DE102009018490A1 - Cultivation compressor, which can be coupled to an excavator, with an unbalance generator - Google Patents

Abstract

The invention relates to a mounted compressor, which can be coupled to an excavator, with a preferably hydraulically driven unbalance generator with at least one rotating mass which is movable relative to the drive shaft such that they at a first rotational direction of a drive shaft, a first eccentricity and a second direction of rotation second eccentricity relative to a rotational axis of the drive shaft occupies, wherein the attachment compressor has at least one switching means with which the rotational speed of the drive shaft can be changed during operation.

Description

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

in the There are various fields of compaction technology for soils Requirements by soil type, grain shape, particle size distribution and by the water content. So you can reach, for example, with cohesive Soils a good compaction result by increasing the compaction frequencies be kept low by cultivators used. For non-binding, So sandy soil, however, is a high compression frequency sought to achieve a good compaction. About that In addition, from a vibrational point of view, they are in urban areas Regions higher excitation frequencies desirable. Natural frequencies of floor slabs are mostly in ranges between 10 to 30 Hz (Hertz). The risk of resonance effects is lower at higher frequencies.

mostly In this case, eccentrically rotating systems are used. An arrangement of masses rotating eccentrically about an axis according to physical laws to one radial centrifugal force about this axis, with a design-related Imbalance frequency and imbalance amplitude. The dynamic thus formed Forces are dissipated into the ground via slabs. As a result, the soil to be compacted is stimulated by its To move grain boundaries and its density and thus its rigidity to increase.

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.

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

These Task is solved by a cultivation compressor according to claim 1. Advantageous developments are in the dependent claims specified. For the invention important features can be found further in the following description and in the drawings, the features being both unique and different Combinations may be important to the invention without being explicitly mentioned again.

By the invention becomes clear the field of application of the add-on compactor extended, because with him can cohesive soils as well as nonbinding soils are optimally compacted, without time-consuming rebuilding work on the excavator or on the compactor required are. This is also especially useful to Resonances of possibly in the working area of the add-on compactor lying structures, such as buildings, bridges, Piers and the like, so that they are not damaged. By the switching means is a drive of a hydraulic motor determining volume flow and consequently the speed of the drive shaft changed during operation.

there The invention is based on an imbalance, as in so mentioned cultivation compressors is used, especially in Models that can be coupled to an excavator. there It is beneficial if the attached compressor from a hydraulic system is driven and controlled, preferably from that of the excavator. It uses the fact that rotating masses, their focal points eccentric to its axis of rotation, generate an imbalance. These can be based on the theorem of Steiner for individual or determine several rotating masses. It is intended that the rotating masses depending on a direction of rotation a drive shaft to take different end positions to each other. This is achieved by making part of the rotating masses rigid coupled with the drive shaft, another part in contrast a certain angle range is pivotable about the drive shaft, for example, in a range of about 180 degrees.

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

The unbalance generator should one or more rigid with respect to the drive shaft rotating Masses and one or more rotating masses pivotable about the drive shaft in an angular range of up to about 180 degrees, and these should be arranged on the drive shaft so that imbalances occur only in a plane determined by the direction of rotation. 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 flexible if a use of more than three total rotating masses is taken into account. Changing the direction of rotation of the drive shaft can be easily achieved by reversing the flow direction of the hydraulic flow driving the hydraulic motor ("flow rate").

To It is proposed that the cultivating compressor is a switching means for Contains change in the speed of the drive shaft, which has a hydraulic switching valve, and which in a first position releases an additional volume flow and in a second position the additional volume flow locks. This can be done by connecting a parallel path the volume flow to drive the hydraulic motor increases and its speed are increased, resulting in a corresponding Increasing the beat frequency results. This variant is without great constructive changes, too existing versions of add-on compactors realized and thus comparatively inexpensive. Possibly. is this Variant can be retrofitted even with existing add-on compactors.

A Modification to this provides that the switching means a hydraulic Switching valve which, in a first position, a first Volume flow and in a second position, a second volume flow releases. This results in a constructive simplification of Hydraulics of the crop compactor, adding a change the volumetric flow can occur over a single element, and a switchable parallel path is not required.

Especially it is useful if the switching means by a hydraulic Switching pulse or electrohydraulic or manually operable is. As a result, the hydraulic flow can be applied to one of a type of Or unbalanced or dredged or adapted to the excavator be switched. In particular, the switching is by a short hydraulic impulse ("ballpoint principle") advantageous if a manual conversion is out of the question and an electrical or additional hydraulic connection between the attached compactor and the excavator operating it is provided.

