• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    compactor as well as process for compacting soils. in a compacting apparatus with at least one movable bandage (2), rotatable about a bandage axis (1), with coupled vibration exciter (30a, 30b) which around the bandage (1) generates oscillating torque , with unbalances (3) rotating in the same direction of rotation, phase-shifted by 180 degrees and having a drive shaft (5a, 5b) that projects coaxially to the bandage shaft (1), intended to drive the exciter 30a, 30b), it is envisaged that the bandage (2) will be split at least once and that each part of the bandage (2,2b) has at least two coupled vibration exciter (30a, 30b) integrated in the bandage. (2) and spaced from the bandage axis (1).
    公开号:BR112012012812B1
    申请号:R112012012812-4
    申请日:2010-11-29
    公开日:2019-07-02
    发明作者:Hans-Peter Ackermann；Peter Janner
    申请人:Hamm Ag；
    IPC主号:
    专利说明:

    Descriptive Report of the Invention Patent for COMPACTING EQUIPMENT AND PROCESS TO COMPACT SOILS. [001] The present invention relates to a compaction apparatus for compacting soils, according to the preamble of claim 1, as well as a process for compacting soils, according to claim 21.
    [002] Compaction devices are known, for example, in the form of a road roller.
    [003] Soil can be compacted to a large extent with the help of a roller, for example, asphalt coverings. Sufficient compaction is necessary to ensure soil resistance and durability. In the rollers, there is a differentiation between the dynamic action mode and the static action mode during compaction. In dynamic action mode, compaction is verified by movement and in static action mode, compaction is verified by the weight of the steamroller.
    [004] The steamroller can be a self-propelled vehicle and has at least one drum.
    [005] When curving with the drum of the compaction device, in the form of a steamroller, an internal and external radius of the drum appears at its lateral ends. At the edge of the drum, at the outer section of the curve, due to the longer path that was covered, the speed is higher than at the inner edge. With the increase in directional movement and, therefore, with a smaller radius of curves, the difference of these difficulties increases in a reciprocal sense. However, as a drum cannot rotate with different circumferential speeds at its lateral ends, the drum rolls in the center of its width at the base, that is, on the ground, whereas in the outer marginal regions of the drum there is a push movement ( slip) between the asphalt and the jacket
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    2/17 drum bearing. Because of this reason, it is useful to split the drum and drive both halves, one independently of the other, in order to reduce this forced effect in this way due to the smaller divided drum width.
    [006] Oscillating drums - as opposed to vibrating drums - are not produced in the split configuration, because the technical implementation is clearly more complex. The synchronization of the imbalance masses that generate the centrifugal forces must be ensured at any time, especially also in the case of a relative rotation of the two drums, in relation to each other.
    [007] In a known oscillating cylinder, according to the document WO 82/01903, two imbalance axes are provided that rotate in synchronism and that are driven by toothed belts through a central axis. In this way, a movement is forcibly applied to the roller which alternates rapidly back and forth, in rotation. The oscillating cylinder, therefore, is never suspended from the base.
    [008] In document WO 82/01903 (figure 5) four operational states typical of the oscillating system of an undivided drum can be verified, according to the state of the art. From left to right, the positions of the imbalance masses are shown in 90 ° rotation steps in advance (with phase lag). [009] Due to the coupled drive, the two imbalance masses (imbalance weights) rotate in the same direction. While in the operational states of the illustrations on the left side of figure 5, the centrifugal forces will eliminate each other, the rotational moment in the illustrations on the right side (figures 5B, 5D), due to the directions of the centrifugal forces F and the arms of lever x, a torque appears
    M = 2. x. F
    Petition 870190033194, of 5/5/2019, p. 4/33
    3/17 [0010] clockwise (Figure 5B) and, respectively, counterclockwise (figure 5D).
    [0011] Therefore, with each turning of the imbalance axis, the drum undergoes a small rotation to the left and right sides and begins to oscillate around the axis of rotation M of the drum.
