EP2243881A2 - Mounted compactor which can be attached to a digger and method for operating same - Google Patents

Abstract

The compactor (10) has a rotating mass unit arranged eccentrically relative to a drive shaft for generating an impact effect, where the eccentricity and impact frequency of the rotating mass unit in operation of the compactor are target variable. The eccentricity in a discrete operating mode (X1) is greater than in another discrete operating mode (X2) and a third discrete operating mode (X3). The eccentricity is equal in the latter and the third mode, and the impact frequency in the latter operating mode is smaller than in the third operating mode. An optical display device comprises LED. An independent claim is also included for a method for operating a mounted compactor.

Description

The invention relates to a cultivation compressor according to the preamble of claim 1.

In the field of soil compaction, there are many different requirements based on soil type, grain shape, particle size distribution and water content. For example, in cohesive soils a good compaction result is achieved by keeping the compaction frequencies of cultivators used low. In non-binding, so sandy soils, however, a high compression frequency is sought in order to achieve a good compaction. In addition, higher exciter frequencies are desirable from a vibrational point of view in inner city areas. Natural frequencies of floor slabs lie mostly in ranges between 10 to 30Hz (Hertz). The risk of resonance effects is lower at higher frequencies.

In most cases eccentric rotating systems are used. An arrangement of masses that eccentrically rotate about an axis, according to physical laws to a radial centrifugal force about this axis, with a design-related imbalance frequency and imbalance amplitude. The dynamic forces thus formed are dissipated into the soil via plates. As a result, the soil to be compacted is stimulated to shift at its grain boundaries and to increase its density and thus its rigidity.

Cultivation compressors are known from the market, which are equipped with so-called reversible imbalance masses. These are arranged eccentrically on a drive shaft and can produce different imbalance amplitudes and thus impact forces as a function of the direction of rotation, with an approximately constant frequency. The imbalance system consists for example of three exciter masses, of which at least one is pivotable about a certain angular range on the axis in relation to the other rotating masses. Such an arrangement will be approximately in the DE 20 2005 006 059 U1 described.

Furthermore, for example EP 1 411 175 B1 Cultivation compressor known whose vibration frequency is variable.

The object of the invention is to improve the operation of a cultivation compressor.

This object is achieved by a cultivation compressor according to claim 1. Advantageous developments are specified in the subclaims. Features which are important for the invention can also be found in the following description and in the drawings, wherein the features, both alone and in different combinations, can be important for the invention, without being explicitly referred to again.

The inventively proposed at least three modes of operation of the add-on compactor is significantly expanded, because with him both cohesive soils and non-cohesive soils can be optimally compacted. The fact that there are three different discrete modes ensures that complex adjustment work is just as little required as a purely based on the user's feeling and thus in the end rather inaccurate setting. Instead, the three discrete modes of operation, for example, are designed to avoid resonances of any structures in the work area of the add-on compactor, such as buildings, bridges, pillars, and the like, to prevent them from being damaged.

The invention is based on an imbalance, as it is commonly used in cultivation compressors, especially in versions that can be coupled to an excavator. It is advantageous if the cultivation compressor is driven and controlled by a hydraulic system, preferably of that of the excavator. The fact is used that rotating masses whose centers of gravity are eccentric to their axis of rotation, generate an imbalance. This can be based on Steiner's theorem for single or multiple rotating masses determine. It is provided that the rotating masses assume different end positions relative to one another depending on a direction of rotation of a drive shaft. This is achieved by a part of the rotating masses are rigidly coupled to the drive shaft, another part, however, is pivotable in a certain angular range around the drive shaft, for example in a range of about 180 degrees.

When changing the direction of rotation of the drive shaft, the pivoting rotating masses can then assume one of two possible end positions relative to the rigid rotating masses due to their inertia. As a result, a kind of "driver system" is formed. The rigidly mounted on the drive shaft rotating masses may be positively or non-positively connected to the drive shaft, so for example via a gearing or a shrinkage.

