Vibration generator and method for generating vibrations

Abstract

A vibration generator has a first rotationally drivable imbalance shaft, on which a first imbalance is arranged, at least one second rotationally drivable imbalance shaft, on which a second imbalance is arranged, a joint drive for rotationally driving the two imbalance shafts and a transmission arrangement which is arranged between the drive and the imbalance shafts for transmitting a torque of the drive to the imbalance shafts. The transmission arrangement distributes an input torque of the drive to a first output element for the first imbalance and a second output element for the second imbalance. For the torque transmission a first deflection element is arranged between the transmission arrangement and the first imbalance shaft and for the torque transmission a second deflection shaft is arranged between the transmission arrangement and the second imbalance shaft.

Claims

1. Construction machine having a mast, which is arranged on a carrier and having a vibration generator having a housing, a first rotationally drivable imbalance shaft, on which a first imbalance is arranged, at least one second rotationally drivable imbalance shaft, on which a second imbalance is arranged, a drive for rotationally driving the imbalance shafts and a transmission arrangement which is arranged between the drive and the imbalance shafts for transmitting a torque of the drive to the imbalance shafts, and a clamping means for clamping a sheeting element for the soil, which is fixed at the housing, wherein the vibration generator is arranged on a carriage guided on the mast, and the transmission arrangement and the drive of the vibration generator are fixed on the carriage, wherein the transmission arrangement distributes an input torque of the drive to a first output element for the first imbalance and at least one second output element for the at least one second imbalance, for the torque transmission a first deflection element is arranged between the first output element of the transmission arrangement and the first imbalance shaft and for the torque transmission a second deflection element is arranged between the second output element of the transmission arrangement and the second imbalance shaft, wherein the first deflection element and the second deflection element are each designed to permit a deflection mainly in a direction transverse to a shaft axis, and wherein the first deflection element compensates for an axial offset between the first output element and the first imbalance shaft and the second deflection element compensates for an axial offset between the second output element and the second imbalance shaft.

2. Construction machine according to claim 1, wherein in order to form an imbalance unit the first imbalance shaft is rotatably supported inside the second imbalance shaft and in that the second imbalance is arranged in a circulating manner around the first imbalance.

3. Construction machine according to claim 1, wherein at least one of the deflection elements is a Cardan shaft which has a Cardan joint on at least one side.

4. Construction machine according to claim 1, wherein at least one of the deflection elements has a coupling with a radially displaceable coupling disk.

5. Construction machine according to claim 1, wherein at least one compensating element is designed as a movable hollow shaft, in particular as a metal bellows tube.

6. Construction machine according to claim 1, wherein the transmission arrangement is provided on one side of the imbalance unit.

7. Construction machine according to claim 1, wherein an adjustment motor for adjusting an angular offset of the imbalances to each other is arranged on the transmission arrangement.

8. Construction machine according to claim 1, wherein the second imbalance shaft is rotatably supported in a housing that surrounds the first imbalance and the second imbalance.

9. Construction machine according to claim 1, wherein the vibration generator is guided on a leader.

10. Construction machine according to claim 1, wherein the drive is for driving the two imbalance shafts in a counter-rotating manner.

11. Construction machine according to claim 1, wherein the drive is for driving the two imbalance shafts synchronously.

12. Construction machine according to claim 1, wherein the clamping means is for introducing the sheeting element into the soil.

Description

(1) The invention is set out hereinafter by way of preferred embodiments illustrated schematically in the accompanying drawings, wherein show:

(2) FIG. 1 a side view of a first vibration generator with three imbalance units and a transmission arrangement on one side for the invention;

(3) FIG. 2 a side view of a second vibration generator with four imbalance units and a transmission arrangement on one side for the invention;

(4) FIG. 3 a side view of a third vibration generator with three imbalance units and a transmission arrangement on two sides for the invention;

(5) FIG. 4 a cross-sectional view of a further embodiment of a vibration generator for the invention;

(6) FIG. 5 a first perspective view of a compensating coupling; and

(7) FIG. 6 a second perspective view of a compensating coupling.

(8) FIGS. 1 to 3 each show a vibration generator 100, 200 with a plurality of imbalance units 2. In all of these embodiments of the vibration generator 100, 200 the individual imbalance units 2 are substantially of the same design.