    [0012] In vibrating drums, the division of the drum is already known, because it is technically easy to achieve. The description in figure 2 of the present application shows a sectional view of a divided vibrating drum. The two sections of the drum 2a, 2b are reciprocally screwed through a swivel connection. Here, the imbalance masses 3 for both drum sections 2a, 2b are arranged on the central imbalance axis 31 which is driven by a hydraulic motor 7. In the case of displacement on a curve and, therefore, the turning of the sections of drum 2a, 2b, relative to each other, nothing will change with respect to the vibration of the two drum sections 2a, 2b, with respect to each other, that is, the two sections of drum 2a, 2b vibrate in synchronism.
    [0013] A simple structure with a continuous central axis 33 for the actuation of the unbalanced masses 3 as in a vibrating drum, is shown in figure 3 for an oscillatory drum. This solution cannot solve the phase problem, due to the following reasons:
    [0014] When drum sections 2a, 2b (roller surfaces) are being rotated relative to each other, for example, in the displacement by curves, the position of the axes of imbalance 31a, 31b, with respect to each other will change , because the imbalance axes 31a, 31b are mounted on the respective drum sections 2a, 2b. As the imbalance masses 3, which are driven by toothed belts 32 by a central axis 33, preserve their orientation, the direction of the force effectiveness in the rotated section of the drum 2a, 2b will, each time,
    Petition 870190033194, of 5/5/2019, p. 5/33
    4/17 displaced (figure 4 to figure 7).
    [0015] For a better representation of the timing belt assembly in figures 4 to 7, the described timing belt assembly is being shown in the perspective view of figure 3.
    [0016] Figures 4 and 5 show the two drum sections 2a, 2b, before their turns. In figure 6 and figure 7 are shown the sections of the drum 2a, 2b after a 90 ° rotation of the section of the drum 2b. [0017] As an explanation, it should be considered that the drum section 2a does not change its position, while the drum section 2b continues to be rotated by 90 °. For visualization, the rotating central axis is also shown in a moment register and thus is virtually paralyzed. As shown in figure 7, the two unbalanced masses of the right section of the drum 2b are now superimposed. As the drive shaft 33 in the center of the drum is paralyzed, the toothed belt 32 has already rotated on the central belt drive pulley 21, having not changed the orientation of the unbalanced masses 3. Due to the new position, however, of the masses of imbalance 3, the centrifugal forces now induce the moment with maximum lever, which will cause the drum section 2b to rotate. In the position shown in figure 6, in turn, there is no moment, because the operating lever is equal to zero.
    [0018] The problem described has the consequence that the drum sections 2a, 2b cannot oscillate in synchronism. In an extreme case, when the two drum sections 2a, 2b work precisely in the opposite direction, push movements result in the gap between the drum sections 2a, 2b and in the adjacent regions that cause a break in the asphalt layer. Depending on the rotation of the drum sections 2a, 2b with respect to each other, phase errors from 0 ° to 180 ° may occur. Phase failures already on the order of 10 to 20 ° would result in asphalt scraping at the joint between drum sections 2a,
    Petition 870190033194, of 5/5/2019, p. 6/33
    5/17
    2b.
    [0019] The present invention, therefore, has the task of proposing a vibrating device, that is, a process for compacting soils that do not present the problems mentioned above.
    [0020] To solve this task, according to the invention, the characteristics of claim 1, that is, 21, serve.
    [0021] According to the invention, it is foreseen that in the case of a compacting device with at least one displaceable drum, rotatable around a drum axis, with oscillation drivers with coupled unbalance masses and producing oscillating torque around of the drum axis, masses of imbalance that rotate with 180 ° of phased phase, in the same direction of rotation and with a drive axis that moves coaxially towards the drum axis, and which is intended to drive the oscillation exciter , the drum is divided at least once and each section of the drum has at least two oscillation drivers, coupled and which are integrated in the drum with a distance from the axis of the drum.
    [0022] The respective oscillation drivers are mounted in respective sections of the drums.
    [0023] Preferably, the driving axes for the oscillation exciter of the different drum sections are mechanically coupled or through a control means adjusted to be in phase, so that the oscillation exciter of all drum sections also oscillate with respect to each other when the drum sections are turned.
    [0024] The command can be processed electrically, electronically or hydraulically / pneumatically.