The unbalance generator could include one or more rigid masses rotating relative to the drive shaft and one or more rotating masses pivotable about the drive shaft in an angular range of up to about 180 degrees, and these could be positioned on the drive shaft so that imbalances would only occur in one the direction of rotation specific level occur. As a result, a symmetrization of the masses is achieved with respect to the rotational movement of the drive shaft and a staggering of the unbalance generator prevented. At the same time, the bearings of the drive shaft are spared. At least such an imbalance generator therefore requires three rotating masses, a pivotable rotating mass approximately centrally on the drive shaft and two rigid rotating masses symmetrical to both sides. The unbalance generator can be structurally designed to be flexible when used is also taken into account by more than a total of three rotating masses. The change in the direction of rotation of the drive shaft can be easily achieved if, for example, the excavator, the direction of flow of the hydraulic motor driving hydraulic flow ("flow") is reversed.

It would also be conceivable to vary the overall eccentricity by selectively adding or disabling at least one additional drive shaft with at least one additional eccentric mass.

Preferably, the beat rate in the second mode is between the beat rate in the first and third modes. Although the impact force in the second mode is below that of the other two modes, but with a slightly higher than the first mode beat rate. It is thus created, so to speak, a "soft mode" with low power and relatively low beating frequency, which is slightly increased for particularly safe avoidance of resonances over that of the first mode.

It is also proposed that the impact frequencies and eccentricities are coordinated so that the impact force of the add-on compactor in the first mode at least approximately corresponds to the impact force in the third mode, and preferably the impact force in the second mode is about 50 to 60% thereof. This allows a coverage of almost all possible scenarios.

This is especially true when the beat frequency in the first mode between 30 and 40 Hz, preferably approximately 35 Hz, in the second mode between 40 and 50 Hz, preferably at about 45 Hz, and in the third mode is between 55 and 65 Hz, preferably about 60 Hz.

For example, three operating modes X1, X2 and X3 are defined, which have properties according to the invention in the combination of direction of rotation and rotational speed, as described by way of example in the following table and as an approximate size specification: operating mode Eccentricity of the masses beat frequency clout X1 large small (about 35 Hz) big (about 80-100 kN) X2 small medium (about 45Hz) medium (about 40-60 kN) X3 small large (about 60 Hz) big (about 80-100 kN)

In mode X1, a maximum eccentricity and thus a maximum imbalance is set, and the hydraulic current driving the hydraulic motor is set to give a beat frequency of about 35 Hz. This leads to an imbalance amplitude or impact force of about 80-100 kN, in particular of about 85 kN.

In operating mode X2, a minimum eccentricity and thus a minimum imbalance is set. The the Hydraulic motor driving hydraulic current remains approximately unchanged compared to the X1 operation, so that as a result of the relief by the lower imbalance results in a slightly increased impact frequency of about 45 Hz. As a result, this results in an imbalance amplitude or impact force of about 40-60 kN, in particular of about 45 kN.

In the operating mode X3, the eccentricity or impulse is identical to the X2 operation. However, the hydraulic current driving the hydraulic motor is set to an increased value as compared to the X1 and X2 operations, resulting in a likewise increased beat frequency of about 60 Hz. In turn, due to the faster rotation, in spite of a mass distribution equal to X2, a high imbalance amplitude or impact force similar to the X1 operation of approximately 80-100 kN, in particular approximately 85 kN, is achieved.

The three operating modes X1, X2 and X3 can be adjusted solely by means of a changeover or switching of the hydraulic flow, the basic hydraulics of the excavator being structurally the same. This avoids excessive construction effort. Furthermore, the operating mode X1 represent a basic operating mode, is switched from the respectively in an X2 or X3 operation and, if necessary, switched back again.

A particularly advantageous embodiment of the add-on compactor according to the invention provides that it comprises a preferably optical display device which indicates to the excavator operator during operation the current operating mode of the add-on compactor. This greatly simplifies handling.

The display device may be designed such that it outputs a first signal associated with the respective operating mode-for example a continuous signal-when the mounted compressor is at least approximately in one of the at least three discrete operating modes, and a second signal assigned to the respective operating mode-for example an intermittent one Signal - emits when the attachment compressor is slightly outside of the corresponding operating mode.

In a further development, it is proposed that the display device is designed so that it emits the first signal when the current beat frequency is approximately within +/- 2.5 Hz of a desired frequency of the respective mode, and outputs the second signal when the current Rate deviates from the target frequency by more than about +/- 2.5 Hz, but less than about 5 Hz, and outputs a third or no signal when the current beat frequency deviates from the target frequency by more than about 5 Hz.

