EP2504490B1 - Verdichtungsgerät, sowie verfahren zum verdichten von böden - Google Patents

Verdichtungsgerät, sowie verfahren zum verdichten von böden Download PDF

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Publication number
EP2504490B1
EP2504490B1 EP10781912.0A EP10781912A EP2504490B1 EP 2504490 B1 EP2504490 B1 EP 2504490B1 EP 10781912 A EP10781912 A EP 10781912A EP 2504490 B1 EP2504490 B1 EP 2504490B1
Authority
EP
European Patent Office
Prior art keywords
drum
belt
transmission
compaction device
drive
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP10781912.0A
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German (de)
English (en)
French (fr)
Other versions
EP2504490A2 (de
Inventor
Hans-Peter Ackermann
Peter Janner
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hamm AG
Original Assignee
Hamm AG
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Filing date
Publication date
Application filed by Hamm AG filed Critical Hamm AG
Publication of EP2504490A2 publication Critical patent/EP2504490A2/de
Application granted granted Critical
Publication of EP2504490B1 publication Critical patent/EP2504490B1/de
Active legal-status Critical Current
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Classifications

    • E—FIXED CONSTRUCTIONS
    • E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
    • E01C—CONSTRUCTION OF, OR SURFACES FOR, ROADS, SPORTS GROUNDS, OR THE LIKE; MACHINES OR AUXILIARY TOOLS FOR CONSTRUCTION OR REPAIR
    • E01C19/00—Machines, tools or auxiliary devices for preparing or distributing paving materials, for working the placed materials, or for forming, consolidating, or finishing the paving
    • E01C19/22—Machines, tools or auxiliary devices for preparing or distributing paving materials, for working the placed materials, or for forming, consolidating, or finishing the paving for consolidating or finishing laid-down unset materials
    • E01C19/23—Rollers therefor; Such rollers usable also for compacting soil
    • E01C19/28—Vibrated rollers or rollers subjected to impacts, e.g. hammering blows
    • E01C19/286—Vibration or impact-imparting means; Arrangement, mounting or adjustment thereof; Construction or mounting of the rolling elements, transmission or drive thereto, e.g. to vibrator mounted inside the roll
    • E—FIXED CONSTRUCTIONS
    • E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
    • E01C—CONSTRUCTION OF, OR SURFACES FOR, ROADS, SPORTS GROUNDS, OR THE LIKE; MACHINES OR AUXILIARY TOOLS FOR CONSTRUCTION OR REPAIR
    • E01C19/00—Machines, tools or auxiliary devices for preparing or distributing paving materials, for working the placed materials, or for forming, consolidating, or finishing the paving
    • E01C19/22—Machines, tools or auxiliary devices for preparing or distributing paving materials, for working the placed materials, or for forming, consolidating, or finishing the paving for consolidating or finishing laid-down unset materials
    • E01C19/23—Rollers therefor; Such rollers usable also for compacting soil
    • E01C19/28—Vibrated rollers or rollers subjected to impacts, e.g. hammering blows
    • E01C19/282—Vibrated rollers or rollers subjected to impacts, e.g. hammering blows self-propelled, e.g. with an own traction-unit
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02D—FOUNDATIONS; EXCAVATIONS; EMBANKMENTS; UNDERGROUND OR UNDERWATER STRUCTURES
    • E02D3/00—Improving or preserving soil or rock, e.g. preserving permafrost soil
    • E02D3/02—Improving by compacting
    • E02D3/046—Improving by compacting by tamping or vibrating, e.g. with auxiliary watering of the soil
    • E02D3/074—Vibrating apparatus operating with systems involving rotary unbalanced masses

