EP2531305A2 - Système destiné à produire des vibrations - Google Patents

Système destiné à produire des vibrations

Info

Publication number
EP2531305A2
EP2531305A2 EP10801138A EP10801138A EP2531305A2 EP 2531305 A2 EP2531305 A2 EP 2531305A2 EP 10801138 A EP10801138 A EP 10801138A EP 10801138 A EP10801138 A EP 10801138A EP 2531305 A2 EP2531305 A2 EP 2531305A2
Authority
EP
European Patent Office
Prior art keywords
hydraulic motor
pressure
pressure accumulator
hydraulic
vibration
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.)
Granted
Application number
EP10801138A
Other languages
German (de)
English (en)
Other versions
EP2531305B1 (fr
Inventor
Nikolaus Renz
Tobias Simmendinger
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2531305A2 publication Critical patent/EP2531305A2/fr
Application granted granted Critical
Publication of EP2531305B1 publication Critical patent/EP2531305B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B06—GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS IN GENERAL
    • B06B—METHODS OR APPARATUS FOR GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS OF INFRASONIC, SONIC, OR ULTRASONIC FREQUENCY, e.g. FOR PERFORMING MECHANICAL WORK IN GENERAL
    • B06B1/00—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency
    • B06B1/18—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency wherein the vibrator is actuated by pressure fluid
    • B06B1/186—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency wherein the vibrator is actuated by pressure fluid operating with rotary unbalanced masses
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18056—Rotary to or from reciprocating or oscillating
    • Y10T74/18344—Unbalanced weights

Definitions

  • the present invention relates to a vibration drive of a vibratory roller according to the preamble of patent claim 1.
  • a vibratory roller is generally a construction machine and belongs to the group of compactors. With their help, cohesive and non-cohesive soils, bearing and antifreeze layers as well as asphalt can be compacted over a large area.
  • the vibrating roller generally has two roller bodies with preferably smooth-coated bandages, in the interior of which a vibration unit for improving the compression result is installed.
  • the vibratory roller has the ability to initiate additional energy in addition to its own weight in the underground.
  • a vibratory roller of this type is known.
  • This has a roller frame to which a propulsion unit is attached and at least one bandage, in the interior of which a vibrating unbalance vibration exciter is arranged.
  • Imbalance vibration exciter consists of an imbalance shaft, which is set in rotation by a further drive motor separate from the traction drive motor. Both the traction drive motor and the further vibrator drive motor are each designed as hydraulic motors, via a hydraulic system with one of a
  • Combustion engine driven hydraulic pump are fluidly connected.
  • Hydraulic pump to be supplied with pressure medium.
  • Hydraulic circuit design known. Such hydrostatic drives have at least a hydraulic pump, which is fluidly connected via working lines with a hydraulic motor. The downstream connection of the hydraulic motor can optionally be connected to a high-pressure accumulator.
  • the hydraulic pump delivers pressure to the hydraulic motor, which accordingly outputs torque to an output shaft to drive an engine and / or a vehicle.
  • the hydraulic motor In the case of a shift operation, d. h., In the case where a torque from the output shaft is applied to the hydraulic motor, the hydraulic motor now acts as a pump and promotes pressure medium in the direction of its downstream port.
  • the high pressure accumulator is connected to the downstream port of the hydraulic motor
  • the high-pressure accumulator is connected to the upstream connection of the hydraulic pump
  • Vibratory roller comprising an imbalance vibration exciter in at least one preferably driven by the propulsion engine bandage of
  • Vibratory roller is rotatably inserted or used.
  • the unbalance vibration exciter is mechanically coupled to a hydraulic motor (preferably via an output shaft) or coupled, which in turn can be supplied by a hydraulic pump with a pressure medium via working lines.
  • a hydraulic motor preferably via an output shaft
  • Vibration drive provided at least one high-pressure accumulator, which is for receiving from the hydraulic motor in a push operation, d. h., In a discontinued operation of the unbalance vibration generator promoted pressure medium is used.