    [0025] The drive shafts for the oscillation exciter of the contiguous drum sections can be mechanically coupledPetition 870190033194, from 05/04/2019, p. 7/33
    6/17 through a transmission, this transmission transferring the swing, that is, the moment of activation of a drive axis, in the right phase to the next drive axis.
    [0026] The transmission for coupling the sections of the drive shafts can be a planetary gear transmission or a gear transmission or a bevel gear transmission.
    [0027] The drum is divided into two sections and each drum section has its own displacement drive, with the two drum sections being interconnected, being axially rotatable, relative to each other.
    [0028] A planetary transmission that can preferably be used can consist of at least two sets of planetary gears.
    [0029] The planetary transmission, constituted of two sets of planetary gears, can present a common planetary conveyor, being that the annular gears of the planetary gear sets are coupled to the rotation proof with a section of the drum and the respective driving axes are united with the respective central transmissions of the planetary system of the planetary gear sets.
    [0030] The transmission for driving the unbalanced masses can be a belt or chain transmission.
    [0031] The transmission to drive the oscillation exciter will preferably be a toothed belt drive with omega wrapping, which drives toothed belt pulleys, coupled with unbalanced masses.
    [0032] The transmission will preferably be a belt transmission with a belt conduction that allows an inversion of the turning direction and a reciprocal transmission rate, in relation to the
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    7/17 planetary transmission.
    [0033] The transmission rate of the belt transmission and the transmission rate of the planetary transmission should altogether provide a transmission ratio of 1: 1.
    [0034] A multi-stage planetary transmission and a belt drive may also be provided, without reversing the direction of rotation and without reciprocal transmission rate in relation to planetary transmission.
    [0035] The oscillation drivers have weights of unbalanced masses and these unbalance weights preferably consist of unbalance plates which are preferably attached laterally to the belt pulleys of the belt transmission and have a flank that projects radially inwards and that, in a given output position, is aligned with the belt of the belt transmission, when the offset of the rotation angle between the two imbalance axes, that is, belt pulleys driven by the belt transmission, corresponds to the desired value . Preferably, the belt transmission will be a toothed belt transmission.
    [0036] A belt tensioning assembly can protect the belt to drive the unbalanced masses, that is, the belt disc with the help of a rolling pin, eccentrically displaceable to the belt disc.
    [0037] The belt tensioner assembly may have an eccentric adjustment pin to rotate and secure the eccentric mounting pin. [0038] In the direction of the axis of rotation of the imbalance, the belt transmissions may have coaxial and concentric belt pulleys, whose weight distribution does not occur with rotational symmetry, in relation to the axis of rotation of the imbalance masses.
    [0039] Cutouts, preferably holes and perforations, provision 870190033194, dated 05/05/2019, p. 9/33
    8/17 asymmetrically in relation to the axes of rotation of the imbalance masses, and provided for in the material of the toothed belt disc, can produce a weight distribution that is not of rotational symmetry, forming a negative imbalance mass.
    [0040] Side-mounted imbalance plates can be attached to the belt pulleys and / or asymmetrically exposed screws that form an imbalance weight, and the screws can also be used to fix the imbalance plates.
    [0041] In order to receive the rolling bearings of the unbalanced masses, flywheel pins may be provided, with the mounting sections, that is, the bearings being preferably centrally arranged in relation to the radial force of the belt and the centrifugal radial force. of the masses of imbalance.
    [0042] To secure the belt, these rolling pins for the purpose of prestressing the belt are mounted in the grooves of the drum sections.
    [0043] For compacting soils with a drum of a compaction device, it is planned to generate compaction oscillations of the drum, at least with the aid of an oscillation exciter and with rotary unbalance weights, and by using a drum divided with two drum halves, when the unbalance weights of the oscillation drivers are rotated, relative to each other, in each part of the drum at the same angle, relative to the phase position as the relative rotation of the drum halves in a reciprocal direction, aiming to achieve a synchronization of the rotating movement in the two halves of the drums, also when the halves of the drums are rotated, relative to each other.
    [0044] A mechanical relationship must make it possible to synchronize the excitation forces in the two drum halves. This function is performed by a multi-stage planetary transmission.
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    9/17 [0045] In this case, it is up to a transmission to transfer the moment of the hydraulic motor in the correct phase to activate the unbalanced masses from the left drum to the right drum, on the correct face.