Definitions

  • the invention relates to a compacting device for compacting trays according to the preamble of claim 1, as well as to a method for compaction of trays according to claim 16.
  • Compactors are known, e.g. in the form of a road roller.
  • the road rollers distinguish between a dynamic and a static mode of compression. In the dynamic mode of operation, the compaction takes place by movement, and in the static mode of operation, the compaction is carried out by the weight of the road roller.
  • a road roller may be a self-propelled vehicle and has at least one bandage.
  • Oszillationsbandagen are so far, in contrast to vibration bandages not made in split design, since the technical realization is much more difficult.
  • the synchronization of the centrifugal forces generating imbalances must be guaranteed at all times, especially with a relative rotation of the two bandages each other.
  • the bandage thus undergoes a small twist to the left and right with each revolution of the imbalance shaft and begins to oscillate about the axis of rotation M of the bandage.
  • Fig.2 In the present description, the sectional view of a split vibration bandage.
  • the two bandage parts 2a, 2b are screwed together via a rotary joint.
  • the imbalances 3 for both bandage parts 2a, 2b are located here on the central imbalance shaft 31, which is driven by a hydraulic motor 7.
  • cornering and thus rotation of the bandage parts 2a, 2b to each other nothing changes at the vibration in the two bandage parts 2a, 2b, ie both bandage parts 2a, 2b vibrate synchronously.
  • Timing belt guide For a better representation of the timing belt guide from the Fig.4 to Fig.7 is the described timing belt guide in Fig. 3 spatially represented.
  • Fig.4 and Fig.5 show the two bandage parts 2a, 2b before their rotation.
  • Fig.6 and Fig.7 are the bandage parts 2a, 2b shown by a rotation of the bandage part 2b by 90 °.
  • the invention is therefore based on the object of specifying a vibrating device or a method for compacting trays in which, in the case of divided bandages with oscillatory oscillation, no excessive shearing forces act on the asphalt surface on the joint between the band conveyor parts.
  • the bandage is divided at least once with the drive shaft and that each bandage part has at least two coupled vibration exciters mounted in the bandage at a distance from the bandage axis, wherein the vibration exciters of one bandage part are coupled to the vibration exciters of another bandage part, that the vibration exciters all hinge parts swing synchronously relative to each other even with a rotation of the bandage parts.
  • the respective vibration exciter are stored in the respective band parts.
  • the drive shafts for the vibration exciters of the individual bandage parts are mechanically coupled or adjusted in phase by a control.
  • the control can be done electrically, electronically or hydraulically / pneumatically.
  • the drive shafts for the vibration exciter of the adjacent bandage parts can be mechanically coupled via a transmission, wherein the transmission
  • Rotation or the drive torque of a drive shaft transmits in the correct phase to the subsequent drive shaft.
  • the transmission for coupling the drive shaft parts may be a planetary gear or a spur gear or a bevel gear.
  • the bandage is preferably divided into two parts and each bandage part has its own travel drive, wherein the two bandage parts are coaxially rotatable relative to each other rotatably connected to each other.
  • a preferably usable planetary gear may consist of at least two planetary gear sets.
  • the planetary gear of two planetary gear sets may have a common planet carrier, wherein the ring gears of the planetary gear sets are each rotatably connected to a bandage part and the respective drive shafts with the respective sun gears of the planetary gear sets.
  • the gear to drive the imbalances may be a belt transmission or chain transmission.
  • the transmission for driving the vibration exciters is preferably a toothed belt drive with omega wrap, which drives with unbalanced coupled toothed pulleys.
  • the transmission is preferably a belt transmission with a belt guide, which allows a reversal of direction and a reciprocal ratio to the planetary gear.
  • the translation of the belt drive and the translation of the planetary gear should give a total ratio of 1: 1.