A further embodiment of the add-on compactor according to the invention is that it has three operating states according to the direction of rotation and the position of the switching means, wherein the first operating state has approximately the same speed of the drive shaft as a greater eccentricity than the second operating state, and wherein the second operating state same eccentricity as, however, has a lower speed than the third operating state. 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 100 kN) X2 small medium (about 45 Hz) medium (about 60 kN) X3 small large (about 60 Hz) big (about 100 kN)

In mode X1, the pivotable rotating mass in the same direction Aligned to the rigid rotating masses, leaving a maximum unbalance gives which an imbalance amplitude or impact of about 100 kN. The hydraulic motor driving the hydraulic motor is set so that there is a beat frequency of about 35 Hz results.

In mode X2, the pivotable rotating mass is in opposite directions Aligned to the rigid rotating masses, leaving a minimal unbalance gives which an imbalance amplitude or impact caused by about 60 kN. The hydraulic motor driving the hydraulic motor remains unchanged compared to the X1 mode, so that as a result of the relief by the lower imbalance one slightly increased beat frequency of about 45 Hz.

In X3 mode, the pivoting rotating mass, as in X2 operation, is opposite to the aligned to rigid rotating masses. 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 similarly increased beat frequency of about 60 Hz. In turn, due to the faster rotation, a high imbalance amplitude or impact force, similar to the X1 operation of about 100 kN, is achieved despite an equal mass distribution to X2.

The three operating modes X1, X2 and X3 can be used alone a changeover or switching of the hydraulic control, the basic hydraulics of the excavator being structurally the same. In order to is an excessive construction effort avoided. Furthermore, the mode X1 can be a basic mode from which each switch to X2 or X3 mode and, if necessary, switched back again.

A Another important embodiment of the invention is that the pivotable mass relative to the drive shaft and a for Drive shaft parallel or coaxial axis from a first in a second position and is pivotable back and at least having a stop surface with a relative to the drive shaft rigid but cooperates in rubber-elastic bump stop, wherein the stop surface is parallel to the drive shaft Axis is pivotally mounted. This is the following consideration. Underlying: It makes sense, the first and the second position so to choose that two very different eccentricities arise. The required limit is set with the help of a two-sided acting stop device, consisting of a rotatable mounted stop bolts and, for example, four stop buffers realized. The case of a change in the direction of rotation of the drive shaft occurring angular acceleration leads together with the Moment of inertia of the pivotable rotating mass too high Forces when reaching the end positions. The stop buffers absorb these forces and absorb at least one Part of the kinetic energy.

For example are the bumpers as progressively working structure damper made of a material that is whole or partial Made of co-polyester elastomers and on a metal surface the rigid rotating masses are vulcanised. It can be beneficial be to design the stop buffer as (dense) hollow body, so that the air contained in it contributes to the energy intake is. Preferably, the stop pin (mirror image to its ends) a total of four abutment surfaces, namely two for each of the two end positions of the swiveling rotating mass. This becomes one - based on a cylindrical basic shape of the stop bolt - as large as possible Area for the stop determining zone allows. ever greater the area determining the stop is, the lower the occur during a stop Compressive stresses in the stop buffers.

The Rotatability of the stop pin causes that this automatically when hitting the stop buffers themselves adjusted so that the stop surfaces of the stop pin the surfaces of the stop buffer at least approximately plane-parallel touch. The stop pin can so during Turn the deformation phase of the stop buffer and so a flat Contact the stop surfaces with the stop buffers maintained. It helps if the stop bolts only in a limited angular range rotatable about its axis is, for example, in an angular range of +/- 12 degrees. In addition, the limitation of the angular range prevents that the stopper bolt in a bore receiving it due Vibrations begin to turn uncontrollably.

proposed further, that the mass comprises a plurality of sub-masses, which are accommodated in a receiving space whose volume is larger is the total volume of the sub-masses, and the at least one Having boundary wall, which the sub-masses in the first direction of rotation in a first position and in the second direction of rotation in a second Position forces, where the overall center of gravity of the sub - masses in the the first position has a different total distance to the axis of rotation than in the second position. Such an imbalance generator works very wear-resistant and therefore has a long life.

following Example embodiments of the invention below Explained referring to the drawing. In the drawing demonstrate:

1 a schematic side view of a mounted compressor;

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

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

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

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

6 a representation similar to 5 for a second mode of operation;

7 a representation similar to 5 for a third mode of operation;

8th a circuit diagram of a second embodiment of a hydraulic circuit of the add-on compactor of 1 ; and

9 a section through an alternative embodiment of an unbalance generator of the add-on compactor of 1 ,

In all figures are for functionally equivalent Parts or sizes each have the same reference numerals used.