  • the invention for energy recovery sees not the propulsion unit, but the vibration drive than that for the
  • An advantageous embodiment of the invention provides that the hydraulic pump and the hydraulic motor are arranged in a closed circuit, in which in the overrun mode (discontinuation of the unbalance vibration generator) of the
  • the upstream connection of the hydraulic motor with the high-pressure accumulator can be fluidly connected.
  • another advantageous embodiment of the invention provides that the hydraulic pump and the hydraulic motor are arranged in an open circuit, in which the downstream connection of the hydraulic motor with a tank or with the high-pressure accumulator is fluid-connectable.
  • a valve arrangement is provided, via which the high-pressure accumulator optionally with the downstream connection of the hydraulic motor or with the upstream connection of the hydraulic motor
  • a low-pressure accumulator provided in the shift operation of
  • Hydraulic motor with the upstream connection is connectable and in the
  • FIG. 1 shows a hydrostatic vibration drive
  • Vibratory roller with energy recovery according to a first preferred
  • FIG. 2 shows a hydrostatic vibration drive of a vibratory roller according to the first preferred embodiment in a second open one
  • FIG. 3 shows a hydrostatic vibration drive of a vibratory roller according to a second preferred exemplary embodiment of the invention in a first closed hydraulic circuit variant
  • Figure 4 shows a hydrostatic vibration drive of a vibrating roller according to the second preferred embodiment in a second closed
  • Figure 5 is a schematic representation of a vibrating roller.
  • the vibration drive has a hydraulic pump 1, whose
  • Intake port with a pressure medium tank 2 is fluidly connected and whose Pressure port via a working line 4 with an upstream port of a hydraulic motor 6 is fluidly connected.
  • In the working line 4 is a
  • adjustable pressure relief valve 12 is interposed. This is to
  • the downstream port of the hydraulic motor 6 is connected via an electromagnetically actuated two-way two-position switching valve 14 to the pressure medium tank 2.
  • an energy recovery line 16 which leads to a biased (biasing pressure, for example, 150 bar) high-pressure accumulator 18.
  • an energy recovery valve assembly 20 is interposed. This consists according to the present embodiment of an electromagnetically actuated 3-way 3-position switching valve 22, which blocks all connections in a first designed as a spring-centered switching position. In a second switching position, this switching valve 22 connects the downstream port of the hydraulic motor 6 to the high-pressure accumulator 18. In a third switching position, the switching valve 22 connects the high-pressure accumulator 18 with an energy return line 24, which at the
  • upstream connection of the hydraulic motor 6 is connected downstream of the check valve 8.
  • this return line 24 is also a spring-biased check valve 26 interposed, which is preferably 2 bar
  • Opening pressure is set.
  • the pressure relief valve 12 is set to a higher pressure than usual, and serves only as a safety valve. In this case, pressure medium from the hydraulic pump 1 via the spring-biased
  • Pressure limiting valve 12 is set to a very small value, so that the pressure upstream of the hydraulic motor 6, for example, drops to 6 bar.
  • the imbalance vibration exciter 34 oscillates or rotates due to its moment of inertia. In this case, a torque on the output shaft 32 on the
  • Transfer hydraulic motor 6 which now assumes the function of a pump in this case. D. h., The hydraulic motor 6 now promotes pressure fluid from the working line 4 in the direction of pressure medium tank 2.
  • An electronic control not shown, which also gives the signal of adjustment of the pressure relief valve 12, switches at this moment the 2-position 2-way Switching valve 14 in the closed position and the 3-way 3-position switching valve 22 in the second switching position, in which the downstream port of the hydraulic motor 6 is connected to the high-pressure accumulator 18.
  • the high-pressure accumulator 18 is charged, ie, the pressure medium conveyed by the hydraulic motor 6 (now in the function of a pump) is fed into the high-pressure accumulator 18.
  • Decisive here is that the output shaft 32 of the hydraulic motor 6 is connected to the unbalance vibration generator 34 of the vibratory roller, ie, the tracking energy of the unbalance Vibration generator 34 is used to recover energy in the form of hydraulic pressure in the high-pressure accumulator 18.
  • the 3/3-way switching valve are brought by switching off the one solenoid back to its first switching position and the proportional pressure relief valve 12 is set to a high pressure value. Then the hydraulic motor is supplied by the hydraulic pump with pressure medium.