  • the vibration exciters have imbalance weights and the imbalance weights are preferably made of unevenness plates which are preferably laterally attached to the pulleys of the belt transmission and have a radially outwardly extending flank which is aligned in a certain initial position with the belt of the belt drive when the rotational angle offset between the both driven by the belt transmission unbalanced shafts or pulleys corresponds to the target value.
  • the belt transmission is a toothed belt transmission.
  • a belt tensioning device can tension the belt for driving the imbalance or the pulley by means of an eccentrically displaceable bearing pin for the pulley.
  • the belt tensioner may include an eccentric adjustment bolt for rotating and locking the eccentric journal.
  • the belt drive can have coaxial and concentric pulleys with the axis of rotation of the imbalances whose weight distribution is not rotationally symmetrical with respect to the axis of rotation of the imbalances.
  • holes or holes in the material of the toothed belt can cause a non-rotationally symmetric weight distribution and form a negative imbalance mass.
  • Laterally arranged unbalance plates may be attached to the pulleys and / or asymmetrically arranged screws, which is an imbalance weight form, the screws can also serve to fasten the unbalance plates.
  • the bearings are preferably arranged centrally to the radial belt force and centrifugal force of the imbalances.
  • a drum of a compacting device For compacting soils with a drum of a compacting device is provided to generate with the aid of at least one vibrator with rotating unbalanced weights compression vibrations of the bandage, by using a split bandage with two bandage halves, wherein the imbalance weights of the vibration exciters in each part of the bandage to the same angle! be rotated with respect to the phase position as the relative rotation of the Bandagenphasetften each other to achieve a synchronization of the oscillatory motion in the two halves of the bandage, even if the bandage halves are twisted to each other.
  • a mechanical connection should enable the synchronization of the exciter forces in both halves of the bandage. This function is performed by a multi-stage planetary gear.
  • a transmission has the task to transmit the moment of the hydraulic motor for driving the imbalances from the left to the right bandage in the correct phase.
  • Fig. 1 shows as an example of a vibration device, a road roller, namely in particular a tandem vibratory roller with a front and a rear drum 2.
  • FIGS. 2 to 7 explain, as already mentioned in the introduction, the prior art.
  • FIG 8 a split oscillatory bandage 2 is shown. Shown are the two bandage parts 2a, 2b with built-in gear, for example, the in Fig. 9 illustrated planetary gear 6 to solve the phase problem when cornering, imbalances (unbalance weights) 3 of the vibration exciter 30a, 30b and the attachments.
  • Travel drives 7a, 7b drive the respective bandage parts 2a, 2b.
  • the planetary gear 6 has two planetary gear sets 6a, 6b.
  • Each bandage part 2a, 2b has an inside arranged frontal Ronde 12a, 12b, in the example, bearing journals 20a, 20b for receiving rotating imbalances 3 of the vibration exciter 30a, 30b are stored.
  • the ring gear 10a on the left side of the first planetary gear set 6a is fixedly connected to the bandage part 2a on the left side of the bandage 2 by the journal 16a and the round plate 12a.
  • the ring gear 10b on the right side of the bandage is coupled via the bearing pin 16b and the blank 12b to the bandage part 2b on the right side of the bandage 2.
  • Table 1 Number of teeth of the gears wheel 1 2 3 sun planet ring gear number of teeth 40 20 80
  • the bandage part 2b on the other side is now mentally twisted by any angle.
  • the ring gear 10b of the planetary gear set 6b on the other (in Fig. 9 right) side is connected via the ring gear driver and the bearing pin 16b with the bandage part 2b. This now gives the rotation of the bandage part 2b on the planet gears 8b on the sun gear 11b on the right side.
  • the common planet carrier 9 is, as already explained, blocked by the planetary gear set on the left side. Therefore, case 2 of the elementary planetary gear set from table 2 applies.
  • the gear ratio i is therefore -0.5.