Particularly robust, inexpensive and easy for the user, such as the excavator operator, it is understandable if the display device comprises three lighting devices, in particular LEDs, each of which one of the three operating modes is assigned.

The design of the attachment compactor is simple if the impact frequency during operation can only be changed by the hydraulic flow provided by the excavator. On a present in or on the attachment compressor hydraulic valve can then be dispensed with.

Alternatively, the cultivation compressor could include a switching means for changing the rotational speed of the drive shaft, which has a hydraulic switching valve, and which releases an additional volume flow in a first position and blocks the additional volume flow in a second position. This can be increased by connecting a parallel path of the flow to drive the hydraulic motor and its speed can be increased, resulting in a corresponding increase in the beat frequency. This variant can be realized without major structural changes even with existing versions of add-on compactors and thus relatively inexpensive. Possibly. this variant can even be retrofitted to existing add-on compactors.

A modification to this provides that the switching means comprises a hydraulic switching valve which releases a first volume flow in a first position and a second volume flow in a second position. This results in a constructive simplification of the hydraulics of the add-on compactor in that a change in the volume flow can take place via a single element, and a switchable parallel path is not required.

It is particularly useful when the switching means by a hydraulic switching pulse or electro-hydraulically or manually operated. Thereby, the hydraulic flow can be changed or switched to a manner adapted to a design of the unbalance generator or the excavator. In particular, switching by means of a short hydraulic impulse ("ballpoint pen principle") is advantageous if manual changeover is out of the question and an electrical or additional hydraulic connection between the add-on compactor and the excavator operating it is not provided.

Another important aspect of the invention is that the mass is pivotable relative to the drive shaft and about an axis parallel to the drive shaft or coaxial axis from a first to a second position and back and at least one stop surface has, with a relative to the drive shaft but rigid in rubber-elastic stop buffer cooperates, wherein the stop surface is pivotally mounted about an axis parallel to the drive shaft. This is based on the following consideration: it makes sense to choose the first and the second position so that two very different eccentricities arise. In this case, the required limitation by means of a two-sided stop device, consisting of a rotatably mounted stop pin and, for example, four stop buffers realized. The angular acceleration occurring when the direction of rotation of the drive shaft changes, together with the moment of inertia of the pivotable rotating mass, leads to high forces when reaching the end positions. The bumpers absorb these forces and absorb at least part of the kinetic energy.

For example, the bumpers are designed as progressively working structure damper of a material which consists wholly or partly of co-polyester elastomers and vulcanized on a metal surface of the rigid rotating masses. It may be advantageous to design the stop buffers as (dense) hollow bodies, so that the air contained therein is involved in the energy absorption. Preferably, the stop pin (mirror image at its ends) has a total of four stop surfaces, namely two for each of the two end positions of the pivotable rotating mass. This is one - based on a cylindrical basic shape of the stop pin - the largest possible area for the stop enabling zone. The larger the surface defining the stop, the lower the compressive stresses occurring in a stop in the stop buffers.

The rotatability of the stop pin causes it automatically adjusted when hitting the stop buffer by itself so that the abutment surfaces of the stop pin touch the surfaces of the stop buffer at least approximately plane-parallel. The stop pin can thus rotate during the deformation phase of the stop buffer and thus maintain a flat contact of the stop surfaces on the stop buffer. It helps when the stopper bolt is rotatable about its axis only in a limited angular range, for example in an angular range of +/- 12 degrees. In addition, the limitation of the angular range prevents the stopper bolt from starting to rotate uncontrollably in a bore receiving it due to vibration.

It is further proposed that the movable mass comprises a plurality of sub-masses, which are accommodated in a receiving space whose volume is greater than the total volume of the sub-masses, and which has at least one boundary wall, which the sub-masses in the first rotational direction in a first position and forces in the second direction of rotation in a second position, wherein the total center of gravity of the sub-masses in the first position, a total of a different distance from the axis of rotation than in the second position. Such an unbalance generator works very wear and therefore has a long life.