    [0046] In the following, with reference to the drawings, examples of carrying out the invention will be explained.
    [0047] The figures show:
    [0048] Figure 1 a vibrating device, [0049] Figure 2 a divided vibrating drum of the DV90 cylinder according to the state of the art, [0050] Figure 3 simple toothed belt drive for split oscillation, with which the phase problem cannot be solved, [0051] Figures 4 to 7 different drum positions, [0052] Figure 8 section view of the drum, according to the invention, [0053] Figure 9 a planetary game, [0054] Figure 10 a drive of toothed belt with omega wrapping, [0055] Figure 11 the eccentricity of the unbalance flange / rolling pin, and [0056] Figure 12 a perspective view of a toothed belt disc.
    [0057] Figure 1 shows as an example for a vibrating device a compactor roller, which is especially a vibrating tandem roller, preferably with a front drum 2 and a rear drum.
    [0058] Figures 2 to 7 explain - as already mentioned in the introduction to the description - the state of the art.
    [0059] Figure 8 shows a drum 2 divided and able to oscillate. The two drum sections 2a, 2b with transmission are shown
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    10/17 integrated, for example, planetary transmission 6 shown in figure 9, to solve a phase problem in displacement by curves, unbalance masses (unbalance weights) 3 of the oscillation exciter 30a, 30b and the attached components.
    [0060] Displacement drives 7a, 7b activate the respective drum sections 2a, 2b. The planetary transmission 6 has two sets of planetary gears 6a, 6b.
    [0061] Each drum section 2a, 2b has a front insert 12a, 12b, provided on the inside, on which are installed, for example, rolling pin 20a, 20b for receiving unbalanced masses 3 rotating from the oscillation exciter 30a, 30b. [0062] The ring gear 10a on the left side of the first planetary set 6a is fixedly joined by the rolling pin 16a and the socket 12a with the drum section 2a on the left side of the drum 2. The ring gear 10b on the right side of the drum, in turn, through the bearing pin 16b and the socket 12b it is coupled to the section of the drum 2b on the right side of the drum 2.
    [0063] Figure 9 shows the structure of a planetary transmission 6.
    [0064] The synchronization of the moments of imbalance does not depend on the rotation of the drum sections 2a, 2b. For the simplest explanation, let's assume the following:
    [0065] The hydraulic motor 7 to activate the oscillatory movements is running, the drum sections 2a, 2b are not running, that is, the two drum sections 2a, 2b are paralyzed. Therefore, the two ring gears 10a, 10b, shown in figure 9, are blocked because - as already mentioned, they are rigidly and counter-rotated with the drums 2a, 2b.
    [0066] In the planetary game 6a on the left side of figure 9, a moment of activation, transmitted by the hydraulic motor 7 to the
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    11/17 drive shaft 5a (solar gear), through this solar gear 11a and the planetary gears 8a is advanced for the planetary conveyor 9. Here case 3 (solar gear, drives fillet and thrust) of the elementary planetary set of according to table 2. The transmission ratio i is in the case, therefore, 3. [0067] The numbers of teeth of the planetary transmission wheels 6 for the calculation of the transmission ratio ratio are listed in table 1.
    Table 1: Number of teeth of the transmission wheels
    Wheel 1 2 3 Gearsolar Gearplanetary Gearcancel Number ofteeth 40 20 80
    [0068] From the planetary conveyor 9, the moment will be transmitted (figure 9) ahead, through the planetary gears 8b of the right stage to the right solar gear 11b and to the driving axis (solar axis) 5b. As both sets of planetary gears 6a, 6b are of similar constitution, the ratio of transmission rate 1, according to table 2, case 4, will therefore be 1/3 for the right stage (planetary set 6b) . This indicates at the moment transfer a global transmission rate of 1 (left central wheel of planetary system 11a to the right central wheel of planetary system 11b).
    [0069] Therefore, when both drum sections 2a, 2b rotate with the same rotation - in the case of straight displacement - or at standstill, when, therefore, there is no rotation of the drum sections 2a, 2b, in a reciprocal direction converging torque - as desired - will be transferred in a 1: 1 ratio from one side to the other.