  • valves 22 and 12 also in dependence on the speed or the
  • FIG. 2 shows a second variant of a vibration drive
  • Vibration roller according to an open hydraulic circuit design, wherein only the circuit-technical differences compared to the first variant described above will be discussed below mainly.
  • Proportional pressure relief valve 12 arranged in a leading to a pressure medium tank 2 branch line 10, which branches off from the working line 4 between the hydraulic pump 1 and the hydraulic motor 6.
  • This proportional Pressure relief valve 12 is adjustable in a range of 8 to 250 bar.
  • the hydraulic motor 6 is optionally set to shut down. That is, when the vibration drive is to be turned off, the proportional pressure relief valve 12 is set at 8 bar, so that the hydraulic pump 6 conveys substantially directly into the pressure medium tank 2. At this moment, the hydraulic motor 6 is turned off as a torque output means.
  • An alternative embodiment for this purpose shows the second variant of the open hydraulic circuit design according to the figure 2. Accordingly, the aforementioned proportional pressure relief valve 12 by a first fixed set
  • Pressure relief valve 38 replaced, which is preferably set to 250 bar, a second fixed pressure relief valve 48 and a directional control valve 46 replaced.
  • a bypass line 40 is provided, which bypasses the hydraulic motor 6 as well as the spring-biased check valve 8 connected upstream of the hydraulic motor 6, ie. h., The output terminal of the hydraulic pump 1 with the output terminal of
  • Hydraulic motor 6 connects, and in which a 2-position 2-way switching valve 42 is joined between.
  • This switching valve 42 is by means of a spring in his
  • the hydraulic pump 1 conveys a pressure medium via the spring-biased check valve 8 to the upstream connection of the hydraulic motor 6, so that it applies a torque an output shaft 32 for driving an unbalance vibration generator 34 shown in FIG.
  • the pressure-released pressure medium is then on the biased in the open position 2-position 2-way switching valve in the
  • Pressure tank 2 discharged.
  • the two valves 42 and 46 are in their blocking position.
  • the 2-way 2-position switching valve 46 is switched from its closed position to the open position.
  • the hydraulic pump 1 promotes pressure medium via the branched off from the bypass line 40 branch line 44 into the pressure medium tank 2.
  • Output shaft 32 applies a torque to the hydraulic motor 6, takes place in
  • the acceleration is also carried out according to the embodiment of Figure 1. It is the directional control valve 22 brought into the switching position, in which the hydraulic accumulator is connected via the check valve 26 to the upstream port of the hydraulic motor 6. After a certain period of time or speed-dependent or depending on the degree of speed change, the directional control valve 22 are brought into its central position and the directional control valve 46 in its blocking position. Because of the blocking position of the directional valve 46, the pressure relief valve 48 is ineffective and it can build up in the working line 4 a pressure.
  • the directional control valve 42 is only in its open switching position when the vibration drive is to be completely switched off, but the hydraulic pump 1 is still driven by a primary unit. Then the hydraulic pump delivers with a very low circulation pressure through the valves 42 and 14 to the tank, so that only very small energy losses.
  • the drive of the hydraulic motor 6 in the vibration drive according to the figure 1 as well as the figure 2 must be designed so that the hydraulic pump 1 when starting the hydraulic motor 6 the Mass moment of inertia of the unbalance vibration generator 34 overcomes.
  • an excessive power is demanded by the hydraulic pump drive.
  • the drive for the hydraulic pump 1 is designed so that the
  • Hydraulic pump drive over-dimensioned for the normal operating state of the vibration drive.
  • FIG. 3 shows a vibration drive of a vibration roller in a closed hydraulic circuit design. While the disclosed above with reference to Figures 1 and 2 open hydraulic circuit design is mainly intended for lighter weight vibratory rollers, a vibration drive of the closed hydraulic circuit design is usually provided for heavy vibratory rollers with corresponding heavyweight unbalance vibration exciters.
  • the imbalance masses can be driven in a simple manner by reversing the conveying direction of a pump which can be pivoted over zero in both directions of rotation. By reversing the direction of rotation, different frequencies and amplitudes of vibration are often realized.