Figur 1

eine schematische Seitansicht eines Anbauverdichters;

Figur 2

eine perspektivische Ansicht eines Unwuchterzeugers des Anbauverdichters von Figur 1 in einer ersten Betriebsart;

Figur 3

eine perspektivische Ansicht des Unwuchterzeugers von Figur 2 in einer zweiten Betriebsart;

Figur 4

einen Querschnitt durch einen Bereich des Unwuchterzeugers von Figur 2 längs der Linie IV- IV von Figur 3;

Figur 5

ein Schaltplan einer ersten Ausführungsform einer Hydraulikschaltung des Anbauverdichters von Figur 1 für eine erste Betriebsart;

Figur 6

eine Darstellung ähnlich zu Figur 5 für eine zweite Betriebsart;

Figur 7

eine Darstellung ähnlich zu Figur 5 für eine dritte Betriebsart;

Figur 8

ein Schaltplan einer zweiten Ausführungsform einer Hydraulikschaltung des Anbauverdichters von Figur 1;

Figur 9

einen Schnitt durch eine alternative Ausführungsform eines Unwuchterzeugers des Anbauverdichters von Figur 1;

Figur 10

eine Ansicht von vorne des Anbauverdichters von Figur 1; und

Figur 11

ein Diagramm zur Erläuterung einer Einstellung einer Betriebsart des Anbauverdichters der Figur 1..

Hereinafter, exemplary embodiments of the invention will be explained with reference to the drawings. In the drawing show:

FIG. 1

a schematic side view of a mounted compressor;

FIG. 2

a perspective view of an unbalance generator of the attached compactor of FIG. 1 in a first mode;

FIG. 3

a perspective view of the unbalance generator of FIG. 2 in a second mode;

FIG. 4

a cross section through an area of the unbalance generator of FIG. 2 along the line IV-IV of FIG. 3 ;

FIG. 5

a circuit diagram of a first embodiment of a hydraulic circuit of the add-on compactor of FIG. 1 for a first mode of operation;

FIG. 6

a representation similar to FIG. 5 for a second mode of operation;

FIG. 7

a representation similar to FIG. 5 for a third mode of operation;

FIG. 8

a circuit diagram of a second embodiment of a hydraulic circuit of the add-on compactor of FIG. 1 ;

FIG. 9

a section through an alternative embodiment of an unbalance generator of the add-on compactor of FIG. 1 ;

FIG. 10

a view from the front of the attached compactor of FIG. 1 ; and

FIG. 11

a diagram for explaining an adjustment of an operating mode of the add-on compactor FIG. 1 ..

In all figures, the same reference numerals are used for functionally equivalent parts or sizes.

In the FIG. 1 an attachment compressor 10 is shown, which comprises an imbalance generator 12. The unbalance generator 12 is connected to a hydraulic motor 13, which in turn is connected to the hydraulic system of an excavator, not shown. By the unbalance generator 12, a compressor plate 14 is set in vibration during operation. The compressor plate 14 is connected via connecting elements 15 and buffer devices 16, in particular metal rubber buffer, with an upper part 17 of the add-on compactor 10 elastically. The cultivation compressor 10 can be fastened via a receptacle 18 to an excavator arm 19. The receptacle 18 may be formed as a quick-change system. As a result, a mechanical and hydraulic connection to the excavator can be made in a simple manner. Below the receptacle 18 is followed by a rotary motor 20, over which the cultivation compressor 10 can be rotated with respect to the excavator arm 19. The hydraulic motor 13 is connected in the embodiment shown with the interposition of a valve block 60 via hydraulic lines 21 and the receptacle 18 with the hydraulic system of the excavator. Via the valve block 60, the volume flow, which passes from the excavator to the hydraulic motor 13, can be adjusted in various ways, as described below with reference to the FIGS. 5 to 8 will be explained. The flow direction of the hydraulic flow to the hydraulic motor 13 is excavator side reversible. Alternatively or additionally, however, the volume flow can also be adjusted by the excavator, for example by the excavator operator correspondingly actuating a corresponding control element (accelerator pedal, control stick). This will be discussed in greater detail at the end of this description.