In the 1 is a mounted compactor 10 shown, the one unbalance generator 12 includes. The imbalance generator 12 is with a hydraulic motor 13 connected, which in turn is connected to the hydraulic system of an excavator, not shown. By the imbalance generator 12 becomes a compressor plate during operation 14 vibrated. The compactor plate 14 is about fasteners 15 and buffering devices 16 , in particular metal rubber buffer, with an upper part 17 of the attached compactor 10 elastically connected. The mounted compactor 10 is about a recording 18 on an excavator arm 19 fixable. The recording 18 can be designed 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 picture 18 closes a rotary motor 20 on, about the attached compactor 10 concerning the excavator arm 19 can be twisted. The hydraulic motor 13 is with interposition of a valve block 60 via hydraulic lines 21 and the recording 18 connected to the hydraulic system of the excavator. Over the valve block 60 can the volume flow, from the excavator to the hydraulic motor 13 can be adjusted in various ways, as described below with reference to the 5 to 8th will be explained. The flow direction of the hydraulic flow to the hydraulic motor 13 can be reversed on the backhoe.

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

Between the opposite to the drive shaft 30 rigid rotating masses 32a and 32b is located opposite to the drive shaft 30 swiveling rotating mass 36 , The pivot axis of the mass 36 is coaxial with the drive shaft 30 , By pivoting, the mass 36 relative to the drive shaft 30 and the two to the drive shaft 30 rigid masses 32a and 32b be brought into one of two end positions. In 2 is the pivoting rotating mass 36 with respect to the drive shaft 30 the rigid rotating masses 32a and 32b opposite, so that in the sum of all three masses 32a . 32b . 36 gives a relatively small imbalance.

3 shows the imbalance generator 12 with the pivoting rotating mass 36 in the other of the two possible end positions: the mass 36 is in the axis direction of the drive shaft 30 seen mostly in the same flight with the rigid rotating masses 32a and 32b arranged, that is from the drive shaft 30 Seen on the same page as the rigid rotating masses 32a and 32b , so that in the sum of all three masses 32a . 32b . 36 results in a relatively large imbalance.

In a receiving hole 38 the pivoting rotating mass 36 is one with the stop buffers 34 on the rigid rotating masses 32a and 32b in yet darzustellender manner cooperating rotatable stopper bolt 40 housed, with its projecting ends on both sides of the mounting hole 38 survives. Each projecting end has two oppositely disposed plane-parallel to stop faces 42 on. In 3 are two shaped holes 44 in the pivoting rotating mass 36 visible, which have a slot-like shape in their cross section. In it are two cylindrical pins 46 recorded, the at its invisible end firmly in the stop bolt 40 are anchored. In this way is the stopper bolt 40 in the receiving hole 38 according to the geometry of the formed holes 44 rotatable around a small area.

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

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 orthogonal to the longitudinal axis of the drive shaft 30 is and through the in 3 shown line IV-IV goes. In the stop bolt 40 are the pins 46 firmly anchored, for example, pressed or screwed. At a rotation of the stop pin 40 in the receiving hole 38 be the pins 46 in the formed hole 44 , limited by the size of the column 48 , pivoted. This is the stop pin 40 over an angular range 50 in terms of one through its central axis 52 going reference line 54 limited rotation.

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

Starting from the hydraulic motor 13 (in the upper part of the figure) flows marked by a black triangle symbols return current 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 ever a flow control valve 70 and 72 , The latter in series with a switching valve 88 , The switching valve 88 can be actuated either manually or by a remote electrical action (electrohydraulic valve). The Elements 66 . 70 . 72 and 88 form a total of a hydraulic switching means 87 ,

Parallel to the hydraulic motor 13 are in opposite directions two pressure relief valves 82 and 84 arranged, 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 with the quick coupling 62 for returning any leakage currents.

In 5 is the hydraulic circuit 60 represented in a so-called "X1" operation. In this are located at the P port of the quick coupling 62 a high supply pressure and at the R port to a return pressure. The switching valve 88 is closed. Hydraulic fluid flows over 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 the point 68a controls the check valve 68 on. Without the use of the check valve 68 There is a risk of cavitation of the hydraulic motor 13 when switching off. In this X1 operating mode the unbalance generator rotates 12 in a first direction of rotation in which the pivotable rotating mass 36 in the in 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.

6 shows the hydraulic circuit 60 at one opposite 5 reverse flow direction of the hydraulic flow, which is referred to as "X2" operation. Starting from the pressurized port R of the quick coupling 62 flows the flow stream 64 now over the check valve 68 and the flow control valve 70 towards the hydraulic motor 13 , The flow control valve 70 again has the task of hydraulic power independent of pressure. Starting from the hydraulic motor 13 the return current flows 74 over 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, the unbalance generator rotates 12 in a second direction of rotation, in which the pivotable rotating mass 36 in the in 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.