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    12/17
    Table 2: Individual cases in the planetary stages - Elementary planetary game
    Case Fixed in housing Driveinput Output Baud rate i 2 Fillet Gearcancel Solar -z1 / z3 = -1/2 3 Ring gear Solar Fillet (z1 + z3) / z1 = 3 4 Ring gear Fillet Solar Z1 / (z1 + z3) = 1/3
    [0070] When rotating a section of drum 2a in front of the other 2b, it must be ensured that the unbalanced masses 3 follow the rotation in the same measure.
    [0071] For the simplest explanation, let's assume the following: [0072] Drum section 2a on one side is stopped, hydraulic motor 7 is not turning. Expressed quickly, the annular gear 10a of the first stage (planetary set 6a), which is connected with the drum section 2a and the solar gear 11a of the first planetary set 6a, coupled on the drive shaft 5a with the hydraulic motor 7 - are stopped. Therefore, planetary game 6a is blocked on one side (in figure 9, on the left).
    [0073] Drum section 2b on the other side will now presumably be rotated around a random angle.
    [0074] The ring gear 10b of the planetary set 6b on the other side (in figure 9, on the right side), by dragging the ring gear and the bearing pin 16b is connected with the drum section 2b. This will now advance the rotation of the drum section 2b over the planetary gears 8b to the solar gear 11b on the right side. The common planetary conveyor 9, as already explained, is
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    13/17 blocked on the left side through the planetary game. Therefore, case 2 of the elementary planetary game shown in table 2 applies. The transmission rate ratio i will therefore be -0.5.
    [0075] As already explained, imbalance 3 will have to be rotated by the same angle as the drum component 2a, 2b, on which it is mounted, in order to achieve a synchronization of the oscillatory movement in the two drum sections 2a, 2b.
    [0076] Preferably, a two-stage planetary transmission may be used with a belt drive with reversed turning direction and reciprocal transmission rate as planetary transmission 6.
    [0077] The respective ring gears 10a, 10b of the planetary gear sets 6a, 6b, are connected to the swing proof with the drum sections 2a, 2b - with rolling pin 16a, 16b, coaxially positioned in the contiguous fittings 12a, 12b of the drum sections 2a, 2b - the rolling pins 16a, 16b forming, simultaneously, the assembly for the central drive pulleys 21 of the gear transmission 15a, 15b for driving the oscillation exciter 30a, 30b.
    [0078] Alternatively, a multi-stage planetary transmission may also be used, with a belt transmission rate different from the reciprocal transmission value and without reversing direction.
    [0079] In the third planetary stage that would produce a global transmission rate of 1 and a directional inversion, by driving the timing belt 32c with omega wrapping (see figure 10) and with a transmission rate ratio of 2 could be dispensed with. Omega wrapping means that the timing belt 15c wraps the timing belt pulleys 13 by more than 180 °, for example, by up to 200 ° to 210 °, especially 205 °, as shown in
    Petition 870190033194, of 5/5/2019, p. 15/33
    14/17 figure 10.
    [0080] For the individual gears of -0.5 in the planetary game and -2 in the toothed belt transmission, the global transmission rate located at 1 will also be here.
    [0081] Therefore, as required, the imbalance masses 3 will be regulated by the same angle as the rotated drum sections 2a, 2b. The moments produced by the oscillating imbalance masses are, therefore, in each drum section 2a, 2b in identical phase, regardless of the current position of the imbalance masses 3, in a reciprocal direction.
    [0082] In the displacement of the toothed belt, some basic innovations and an advantageous change were achieved.
    [0083] A belt drives two or more unbalance axes. If the WO 82/201903 drive were transferred to a split drum 20, then eight belt pulleys and four belts would be required.
    [0084] Contrary to the constructions hitherto undivided (WO 82/201903) that provide for each axis of imbalance a specific toothed belt drive, here they are driven with a single belt, preferably a toothed belt 32, the two unbalanced masses 3 drum section 2a, 2b. Accordingly, a toothed belt 32 and a drive belt wheel can be dispensed for each drum half.
    [0085] As already described above, when driving the toothed belt, a transmission rate ratio of -2 is achieved. This was achieved with the help of an omega wrapping of the toothed belt 32, according to figure 10. For this purpose, the large pulleys 13 have twice the number of teeth, compared to the small drive belt disk 21.