  • the imbalance 3 must be rotated by the same angle as the bandage part 2a, 2b, in which it is mounted, in order to achieve a synchronization of the oscillatory movement in both band parts 2a, 2b.
  • a two-stage planetary gear with a belt drive with reverse rotation and reciprocal translation can be used as a planetary gear 6.
  • the respective ring gears 10a, 10b of the planetary gear sets 6a, 6b are rotatably connected with bearing pins 16a, 16b, which are coaxially arranged in the adjacent rounds 12a, 12b of the bandage parts 2a, 2b, with the band parts 2a, 2b, wherein the bearing pins 16a, 16b at the same time the storage of the central drive pulleys 21 of the toothed belt drive 15a, 15b to drive the vibration exciter 30a, 30b form.
  • a multi-stage planetary gear with belt ratio not equal to the reciprocal of the transmission and without reversing direction can be used.
  • the omega wrap means; that the toothed belt 15 c, the toothed belt pulleys 13 by more than 180 °, for example by about 200 ° to 210 °, in particular 205 °, as in Fig. 10 shown, encloses.
  • the imbalances 3 are thus adjusted as required by the same angle as the twisted bandage parts 2a, 2b.
  • the moments generated by the Oszillationsunwuchten are thus in each bandage part 2a, 2b in phase, regardless of the current position of the imbalances 3 to each other.
  • a belt drives two or more unbalance shafts. Would you drive out WO 82/201903 transferred to a split drum 20, eight pulleys and four belts would be needed.
  • a gear ratio of -2 is realized in the timing belt guide. This was done by means of an omega wrap of the toothed belt 32 according to Fig. 10 reached. For this, the large toothed pulleys 13 have twice the number of teeth compared to the small drive pulley 21.
  • a large toothed disc 13 can be used, in which also a part of the imbalance 3 can be realized.
  • the already required toothed belt pulley 13 therefore also serves as imbalance 3.
  • the side of the pulley 13 arranged unbalance plates 14 are screwed directly to the respective toothed belt pulley 13.
  • the screws 18 form an additional imbalance weight.
  • the holes or holes 35 on the opposite side of the screws 18 thereby form a negative imbalance.
  • FIG 10 the two laterally mounted unbalance plates 14 are shown in the assembled position with the toothed belt 32 on.
  • the outer contour of the imbalance plates 14 is designed such that the inclined edge 14a on the sides of the imbalance plates 14 with the short strand 32a of the toothed belt 32 is exactly aligned. This is a way to visually check the correct 180 ° offset of the unbalance 3 based on the position of the belt 32.
  • angles of the sloping flanks 14a of the unbalance plates 14 correspond to the angle of the belt 32 at the omega-wrapped side in FIG Fig. 10 shown position.
  • the unbalance plates 14 are preferably arranged on both sides of the toothed belt pulley in the same position. With the thickness of the imbalance plates 14, the mass of the imbalance 3 can be changed, as well as with the number of screws 18 or the size of the holes 35th
  • the required belt tension of the toothed belt 32 has been made either by means of an additional idler pulley, or only selected, measured toothed belts 32 having a precisely tolerated length have been used.
  • the belt tension is adjusted by continuously changing the axial distance between the drive shaft 5a, 5b and the axis of the trunnion 20a, 20b. This is done by turning the eccentrically mounted bearing pin 20a, 20b on the unbalance flange 19 (FIG. Figure 11 ) reached.
  • the rotation of the eccentric unbalance flange 19 with the bearing pin 20a, 20b for tensioning the toothed belt 15c is done by turning an eccentric adjusting pin 17 (FIG. Fig. 10 ).
  • This consists of two mutually eccentric cylinders and a hexagon for attaching a key.
  • the eccentric adjusting bolt 17 is provided for rotating the eccentric unbalance flange 19.
  • the unbalance flange 19 is rotated relative to the blank 12a, 12b when the adjusting bolt 17 is rotated.
  • the cantilever bearing journal 20a, 20b serves to receive a roller bearing 34 for the toothed belt pulley 13.
  • the roller bearing 34 is arranged centric to the radial belt force and centrifugal force of the imbalances 3.
  • Fig. 12 shows a perspective view of the toothed belt pulley 13 without toothed belt 32nd