(9) A single imbalance unit 2 comprises a first imbalance shaft 12 with a first imbalance 10 and a second imbalance shaft 22 with a second imbalance 20. The first imbalance shaft 12 and the second imbalance shaft 22 are supported coaxially, with the first imbalance shaft 12 being located at least in sections inside the second imbalance shaft 22.

(10) The second imbalance shaft 22 is designed as a hollow shaft. The first imbalance shaft 12 is supported by means of a first imbalance radial bearing 14 in the second hollow imbalance shaft 22.

(11) On the first imbalance shaft 12 the first imbalance 10 is arranged by way of a shaft-hub-connection 13. The shaft-hub-connection 13 can be a fitted key connection. The second imbalance shaft 22 surrounds the first imbalance 10, with the second imbalance 20 being arranged in such a manner on or in the peripheral surface of the second imbalance shaft 22 that it is arranged offset radially outwards with respect to the joint shaft axis 3 of the coaxially arranged first imbalance shaft 12 and the second imbalance shaft 22. If both imbalances 10, 20 are set into rotation the second imbalance 20 thus circulates around the first imbalance 10.

(12) The second imbalance shaft 22 is supported in a housing 50 by way of second imbalance radial bearings on both ends of the second imbalance shaft 22. Second imbalance radial bearings 24 and first imbalance radial bearings 14 are arranged at the end sections of the first imbalance shaft 12 and the second imbalance shaft 22, with the two imbalances 10, 20 being arranged in-between the two end sections. The housing 50 thus surrounds the two imbalances 10, 20 that can rotate in the interior of the housing 50. The housing 50 can encase the imbalances 10, 20 and at least in sections the imbalance shafts 12, 22. The imbalance units 2 and the housing 50 form a vibrating unit since vibrations generated by the imbalances are transmitted via the imbalance shafts 12, 22 to the housing 50.

(13) Furthermore, FIGS. 1 to 3 each show a clamping means 60 as a working tool, onto which vibrations can be transmitted with the vibration generators 100, 200 according to the invention.

(14) In FIGS. 1 and 2 the two imbalance shafts 12, 22 are articulated by way of a Cardan shaft 15 and a movable hollow shaft 115 on a transmission arrangement 30. These two deflection shafts, the Cardan shaft 15 and the movable hollow shaft 115, are arranged coaxially. The Cardan shaft 15 is located in the interior of the movable hollow shaft 115. In an idle position of the vibration generator 100 a joint shaft axis of the Cardan shaft 15 and the movable hollow shaft 115 can be parallel to the shaft axis 3 of the imbalance shafts 12, 22.

(15) The Cardan shaft 15 is articulated by way of a first Cardan joint 5 on the first imbalance shaft 12 and by way of a second Cardan joint 5 on a transmission shaft 37 of the transmission arrangement 30, which is rotationally driven by a drive (not shown). A torque of the driven transmission shaft 37 can thus be transmitted via the Cardan shaft 15 to the first imbalance shaft 12 and the first imbalance 10.

(16) The movable hollow shaft 115 can be designed as a metal bellows tube for example. The movable hollow shaft 115 is flanged by way of a first hub 7 on the second imbalance shaft 22. This first hub 7 can therefore be referred to as imbalance hub of the movable hollow shaft 115. At the other end of the movable hollow shaft 115 it is flanged by way of a second hub 7 on an output gearwheel rim 35 of the transmission arrangement 30. The second hub 7 can therefore be referred to as gearwheel hub of the movable hollow shaft 115. For a torque transmission from an output gearwheel rim 35 of the transmission arrangement 30 to the second imbalance shaft 22 the movable hollow shaft 115 is flanged by means of two flange hubs 7. By way of a gearwheel rim bearing 39 the output gearwheel rim 35 can furthermore be supported radially on the driven transmission shaft 37. By way of the transmission arrangement 30 a torque can be transmitted from the driven transmission shaft 37 via an adjustment motor 40 to the output gearwheel rim 35 and therefore also to the movable hollow shaft 115 and the second imbalance shaft 22.

(17) If the imbalance units 2 and the housing 50 are set into vibration, both the Cardan shaft 15 and the movable hollow shaft 115 can move in the direction of the vibrations and thereby absorb or cushion vibrations.