    [0086] By inversion in the small toothed disk 21, the
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    15/17 direction of rotation, which results in the required negative transmission ratio.
    [0087] For the necessary transmission rate of the toothed belt drive of -2, a large toothed disk 13 can preferably be used, in which a portion of the imbalance 3 can also be realized.
    [0088] Since the toothed belt disc 13 needs to be drilled in any way so that it can be screwed onto the imbalance plates 14, additional perforations 35 can be formed to produce a part of the necessary imbalance 3, on the opposite side of the imbalance weights in the form of an imbalance plate 14 (negative imbalance). Another advantage is the lower moment of inertia of the toothed belt disc 13, due to the reduction in weight that leads to higher gear more quickly when starting the drive.
    [0089] The remaining part of the imbalance 3 is provided by the side imbalance plates 14 and, for example, by the nine screws 18 as an imbalance weight (positive imbalance), whereby the imbalance plates 14 are preferably fixed on both sides on the toothed belt pulleys 13 (figure 10).
    [0090] The toothed belt disc 13, however necessary, therefore serves at the same time as imbalance 3. The imbalance plates 14, arranged laterally in relation to the toothed belt disc 13, are screwed directly into the respective disc toothed belt 13. The screws 18 form an additional unbalanced weight. The holes, that is, the perforations 35, on the side opposite the screws 18, form, in this case, a negative imbalance.
    [0091] Figure 10 shows the two imbalance plates 14, laterally mounted, in the assembled position with toothed belt 32 applied. The external contour of the imbalance plates 14 is in accordance with 870190033194, from 05/04/2019, p. 17/33
    16/17 shaped in such a way that the oblique flank 14a on the sides of the unbalance plates 14 is precisely aligned with the shorter section 32a of the toothed belt 32. This is a possibility to visually test the correct 180 ° offset in the unbalanced masses 3, based on the position of the timing belt 32.
    [0092] The angles of the oblique flanks 14a of the imbalance plates 14 correspond to the angle of the belt 32 on the omega wrapped side, in the position shown in figure 10.
    [0093] The imbalance plates 14 are preferably arranged on both sides of the toothed belt disk, in the same position. With the thickness of the imbalance plates 14, the mass of the imbalance 3 can be modified, just as it is possible to do this with the number of screws 18 or the size of the perforations 35.
    [0094] Until now, the necessary belt tension has been presented, that is, the toothed belt 32, or with the help of an additional tensioning roller, or only selected toothed belts 32 have been used and measured with an exact tolerance length.
    [0095] In the present construction, shown in figures 10 and 11, the belt tension will be regulated by a continuous change of the axial distance between the drive shaft 5a, 5b and the bearing pin axis 20a, 20b. This will be achieved by turning the rolling pin 20a, 20b, mounted eccentrically, on the unbalance flange 19 (figure 11).
    [0096] The rotation of the eccentric unbalance flange 19 with the bearing pin 20a, 20b so that the timing belt tensioning 15c occurs, by means of turning of an eccentric adjustment pin 17 (figure 10). This consists of two eccentric cylinders, one in relation to the other, and a hexagon part for the application of a wrench. [0097] The eccentric readjustment pin 17 is provided to rotate the
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    17/17 eccentric unbalance flange 19.
    [0098] Due to the eccentricity, when turning the adjustment pin 17, the unbalance flange 19 will be rotated in relation to the socket 12a, 12b.
    [0099] It is therefore possible to tension the belt 32 by means of a set of rolling pin which can be eccentrically positioned.
    [00100] The rolling pin 20a, 20b, mounted on a flywheel, serves to receive a bearing bearing 34 for the toothed belt disc 13. Bearing bearing 34 is centrally arranged with the radial belt force and centrifugal force imbalance masses 3.
    [00101] Figure 12 shows a perspective of the toothed belt disk 13, without the toothed belt 32.
