (110,112; 114,116) of a group are in each case electrically connected in parallel and jointly acted upon,

   by means of the electric drive and control means (126,128), it is possible to establish at an identical timepoint in the two groups of motors (110,112; 114,116) torque gradients, measurable at the shafts of the motors (110,112; 114,116), having signs that differ from group to group and, in the case of that group in which the motors (110, 112; 114,116) are switched into a generator mode (braking mode) when the torque gradient set is positive, the torque gradient, in passing through a range of adjustment from a relatively small resultant static moment to a maximum resultant static moment, is adjustable in alternation from a positive value to a negative value,

   at least when the preferred direction of vibration of the vibration generator is maintained, the values of the torque gradients in the motors (110,112) of a group are identical in terms of direction and the average magnitude,

   a predeterminable value for the relative-position angle β or a predeterminable value for the amplitude of the vibration travel x or of a time derivative x' or x" thereof can be set by influencing the values of the torque gradients in the motors (110,112; 114,116) in terms of magnitude and direction using the control means or regulating means.
5. Adjusting device according to claim 1 or 2, characterized in that the hydraulic output imposed on the volumetric flow by the other motors (114, 116) is converted into a different output by the incorporation of both a special output transducer element (130) and a pump (P2) from which the output converted by it is delivered in the form of a motor output.
6. Adjusting device according to either claim 2 or claim 5, characterized in that the output transducer element (130) is a throttle the degree of throttling of which can be regulated.
7. Adjusting device according to any one of claims 1 to 5, characterized in that an output generated in the motors (110,112; 114,116) operating in generator mode is returned to the motors (110,112; 114,116) operating in motor mode, as desired

   by the series connection one after another of motors operating in generator and motor modes (110,112; 114,116) or

   by the mechanical coupling of two pumps (P1,P2) of two different hydraulic circuits, or

   by the transfer of electric energy from the motors operating in generator mode to the motors operating in motor mode (110,112; 114,116).
8. Adjusting device according to any one of claims 1 to 6, characterized in that the maximum resultant centrifugal force vector is established when a relative-position angle β = 180° is set, and also when, simultaneously, effective output is delivered to the outside by the vibration generator, in the motors (110,112) of the one kind substantially the same output as in the motors (114,116) of the other kind is converted in motor mode.
9. Adjusting device according to any one of claims 1 to 3, 5, 6 and 8, characterized in that at least one of the hydraulic circuits is in the form of a closed loop.
10. Adjusting device according to any one of claims 1, 2, 5, 6, 8 and 9, characterized in that the magnitude of the feed volume of both pumps (P1 ,P2) is adjustable, and that the two pumps are adjusted differently so that the pressure conditions necessary for setting or regulating a predetermined value for the relative-position angle β (or for a variable linked thereto in terms of function) are created in at least one of the hydraulic circuits.
11. Adjusting device according to any one of claims 1, 2, 5, 6 and 8 to 10, characterized in that the pressure conditions necessary for setting or regulating a predetermined value for the relative-position angle β (or for a variable linked thereto in terms of function) are created in at least one hydraulic circuit by supplying a volumetric flow additional to the main volumetric flow or by removing a particular volumetric flow from the main volumetric flow.
12. Adjusting device according to any one of the preceding claims, characterized in that each unbalanced mass sub-member (102, 106; 104,108) is allocated a second adjusting and/or drive motor.
13. Adjusting device according to any one of the preceding claims, characterized in that the motors (110,112; 114,116) are simultaneously adjusting motors and drive motors.
14. Adjusting device according to either claim 1 or 2, characterized in that the presence of such an adjusting device in a gearless 4-shaft vibration generator adjustable in respect of the static moment can be recognized from the following features:

    at least two hydraulic circuits are provided each having at least one pump of its own,

    there are provided between the pumps (P1,P2) and the motors (110,112; 114,116) in each case at least two conduits for transporting the volumetric flows to the motors (110,112; 114,116) and in each case at least two conduits for transporting the volumetric flows away from the motors (110,112; 114,116).
15. Adjusting device according to either claim I or 2, characterized in that the presence of such an adjusting device in a gearless 4-shaft vibration generator adjustable in respect of the static moment can be recognized from the following features:

    any two motors from a total of four motors (110,112; 114,116) are connected in parallel to a hydraulic circuit of their own,

    no two motors (110,112; 114,116) are in series connection.
16. Adjusting device according to any one of the preceding claims, characterized in that the unbalanced mass vibration generator is provided as a pile-driving vibration generator.

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