(18) In FIG. 1 a transmission arrangement 30 is shown that transmits a torque of a drive (not shown) to three imbalance units 2. The transmission arrangement 30 has two power trains that are both driven by the drive. The two power trains extend from the adjustment motor 40 which has two intermediate gearwheels 32, 33 that can be adjusted to each other and locked. When the intermediate gearwheels 32, 33 are locked a torque can be transmitted from the drive via the adjustment motor 40 to the imbalance shafts 12, 22 and when the intermediate gearwheels 32, 33 are not locked an angular offset between the imbalances 10, 20 can be set or corrected by the adjustment motor 40.

(19) The first power train forms a spur gear transmission of several drive wheels 36 that engage with each other and are driven synchronously by the driven transmission shaft 37. On each of these drive wheels 36 a transmission shaft 41 is located axially that is connected in a torsionally rigid manner via one of the Cardan joints 5 to a Cardan shaft 15 in each case. One of the transmission shafts 41 is the driven transmission shaft 37.

(20) The drive wheels 36 of the spur gear transmission can have the same circumference, whereby the transmission shafts 41 are driven at the same rotational speed and therefore the imbalance shafts 12 articulated by way of the Cardan shafts 15 also rotate at the same rotational speed.

(21) For the torque transmission from the drive to the second imbalances 20 the second power train has several output gearwheel rims 35. As spur gear transmission the output gearwheel rims 35 are in engagement with each other and driven via the intermediate gearwheels 32, 33.

(22) The output gearwheel rims 35 can also have the same circumference and therefore be driven at the same rotational speed. The transmission shafts 41 of the first power train are each supported in the output gearwheel rims 35 by means of a transmission shaft radial bearing 38. Hence, a transmission shaft 41 runs through an output gearwheel rim 35.

(23) The adjustment motor 40 can be designed such that the two intermediate gearwheels 32, 33 and therefore also the two imbalance shafts 12, 22 are driven in a co-rotating or counter-rotating manner by the drive.

(24) The drive, the adjustment motor 40 and/or the transmission arrangement 30 can be fixed on a construction machine or a construction tool (both not shown). Due to the movable articulation by way of the Cardan shafts 15 and the movable hollow shafts 115 vibrations of the imbalance units 2 and the housing 50 are absorbed by the deflection shafts, the Cardan shafts 15 and the movable hollow shafts 115. Hence, the vibrations generated by the imbalance units 2 are substantially not transmitted to the transmission arrangement 30 and the drive. To fix the transmission arrangement 30 holders 70 are shown to some extent, in which the transmission shafts 41 can be supported by way of transmission shaft radial bearings 38. Further holders for fixing the transmission arrangement 30, the adjustment motor 40 and the drive, for instance on the non-depicted construction machine or the construction tool, can be provided in addition.

(25) FIGS. 1 to 3 each show a clamping means 60 that is fixed on the vibrating housing 50. The clamping means 60 can clamp a sheet pile element for example in order to transmit thereto vibrations of the vibration generator 100, 200.

(26) The embodiment of the vibration generator 100 shown in FIG. 2 solely differs from the embodiment shown in FIG. 1 in that four imbalance units 2 instead of three imbalance units 2 are provided. In principle, the vibration generator 100 can be designed with any number of imbalance units 2.

(27) However, a plurality of imbalance units 2 advantageously describes a vibration redundancy concept to enhance the generated vibrational forces.

(28) The embodiment shown in FIG. 2 additionally differs from the embodiment shown in FIG. 1 in that the adjustment motor 40 is arranged centrally, in which case the first and the second intermediate wheel 32, 33 transmit a torque to power trains lying opposite in each case that can otherwise be designed identically to the power trains in FIG. 1.

(29) While in FIGS. 1 and 2 the drive, the adjustment motor 40 and the transmission arrangement 30 are arranged on one side of the imbalance units 2 and the housing 50, in the embodiment of the vibration generator 200 shown in FIG. 3 the transmission arrangement 30 is located on both sides of the imbalance units 2.

(30) While in the embodiments of the vibration generator 100 in FIGS. 1 and 2 the imbalance shafts 12, 22 are articulated on one side on the transmission arrangement 30, the imbalance shafts 12, 22 in FIG. 3 are articulated on two opposite sides.

(31) In FIG. 3 the first imbalance shaft 12 is articulated by way of a first Cardan shaft 15 on a first power train of the transmission arrangement 30 and the second imbalance shaft 22 is articulated by way of a second Cardan shaft 225 on a second power train of the transmission arrangement 30.