    权利要求:
    Claims (16)
    [1]
    1. A compacting device comprising at least one displaceable drum (2) rotatable around a drum axis (1), with oscillation drivers (30a, 30b) coupled that generate oscillating torque around the drum axis (1), said oscillation drivers having unbalanced masses (3) which rotate out of phase 180 degrees in the same direction of rotation, and having a driving axis (5a, 5b) moving coaxially with the drum axis (1), for drive the oscillation drivers (30a, 30b), characterized by the fact that the drum (2) with the drive shaft (5a, 5b) is divided, at least once, and each drum section (2a, 2b) comprises at least two coupled oscillation drivers (30a, 30b), mounted on the drum (2) at a distance from the drum axis (1), where the oscillation drivers (30a) of a drum section (2a) are coupled to the oscillation drivers (30b) from another drum section (2b), in such a way that the scilation (30a, 30b) of all drum sections (2a, 2b) oscillate in sync also in the event of a rotation of the drum sections (2a, 2b) with respect to each other.
    [2]
    2. Compactor apparatus according to claim 1, characterized by the fact that the drive axes (5a, 5b) for the oscillation exciter (30a, 30b) of individual drum sections (2a, 2b) are mechanically coupled or , through a control means, adjusted to be in phase.
    [3]
    3. Compacting apparatus according to claim 1 or 2, characterized by the fact that the drive axes (5a, 5b) for the oscillation exciter (30a, 30b) of the contiguous drum sections (2a, 2b) are coupled mechanically through a transmission (6) and said transmission (6) it is operated to transfer the rotation and, respectively, the driving torque of an actuating shaftPetition 870190033194, from 05/04/2019, p. 21/33
    2/5 namento (5a), in the right phase, for the subsequent drive shaft (5b) of the drum section (2a).
    [4]
    4. Compacting apparatus according to claim 3, characterized in that the transmission for coupling the drive shaft sections (5a, 5b) is a planetary gear transmission (6) or a gear transmission or a bevel gear transmission.
    [5]
    Compactor apparatus according to any one of claims 1 to 4, characterized in that the drum (2) is divided into two sections and each drum section (2a, 2b) comprises a displacement drive (7a, 7b ) itself, the drum sections (2a, 2b) being connected to each other in a way to allow them to be rotated coaxially with respect to each other.
    [6]
    6. Compacting apparatus according to claim 4 or 5, characterized by the fact that the planetary gear transmission (6) comprises at least two sets of planetary gears (6a, 6b).
    [7]
    7. Compacting apparatus according to claim 6, characterized by the fact that the planetary transmission (6) comprises two sets of planetary gears (6a, 6b) having a common planetary conveyor (9), in which annular gears (10a, 10b) of the planetary gear sets (6a, 6b) are respectively connected to a drum section (2a, 2b) for common rotation with it, and the respective drive axes (5a, 5b) are connected with the respective solar gears (11a, 11b) of the planetary gear sets (6a, 6b).
    [8]
    Compactor apparatus according to any one of claims 1 to 7, characterized by the fact that the drive shaft (5a, 5b) of each drum section (2a, 2b) is operated to drive, through a transmission, at least two drivers
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    3/5 oscillations (30a, 30b).
    [9]
    9. Compactor apparatus according to claim 8, characterized by the fact that the drive for driving the unbalanced masses (3) is a belt drive or a chain drive.
    [10]
    Compactor apparatus according to any one of claims 3 to 9, characterized in that the drive for driving the oscillation exciter (30a, 30b) is a toothed belt transmission (15a, 15b) comprising a toothed belt (32) to drive toothed belt pulleys (13) coupled with unbalanced masses (3).
    [11]
    11. Compacting apparatus according to claim 9 or 10, characterized by the fact that the drive is a belt transmission with a belt driving assembly that allows an inversion of the turning direction, and a reciprocal transmission rate in the direction the planetary gear transmission (6).
    [12]
    12. Compacting apparatus according to any one of claims 9 to 11, characterized by the fact that a multi-stage planetary gear transmission (6) and a belt transmission without reversing the turning direction and without reciprocal transmission rate towards the planetary transmission (6) are provided.