  • the vibratory drive according to FIG. 3 has an adjustable over zero
  • Hydraulic pump 1 with a drive unit M, beispei mecanic a Internal combustion engine is mechanically connected.
  • the hydraulic pump 1 delivers fluid via a working line 4 to at least one hydraulic motor 6, which via a
  • Output shaft 32 is coupled to an unbalance vibration generator 34 shown in Figure 5.
  • further hydraulic motors can be inserted serially to the above-mentioned hydraulic motor in the working line, as shown for example in FIG. 3 by the second hydraulic motor shown in dashed lines there.
  • vibration rollers of the heavy embodiment often have two drums in which an unbalance vibration generator 34 according to the invention is used in each case. In this case, at least two hydraulic motors are required for their drive.
  • An output terminal of the at least one hydraulic motor 6 is via a
  • Return line 50 fluidly connected to an input port of the hydraulic pump 1. This creates a closed hydraulic circuit. It is understood that in a reverse conveying direction of the hydraulic pump 1, the line 50, the working line and the line 4 is the return line. Parallel to the at least one hydraulic motor 6, an energy recovery line 16 is arranged, which bypasst the input terminal and the output terminal of the hydraulic motor 6.
  • Recovery line 6 is a biased high-pressure accumulator 8 connected at a branch point. Further, in the recovery line 16 which actually connects the working line 4 and the return line 50 to each other, two 2-way 2-position switching valves 52/54 interposed such that the junction of the high-pressure accumulator 18 to the recovery line 16 between them two switching valves 52, 54 is located. Both switching valves 52, 54 are each spring-biased in a blocking switching position and can be switched independently of electromagnetically in an open position.
  • Parallel to the recovery line 16 a feed line 56 is arranged, which also starts from the working line 4 and the return line 50.
  • a 3/3-way switching valve 58 is interposed, to which a low-pressure accumulator 60 is connected.
  • the switching valve 58 is designed so that it in the lateral switching positions the low-pressure accumulator 60 optionally with the
  • the low-pressure accumulator 60 In a second switching position of the switching valve 58, the low-pressure accumulator 60 is fluidly connected via the feed line 56 to the working line 4. In a third switching position of the low-pressure accumulator 60 is fluidly connected via the feed line 56 to the return line 50.
  • control lines On two control sides of the switching valve 58 control lines are connected, which on one side with the working line and on the other side with the
  • the low-pressure accumulator 60 has a pressure relief line 62, which leads to the pressure medium tank 2 and in which a pressure relief valve 64 is interposed.
  • the vibration drive according to the figure 3 is provided with a balancing pump 66 which to compensate for oil leakage to the hydraulic circuit of
  • the balance pump 66 is fluidly connected to the pressure medium tank 2 via an intake passage.
  • the output connection of the compensation pump 66 opens into a compensation line 68, which the working line 4 and the
  • Compensation line 68 and the working line 4 is a check valve 70th
  • Pressure limiting valve 72 is arranged, which opens in the case of too high a pressure in the working line 4 in the direction of the discharge point between the equalizing pump 66 and the equalizing line 68.
  • a comparable construction can be found in the equalization line 68 between the discharge point and the return line 50.
  • D. h. Between the discharge point of the balancing pump 66 in the compensation line 68 and the return line 50 is also a check valve 74 interposed, which allows only a flow in the direction of the return line 50. Parallel to this check valve 74, a pressure limiting valve 76 is arranged, which in the case that in the
  • the displacement-variable hydraulic pump 1 is withdrawn with respect to its capacity (set to zero), so that the hydraulic motor 6 now no torque to the
  • Output shaft 32 gives more.
  • Imbalance vibration exciter 34 temporarily releases this torque (trailing operation) via the output shaft 32 to the hydraulic motor 6, as a result of which it temporarily assumes the function of a pump.
  • the hydraulic motor 6 now promotes pressure medium in the return line 50th
  • the switching valve 54 is electromagnetically opened between the high-pressure accumulator 18 and the return line 50, so that the pressure medium temporarily conveyed by the hydraulic motor 6 is fed into the high-pressure accumulator 16.