FIG. 2 shows a view of a first embodiment of the unbalance generator 12 in a first mode with small imbalance amplitude: To a drive shaft 30, two rigid rotating and with respect to a central axis of the drive shaft 30 eccentrically arranged masses 32a and 32b are rigidly coupled. On radial shoulders (without reference numeral) of the rigid rotating masses 32a and 32b, a total of four hollow stop buffers 34 are arranged, for example by a vulcanization, of which in the perspective view of Figures 2 and 3 only two are visible, and their function will be explained in more detail below.

The rotational axis of the mass 36 is coaxial with the drive shaft 30 by means of the rotating masses 32a and 32b which are rigid with respect to the drive shaft 30. The mass 36 can be pivoted relative to the drive shaft 30 and the two to the drive shaft 30 rigid masses 32a and 32b are brought into one of two end positions. In FIG. 2 the pivotable rotating mass 36 with respect to the drive shaft 30 opposite the rigid rotating masses 32a and 32b, so that in the sum of all three masses 32a, 32b, 36 results in a relatively small imbalance.

FIG. 3 shows the imbalance generator 12 with the pivotable rotating mass 36 in the other of the two possible End positions: The mass 36 is seen in the axial direction of the drive shaft 30 mostly in the same alignment with the rigid rotating masses 32a and 32b arranged, so seen from the drive shaft 30 on the same side as the rigid rotating masses 32a and 32b, so that in the sum of all three masses 32a, 32b, 36 gives a relatively large imbalance.

In a receiving bore 38 of the pivotable rotating mass 36 a with the stop buffers 34 on the rigid rotating masses 32 a and 32 b in yet darzustellender manner cooperating rotatable stop pin 40 is housed, which protrudes with its projecting ends on both sides via the receiving bore 38. Each projecting end has two oppositely arranged plane-parallel stop surfaces 42. In FIG. 3 two shaped holes 44 are visible in the pivotable rotating mass 36, which have a slot-like shape in their cross section. Therein two cylindrical pins 46 are added, which are firmly anchored at its non-visible end in the stop pin 40. In this way, the stopper pin 40 is rotatable in the receiving bore 38 according to the geometry of the shaped holes 44 by a small area.

How out FIG. 2 can be seen, the stop pin 40 rests by means of the stop surfaces 42 in the in FIG. 2 shown end position of the pivotable rotating mass 36 on the in the Figures 2 and 3 rear stop buffers 34. As out FIG. 3 can be seen, the stop pin 40 rests by means of the stop surfaces 42 in the in FIG. 3 shown end position of the pivotable rotating mass 36 on the in the Figures 2 and 3 front stop buffers 34. It is characterized by the rotatability of the stop pin 40 for a parallel at any time and thus large area Provided contact between the stop surfaces 42 and the stop buffers 34.

FIG. 4 shows a cross section through that portion of the pivotable rotating mass 36 in which the holes 44 are present, wherein the cutting plane is orthogonal to the longitudinal axis of the drive shaft 30 and through the in FIG. 3 shown line IV-IV goes. In the stop pin 40, the pins 46 are firmly anchored, for example, pressed or screwed. Upon rotation of the stop pin 40 in the receiving bore 38, the pins 46 in the formed bore 44, limited by the size of the column 48, pivoted. Thus, the stopper pin 40 is limited by an angular range 50 with respect to a passing through its central axis 52 reference line 54 rotatably.

FIG. 5 12 shows a schematic of the hydraulic circuit of the valve block 60 for operating the unbalance generator 12 in a first mode of operation. Starting from hydraulic connections P, R and L on a hydraulic quick coupling 62 on the receptacle 18 (in the lower part of FIG. 5 ), a pressurized flow stream 64 flows through various elements to the hydraulic motor 13. The white triangle symbols 64 indicate the pressurized main flow path. The hydraulic flow flows through a pressure-controlled check valve 76 and an adjustable flow control valve 78 to the hydraulic motor 13. The flow control valve 78 has the task of keeping the hydraulic flow equal pressure independent. Parallel to the flow control valve 78 is a check valve 80, which blocks to the hydraulic motor 13 out.

Starting from the hydraulic motor 13 (in the upper part of the figure) flows marked by a black triangle symbols Return flow 74 through various elements back to the quick coupling 62. The hydraulic flow flows through a normal check valve 66 and a pressure-controlled check valve 68 back to the quick coupling 62. Parallel to the check valve 66 are in side paths each a flow control valve 70 and 72, the latter in series with a switching valve 88th The switching valve 88 can be actuated either manually or by an electrical remote action (electro-hydraulic valve). The elements 66, 70, 72 and 88 together form a hydraulic switching means 87.