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

8th shows a schematic of a modified embodiment of a hydraulic circuit of the valve block 60 to operate and control the unbalance generator 12 , in which, deviating from the representations of 5 to 7 , in place 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"). This is a hydraulic control current 92 used tapped at a suitable location on the pressurized branch downstream of the P-port. If necessary, the pressure relief valves 82 and 84 for operation with a pulse valve 90 be set to other thresholds 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 in 9 shown. It is true that such elements and areas that are functionally equivalent to in previous elements and areas, the same reference numerals and are not explained again in detail.

The imbalance generator 12 comprises a cylindrical or drum-shaped closed housing 94 which is eccentric about a drive shaft 30 is arranged. Inside the case 94 is a recording room 96 formed, inter alia, by a hollow boundary wall 98 is limited, which is approximately from the geometric center of the housing 94 extends radially outward. In the recording room 96 is a certain number of balls 100 present, which are also referred to as "sub-masses" and so an amorphous moving mass 36 form. Turn the case 94 around the drive shaft 30 clockwise, the balls will be 100 in the in 9 shown forced position in which they are a relatively small distance from the drive shaft 30 to have. The eccentricity is thus comparatively small. Turn the case 94 on the other hand counterclockwise, the balls become 100 forced in the opposite position, in which they are a relatively large distance from the drive shaft 30 exhibit. The eccentricity is thus comparatively large.

QUOTES INCLUDE IN THE DESCRIPTION

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Cited patent literature

• - DE 202005006059 U1 [0004]

Claims (10)

Cultivation compressor ( 10 ), which can be coupled to an excavator, with a preferably hydraulically driven unbalance generator ( 12 ) with at least one rotating mass ( 32 . 36 ), which relative to the drive shaft ( 30 ) is movable such that, in a first direction of rotation of a drive shaft ( 30 ) a first eccentricity and in a second direction of rotation a second eccentricity relative to a rotational axis of the drive shaft ( 30 ), characterized in that the cultivation compactor ( 10 ) at least one switching means ( 87 ), with which the speed of the drive shaft ( 30 ) can be changed during operation. Cultivation compressor ( 10 ) according to claim 1, characterized in that the switching means ( 87 ) a hydraulic switching valve ( 88 ; 90 ), which releases an additional volume flow in a first position and blocks the additional volume flow in a second position. Cultivation compressor ( 10 ) according to one of the preceding claims, characterized in that the switching means ( 87 ) a hydraulic switching valve ( 88 . 90 ), which releases a first volume flow in a first position and a second volume flow in a second position. Cultivation compressor ( 10 ) according to one of the preceding claims, characterized in that the switching means ( 87 ) by a hydraulic switching pulse or electro-hydraulically or manually operable. Cultivation compressor ( 10 ) according to one of the preceding claims, characterized in that it corresponds to the direction of rotation and the position of the switching means ( 87 ) has three operating states, wherein the first operating state, an approximately equal speed of the drive shaft ( 30 ) but having a greater eccentricity than the second operating state, and wherein the second operating state has the same eccentricity as a lower rotational speed than the third operating state. Cultivation compressor ( 10 ) according to claim 5, characterized in that the rotational speeds and eccentricities are coordinated so that the impact force of the add-on compactor ( 10 ) In the first operating state at least approximately corresponds to the impact force in the third operating state. Cultivation compressor ( 10 ) according to one of claims 5 or 6, characterized in that a striking frequency of the add-on compactor ( 10 ) is approximately 35 Hz in the first and second operating states and approximately 60 Hz in the third operating state. Cultivation compressor ( 10 ) according to one of the preceding claims, characterized in that the mass ( 36 ) relative to the drive shaft ( 30 ) and one to the drive shaft ( 30 ) parallel axis from a first to a second position and back is pivotable and at least one stop surface ( 42 ) having a relative to the drive shaft ( 30 ) but in themselves rubber-elastic bumpers ( 34 ), the stop surface ( 42 ) to one to the drive shaft ( 30 ) is mounted pivotably parallel axis. Cultivation compressor ( 10 ) according to claim 8, characterized in that the stop surface ( 42 ) only in a limited angular range ( 50 ) is pivotable. Cultivation compressor ( 12 ) according to one of claims 1 to 7, characterized in that the movable mass ( 36 ) a plurality of sub-masses ( 100 ) located in a receiving room ( 96 ) whose volume is greater than the total volume of the sub-masses ( 100 ), and the at least one boundary wall ( 98 ), which 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 a different distance to the drive shaft ( 30 ) than in the second position.