(32) Both Cardan shafts 15, 225 each have two Cardan joints 5. The Cardan shafts 15, 225 can thus be designed as a double-joint shaft. The first Cardan shaft 15 is articulated by way of a Cardan joint 5 on the first imbalance shaft 12 and by way of a further Cardan joint 5 on a transmission shaft 41 of the first power train. The second Cardan shaft 225 is articulated by way of a Cardan joint 5 on the second imbalance shaft 22 and by way of another Cardan joint 5 on a transmission shaft 41 of the second power train.

(33) Both power trains each have several drive wheels 36 with a respective transmission shaft 41. The transmission shafts 41 are supported in transmission shaft radial bearings 38 of a holder 70.

(34) The imbalance shafts 12, 22 of the three imbalance units 2 shown in FIG. 3 can be driven synchronously by the transmission arrangement 30. For the torque transmission from a drive (not shown) to both power trains a drive shaft 242 is provided, on which the two intermediate gearwheels 32, 33 are arranged on the respective ends. The drive shaft 242 is supported by way of drive shaft radial bearings 243 in the holder 70. The holder 70 can be fixed on a construction machine or a construction tool, not depicted. The drive shaft 242 or one of the two intermediate gearwheels 32, 33 can be rotationally driven by the drive.

(35) The imbalance units 2 can thus vibrate centrally between the power trains of the transmission arrangement 30, while the Cardan shafts 15, 225 absorb the vibrations and substantially do not transmit these to the transmission arrangement 30.

(36) The embodiments of the vibration generator 100, 200 shown in FIGS. 1 to 3 illustrate that under the protection of a housing 50 pairs of imbalances 10, 20 arranged in a compact way can vibrate in a vibration-decoupled manner from a transmission arrangement 30.

(37) The compact arrangement of the imbalances in imbalance units 2 and the movable articulation principle separate from the imbalance shafts renders it possible to provide transmission arrangements both on one and on two sides.

(38) As a result of the vibration decoupling the transmission arrangement 30 is on the one hand subject to less stress and due to the described arrangement and articulation principle of the imbalance shafts 12, 22 the transmission arrangement 30 can be designed in a variable manner, in particular on one or on two sides.

(39) A further embodiment of a vibration generator 300 according to the invention is illustrated in FIG. 4. The basic construction of the vibration generator 300 with regard to the imbalance units 10, 20 corresponds to the previously described construction, while a total of four imbalance units 10, 20 is supported in the housing 50.

(40) The transmission arrangement 30 has a total of six shaft-like output elements, with reference being made for the following description to a first output element 77 and a second output element 78. In the illustrated embodiment the drive 80 has two hydraulic drive motors that introduce their torque into the joint transmission arrangement 30, with the introduced torque being evenly distributed by the transmission arrangement 30 to the output elements 77, 78. As set out before, provision is also made in a known manner for an adjustment motor 40 for relative adjustment of the imbalance units 10, 20.

(41) To compensate a possible radial shaft offset between a first imbalance shaft 12 of the first imbalance 10 with respect to the associated first output element 77 or between a second imbalance shaft 22 of the second imbalance 20 with respect to the associated second output element 78 of the transmission arrangement 30 a coupling 115 with a radially adjustable coupling disk 120 is arranged in each case. Such a coupling 115 can also be referred to as a compensation coupling or Schmidt coupling.

(42) Such a Schmidt coupling is graphically illustrated in FIGS. 5 and 6. The coupling 115 has a radially adjustable coupling disk 120 arranged between a right-hand drive disk 121 and a left-hand output disk 122. The drive disk 121 is attached coaxially to the first output element 77, i.e. the first output shaft of the transmission arrangement 30. Correspondingly, the output disk 122 is fixed in a torque-proof and coaxial manner on the imbalance shaft 12 of the first imbalance 10. To compensate a radial offset between the drive disk 121 and the output disk 122 the central coupling disk 120 is in each case connected in an articulated manner via three pivotable levers 125 to the drive disk 121 and the output disk 122 respectively. For this purpose, corresponding bearing pins 126 are in each case attached to the disks 120, 121, 122, on which bearing pins the deflectable levers are supported in a pivotable or rotatable manner. In this way, a torque can be transmitted by the coupling 115 between the output element and the associated imbalance shaft, while a radial offset between drive and output side can be compensated at the same time.