Parallel to the hydraulic motor 13, two pressure limiting valves 82 and 84 are arranged in opposite directions, for example, to compensate for transient operating conditions, to allow about a pressure equalization and a controlled braking in the wake after switching off the hydraulic pump of the excavator. A leakage line 86 connects the hydraulic motor 13 directly to the quick coupling 62 for the return of any leakage currents.

In FIG. 5 For example, the hydraulic circuit 60 is shown in a so-called "X1" operation. In this are at the P port of the quick coupling 62, a high supply pressure and the R port to a return pressure. The switching valve 88 is closed. Hydraulic fluid flows via the check valve 76 and the flow control valve 78 to the hydraulic motor 13 and from there via the check valve 66 and the check valve 68 back. The pressure of the hydraulic flow at location 68a actuates the check valve 68. Without the use of the check valve 68, there would be a risk of cavitation of the hydraulic motor 13 when switching off. In this X1 mode of operation, the unbalance generator 12 rotates in a first direction of rotation in which the pivotable rotating mass 36 moves in the in FIG. 3 shown position (large imbalance) and a speed of, for example, about 35 1 / sec is reached. The result is an impact force of, for example, about 90 kN.

FIG. 6 shows the hydraulic circuit 60 at one opposite FIG. 5 reverse flow direction of the hydraulic flow, which is referred to as "X2" operation. Starting from the now pressurized port R of the quick coupling 62, the flow stream 64 now flows via the check valve 68 and the flow control valve 70 to the hydraulic motor 13. The flow control valve 70 in turn has the task to keep the hydraulic flow equal pressure independent. Starting from the hydraulic motor 13, the return flow 74 flows via the check valve 80 and the check valve 76 back to the now unpressurized return port P on the quick coupling 62. In this X2 mode of the unbalance generator 12 rotates in a second rotational direction in which the pivotable rotating mass 36 in the in FIG. 2 shown position (small imbalance) and a speed of, for example, about 45 1 / sec is reached. It results in a power of, for example, about 50 kN.

FIG. 7 shows the hydraulic circuit 60 in a third mode, referred to as "X3 mode". The flow direction of the hydraulic fluid and thus the direction of rotation of the unbalance generator 12 correspond FIG. 6 , In this "X3" operation, however, the switching valve 88 is opened and increases, in addition to the flow through the flow control valve 70, the flow rate. For example, the volume flow through the switching valve 88 to the volume flow through the flow control valve 70 in a ratio of 1: 2. In this X3 mode, a Speed of, for example, reached about 60 1 / sec, with a power of, for example, about 90 kN.

FIG. 8 FIG. 12 shows a schematic of a modified embodiment of a hydraulic circuit of the valve block 60 for operating and controlling the imbalance generator 12, in which, unlike the illustrations of FIG FIGS. 5 to 7 , Instead of the switching valve 88, a pulse valve 90 is inserted in the hydraulic flow. The impulse valve can be opened or closed by means of a short hydraulic impulse ("ballpoint pen principle"). For this purpose, a hydraulic control stream 92 is used, which is tapped at a suitable location on the pressurized branch downstream of the P-port. If desired, the pressure relief valves 82 and 84 may be set to other thresholds for operation with a pulse valve 90 than for operation with a switching valve 88. For example, the thresholds are increased by a factor of 1.75.

An alternative embodiment of an unbalance generator 12 is shown in FIG FIG. 9 shown. It is true that such elements and areas that are functionally equivalent to elements and areas described in the preceding figures, the same reference numerals and are not explained again in detail.

The unbalance generator 12 comprises a cylindrical or drum-shaped closed housing 94, which is arranged eccentrically about a drive shaft 30. Inside the housing 94, a receiving space 96 is formed, which is limited inter alia by a hollow boundary wall 98, which extends approximately radially from the geometric center of the housing 94 outwardly. In the receiving space 96 is a certain number of balls 100th present, which are also referred to as "sub-masses" and thus form an amorphous movable mass 36. If the housing 94 rotates clockwise around the drive shaft 30, the balls 100 will rotate into the in FIG. 9 shown forced position in which they have a relatively small distance from the drive shaft 30. The eccentricity is thus comparatively small. On the other hand, if the housing 94 rotates in the counterclockwise direction, the balls 100 are forced into the opposite position, in which they have a relatively large distance from the drive shaft 30. The eccentricity is thus comparatively large.