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  • Engineering & Computer Science (AREA)
  • Structural Engineering (AREA)
  • Civil Engineering (AREA)
  • Architecture (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Paleontology (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Mining & Mineral Resources (AREA)
  • Soil Sciences (AREA)
  • Environmental & Geological Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Agronomy & Crop Science (AREA)
  • Road Paving Machines (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)
  • Investigation Of Foundation Soil And Reinforcement Of Foundation Soil By Compacting Or Drainage (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
EP10781912.0A 2009-11-27 2010-11-29 Verdichtungsgerät, sowie verfahren zum verdichten von böden Active EP2504490B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE200910055950 DE102009055950A1 (de) 2009-11-27 2009-11-27 Verdichtungsgerät, sowie Verfahren zum Verdichten von Böden
DE202010005962U DE202010005962U1 (de) 2009-11-27 2010-04-21 Verdichtungsgerät
PCT/EP2010/068418 WO2011064367A2 (de) 2009-11-27 2010-11-29 Verdichtungsgerät, sowie verfahren zum verdichten von böden

Publications (2)

Publication Number Publication Date
EP2504490A2 EP2504490A2 (de) 2012-10-03
EP2504490B1 true EP2504490B1 (de) 2017-01-11

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EP10781912.0A Active EP2504490B1 (de) 2009-11-27 2010-11-29 Verdichtungsgerät, sowie verfahren zum verdichten von böden

Country Status (10)

Country Link
US (1) US9039324B2 (ja)
EP (1) EP2504490B1 (ja)
JP (1) JP5572819B2 (ja)
CN (1) CN102985616B (ja)
AU (1) AU2010323083B2 (ja)
BR (1) BR112012012812B1 (ja)
CA (1) CA2782094C (ja)
DE (3) DE102009055950A1 (ja)
RU (1) RU2513604C2 (ja)
WO (1) WO2011064367A2 (ja)

Cited By (2)

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DE102017122370A1 (de) * 2017-09-27 2019-03-28 Hamm Ag Oszillationsmodul
DE102017122371A1 (de) * 2017-09-27 2019-03-28 Hamm Ag Verdichterwalze

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DE102012201443A1 (de) 2012-02-01 2013-08-01 Hamm Ag Verdichterwalze für einen Bodenverdichter
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EP3445913B1 (en) * 2016-04-21 2019-10-16 Volvo Construction Equipment AB Compacting drum comprising an eccentric assembly for oscillating the compacting drum of a compacting machine
DE102016109888A1 (de) * 2016-05-30 2017-11-30 Hamm Ag Bodenverdichter und Verfahren zum Betreiben eines Bodenverdichters
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CN110770399A (zh) * 2017-06-19 2020-02-07 沃尔沃建筑设备公司 用于压实机的振动偏心组件
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Publication number Priority date Publication date Assignee Title
DE102017122370A1 (de) * 2017-09-27 2019-03-28 Hamm Ag Oszillationsmodul
DE102017122371A1 (de) * 2017-09-27 2019-03-28 Hamm Ag Verdichterwalze
WO2019063540A1 (de) 2017-09-27 2019-04-04 Hamm Ag Oszillationsmodul
EP4234813A2 (de) 2017-09-27 2023-08-30 Hamm AG Oszillationsmodul
EP4234813A3 (de) * 2017-09-27 2023-10-25 Hamm AG Oszillationsmodul

Also Published As

Publication number Publication date
BR112012012812B1 (pt) 2019-07-02
US9039324B2 (en) 2015-05-26
CN102985616B (zh) 2015-08-26
DE202010018525U1 (de) 2017-09-07
CN102985616A (zh) 2013-03-20
CA2782094A1 (en) 2011-06-03
WO2011064367A3 (de) 2012-06-28
RU2012126678A (ru) 2014-01-20
BR112012012812A2 (pt) 2016-08-16
AU2010323083B2 (en) 2014-05-01
CA2782094C (en) 2014-11-25
EP2504490A2 (de) 2012-10-03
US20120301221A1 (en) 2012-11-29
WO2011064367A2 (de) 2011-06-03
DE202010005962U1 (de) 2010-09-30
DE102009055950A1 (de) 2011-06-01
RU2513604C2 (ru) 2014-04-20
JP2013512358A (ja) 2013-04-11
JP5572819B2 (ja) 2014-08-20
AU2010323083A1 (en) 2012-05-24

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