    [13]
    13. Compacting apparatus according to any one of claims 10 to 12, characterized in that the oscillation drivers (30a, 30b) comprise imbalance masses (3) and these imbalance masses (3) comprise imbalance plates ( 14) which are laterally attached to toothed belt pulleys (13) of the toothed belt transmission (15a, 15b), and have a flank (14a) that extends radially outward, which at a given starting position is aligned with the belt denPetição 870190033194, from 05/05/2019, p. 23/33
    4/5 timing (32) of the timing belt transmission (15a, 15b), if the offset of the rotation angle between the two timing belt pulleys (13), driven by the timing belt transmission (15a, 15b) corresponds to the value wanted.
    [14]
    Compactor apparatus according to any of claims 9 to 13, characterized by the fact that a belt tensioning device is operable to tension the belt (32) to drive the unbalanced masses (3) and, respectively, the pulleys (13) with the aid of an eccentrically displaceable rolling pin (20a, 20b).
    [15]
    Compactor apparatus according to any one of claims 9 to 14, characterized by the fact that the belt transmission (15a, 15b) comprises pulleys (13), which are coaxial and concentric with the axis of rotation of the masses of imbalance (3) and whose weight distribution extends with rotational dissymmetry with respect to the axis of rotation of the imbalance masses (3).
    [16]
    16. Process for compacting soils by means of a drum (2) of a compaction apparatus, said drum (2) being rotatable around a drum axis (1), in which with the aid of oscillation exciters (30a , 30b) coupled comprising imbalance masses (3) rotating at a distance from the drum axis (1), a turning moment that oscillates around the drum axis (1) is generated, the imbalance masses (3) being actuated to rotate out of phase 180 degrees in the same direction of rotation, characterized by the fact that the use of a drum (2) divided with at least two drum halves (2a, 2b), in which unbalanced masses (3) of the oscillation drivers (30a, 30b) in each section (2a, 2b) of the drum (2) are rotated by the same angle with respect to the phase position as in the rotation of the drum halves (2a, 2b) with respect to each other, so that the synchronization of the oscillatory movement in all sections
    Petition 870190033194, of 5/5/2019, p. 24/33
    5/5 drum (2a, 2b) is obtained even if the drum sections (2a, 2b) have been rotated with respect to each other.
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    同族专利:
    公开号 | 公开日
    JP2013512358A|2013-04-11|
    DE202010018525U1|2017-09-07|
    CN102985616B|2015-08-26|
    EP2504490B1|2017-01-11|
    CA2782094C|2014-11-25|
    US9039324B2|2015-05-26|
    US20120301221A1|2012-11-29|
    EP2504490A2|2012-10-03|
    AU2010323083A1|2012-05-24|
    JP5572819B2|2014-08-20|
    WO2011064367A2|2011-06-03|
    WO2011064367A3|2012-06-28|
    DE102009055950A1|2011-06-01|
    BR112012012812A2|2016-08-16|
    DE202010005962U1|2010-09-30|
    CN102985616A|2013-03-20|
    CA2782094A1|2011-06-03|
    AU2010323083B2|2014-05-01|
    RU2012126678A|2014-01-20|
    RU2513604C2|2014-04-20|
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    法律状态:
    2019-01-08| B06F| Objections, documents and/or translations needed after an examination request according art. 34 industrial property law|
    2019-02-05| B06T| Formal requirements before examination|
    2019-05-28| B09A| Decision: intention to grant|
    2019-07-02| B16A| Patent or certificate of addition of invention granted|Free format text: PRAZO DE VALIDADE: 20 (VINTE) ANOS CONTADOS A PARTIR DE 29/11/2010, OBSERVADAS AS CONDICOES LEGAIS. (CO) 20 (VINTE) ANOS CONTADOS A PARTIR DE 29/11/2010, OBSERVADAS AS CONDICOES LEGAIS |
    优先权:
    申请号 | 申请日 | 专利标题
    DE102009055950.7|2009-11-27|
    DE200910055950|DE102009055950A1|2009-11-27|2009-11-27|Compactor for compacting grounds, has movable drum rotatable around drum axle, where drum part of drum comprises vibration generator that is supported at distance from drum axle in drum|
    DE201020005962|DE202010005962U1|2009-11-27|2010-04-21|compactor|
    DE202010005962.3|2010-04-21|
    PCT/EP2010/068418|WO2011064367A2|2009-11-27|2010-11-29|Compaction device and method for compacting ground|
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