Out FIG. 10 It can be seen that the attachment compressor 10 has on an end face 102 of the upper part 17, a visual display device in the form of three lighting devices 104a, 104b and 104c, which are each formed by an array of multiple LEDs. In the operating mode X1, that is to say with a relatively large eccentricity and a frequency of approximately 35 Hz, the lighting device 104a illuminates continuously. In the operating mode X2, that is to say with a relatively small eccentricity and a frequency of approximately 45 Hz, the lighting device 104b illuminates continuously. In the operating mode X3, that is to say with a relatively small eccentricity and a frequency of approximately 60 Hz, the lighting device 104c illuminates continuously.

This is particularly advantageous when the hydraulic flow is adjusted exclusively from the excavator, for example, by the excavator operator a corresponding (not shown) control (throttle or accelerator pedal or the like) operated. The excavator operator is instructed by the display of lighting devices 104a-c as he has to operate the control to set the beat frequency of a particular mode of operation.

In addition, the excavator operator sets the eccentricity by the direction of the hydraulic circuit.

The corresponding method will now be described with reference to the diagram of FIG. 11 exemplified for a mode explained. In this diagram, a beat frequency f is plotted over the time t. Fs denotes a desired beat frequency, which may be the desired beat frequency for the operating modes X1, X2 or X3. With fa is a current beat frequency called. A first tolerance band 106 whose limits lie at a distance of df1 from the nominal beat frequency fs and a second tolerance band 108 whose limits lie at a distance of df2 from the nominal beat frequency fs is applied around the nominal beat frequency fs. where df2 is greater than df1. In the present case, for example, df1 is 2.5 Hz, df2 is approximately 5 Hz. If the current beat frequency fa lies within the first tolerance band 106, the corresponding lighting device 104a, b or c lights up permanently. If the current beat frequency fa lies outside the first tolerance band 106, but still within the second tolerance band 108, the corresponding lighting device 104a, b or c lights up intermittently. If the current beat frequency fa also lies outside the second tolerance band 108, the corresponding lighting device 104a, b or c does not light at all.

For this purpose, the display device 104 is coupled to a power supply, not shown, which includes, for example, a generator integrated in the attachment compressor 10, which is coupled either to the drive shaft 30 of the unbalance generator 12 or to a separate hydraulic motor. The display device 104 is controlled by an electronic, also not shown Signal acquisition and processing unit. This detects, for example, the current speed of the drive shaft 30 via a corresponding sensor and - for example, via the direction of rotation of the drive shaft 30 - also the current eccentricity.

Of course, other embodiments of the display device are conceivable, for example, an LCD display, a colored display, a command display, or a transmission, for example, via Bluetooth to a display device in the cab of the excavator. In this way, even the establishment of a closed controlled system is conceivable. It is also understood that the display 104 described above both in an imbalance generator 12 with pivotable masses according to the FIGS. 2 to 4 as well as an unbalance generator 12 with a plurality of individual masses according to the FIG. 9 can be used.

Claims (15)

Cultivation compressor (10) which can be coupled to an excavator, in which a percussion effect by at least one rotating and relative to at least one drive shaft (30) eccentrically arranged mass (32, 36) is generated, wherein both the eccentricity and the beat frequency of the rotating Mass (32, 36) are selectively varied in operation, characterized in that at least three discrete modes (X1, X2, X3) are adjustable, wherein in the first mode (X1) the eccentricity greater than in the second (X2) and third Mode (X3) and the beat frequency is smaller than in the third mode (X3), and wherein in the second (X2) and third mode (X3) the eccentricities are the same, but the beat frequency in the second mode (X2) is less than in the third mode (X3). Cultivation compressor (10) according to claim 1, characterized in that the beat frequency in the second mode (X2) between the beat frequency in the first (X1) and in the third mode (X3). Cultivation compressor (10) according to claim 2, characterized in that the impact frequencies and eccentricities are coordinated so that the impact force of the attachment compressor (10) in the first mode (X1) at least approximately corresponds to the impact force in the third mode (X3), and preferably the impact force in the second mode (X2) is about 50 to 60% thereof. Cultivation compressor (10) according to one of claims 2 or 3, characterized in that the beat frequency in the first mode (X1) between 30 and 40 Hz, preferably approximately 35 Hz, in the second mode (X2) between 40 and 50 Hz, preferably at about 45 Hz, and in the third mode (X3) is between 55 and 65 Hz, preferably about 60 Hz. Cultivation compressor (10) according to any one of the preceding claims, characterized in that it comprises a preferably optical display device (104) which indicates to the excavator operator in operation the current operating mode (X1, X2, X3) of the add-on compactor (10). Cultivation compressor (10) according to claim 5, characterized in that the display device (104) is designed so that it outputs a respective operating mode associated first signal when the add-on compactor (10) at least approximately in one of the at least three discrete modes (X1 , X2, X3), and outputs a second signal associated with the respective operating mode when the add-on compactor is slightly outside the corresponding operating mode (X1, X2, X3). Cultivation compressor (10) according to claim 6, characterized in that the display device (104) is designed so that it outputs the first signal when a current beat frequency (fa) within approximately +/- 2.5 Hz of a desired frequency (fs) is the respective mode, and outputs the second signal if the current beat frequency (fa) deviates from the desired frequency (fs) by more than about +/- 2.5 Hz but less than about 5 Hz, and a third or even does not emit a signal if the current beat frequency (fa) differs by more than approximately 5 Hz from the setpoint frequency (fs). Cultivation compressor (10) according to one of claims 5 to 7, characterized in that the display device comprises three lighting devices (104a, 104b, 104c), in particular LEDs, each of which one of the three operating modes (X1, X2, X3) assigned is. Cultivation compressor (10) according to one of the preceding claims, characterized in that the impact frequency in operation is variable only via the hydraulic power provided by the excavator. Cultivation compressor (10) according to one of claims 1 to 8, characterized in that it comprises the switching means (87) in the form of a hydraulic switching valve (88; 90) for changing the impact frequency, which releases an additional volume flow in a first position and in a second position blocks the additional flow. Cultivation compressor (10) according to one of claims 1 to 8, characterized in that it has a switching means (87) in the form of a hydraulic switching valve (88, 90) for changing the impact frequency, which in a first position, a first volume flow and in a second Position releases a second volume flow. Cultivation compressor (10) according to one of claims 10 or 11, characterized in that the switching means (87) by a hydraulic switching pulse or electro-hydraulically or manually operable. Operating modesOperating modeOperating modeOperating modeOperating modeOperating modeOperating converter (10) according to any one of the preceding claims, characterized in that the mass (36) is pivotable from a first to a second position and back relative to the drive shaft (30) and about an axis parallel to the drive shaft (30) and at least a stop surface (42) which cooperates with a relative to the drive shaft (30) rigid but in rubber-elastic stop buffer (34), wherein the stop surface (42) about an axis parallel to the drive shaft (30) is pivotally mounted, wherein the stop surface ( 42) preferably only in a limited angular range (50) is pivotable. Cultivation compressor (12) according to one of claims 1 to 13, characterized in that the movable mass (36) comprises a plurality of sub-masses (100) which are accommodated in a receiving space (96) whose volume is greater than the total volume of the sub-masses (100), and the at least one boundary wall (98), which forces the sub-masses (100) in the first direction of rotation in a first position and in the second direction of rotation in a second position, wherein the total center of gravity of the sub-masses (100) in the first Position has a different total distance to the drive shaft (30) than in the second position. A method of operating a mounted compactor (10) which is engageable with an excavator in which a hammering action is produced by at least one rotating mass (32, 36) disposed eccentrically relative to a drive shaft (30), both the eccentricity as well as the beat frequency are changed as a function of an application request during operation, characterized in that in a first operating mode (X1) the eccentricity is greater than in a second and third operating mode (X2, X3) and the beat frequency is lower than in the third operating mode (X3), and that in the second and third modes (X2, X3) the eccentricities are the same, but the beat frequency is smaller in the second mode (X2) than in the third mode (X3).

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