  • the switching valve 54 closes between the high-pressure accumulator 18 and the return line 50. Since, during the pushing operation, pressure medium therefore flows out of the closed circuit This is compensated by appropriate switching of the 3-way 3-position switching valve 58 in the feed line 56, which is in. In the hydraulic circuit and in particular in the working line 4. This is compensated by appropriate switching of the 3-way 3-position switching valve 58 in the feed line 56 Consequence of an adjusting pressure difference between the working line 4 and the return line 50 is switched to its second switching position, in which the low-pressure accumulator 60 is fluidly connected to the working line 4. D. h., The temporarily stored in the high-pressure accumulator 18 pressure medium is in the closed hydraulic circuit on the
  • the 2-way 2-position switching valve 52 is opened between the high-pressure accumulator 18 and the working line 4, whereby the compressed in the high-pressure accumulator 18 under pressure pressure medium is fed into the working line 4. In this way, the necessary for starting the hydraulic motor 6 and to overcome the inertia of the unbalance vibration generator 34 power from the high-pressure accumulator 18 can be applied. If the acceleration process is completed from the hydraulic accumulator 18, the valve 52 are brought into its blocking position and the
  • the adjustment can turn time-dependent or depending on the speed or the
  • Low-pressure accumulator 60 is now fluidly connected to the return line 50.
  • D. h. The excess of pressure medium, which arises by relaxing the high-pressure accumulator 18 in the closed hydraulic circuit is tapped via the low-pressure accumulator 60 and stored there between. Should a pressure medium leakage occur in the closed hydraulic circuit system, this causes the hydraulic pressure built up by the equalizing pump 66 at the respective check valves 70, 74 to open one or the other non-return valve in the direction of the working line 4 or the return line 50, whereby the corresponding leakage is compensated.
  • FIG. 4 now shows a second variant of a closed loop hydraulic circuit according to the second preferred embodiment. For reasons of simplification, only the embodiments that differ from the variant according to FIG. 3 will be discussed in more detail below.
  • Feed line 56 fluidly connected.
  • the 2-way 2-position switching valve 78 is interposed, which is spring-biased in the locked position. Furthermore, the other 2-way 2-position switching valve 80 is interposed between the discharge point and the return line 50, which is also spring-biased in the locked position.
  • the functioning of both valves 78, 80 corresponds to that mode of operation of the 3-way 3-position switching valve 58 according to FIG. 3. That is, in a shift operation of the hydraulic motor 6, in which the hydraulic motor 6 feeds pressure medium into the high-pressure accumulator 18 in that the switching valve 78 is open between the working line 4 and the discharge point, so that a corresponding amount of pressure medium can flow from the low-pressure accumulator 60 to the working line 4.
  • the switching valve 80 is opened between the discharge point and the return line 50 to the now excess and pressure-consuming pressure medium from the downstream port of the hydraulic motor 6 in the
  • the stored energy can preferably be used to accelerate the rotating masses of the vibration drive in vibratory rollers to
  • a storage and release of the recycled energy can also in the
  • the vibration drive allows a reduction (reduction) of the maximum drive power of an internal combustion engine to be installed as
  • the hydraulic pressure accumulators (high-pressure / low-pressure accumulators) can be freely arranged or integrated in / on the vehicle frame.
  • the required switching valves and the hydrostatic vibration drive can be controlled electrically or electronically in the system.
  • a vibration drive a vibratory roller with an unbalance vibration exciter, which in at least one by an external drive or
  • Propulsion unit operated bandage of the vibratory roller is rotatable relative to this in at least one direction.
  • the unbalance vibration generator according to the invention is mechanically coupled to a hydraulic motor, the one of
  • Hydraulic pump can be supplied with a pressure medium for rotation of the unbalance vibration exciter. Furthermore, at least one high-pressure accumulator is provided for receiving pressure medium conveyed by the hydraulic motor in a pushing operation.
  • the high pressure accumulator feeds pressure medium stored in a drive operation of the hydraulic motor to the hydraulic motor.

Landscapes

  • Engineering & Computer Science (AREA)
  • Architecture (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Road Paving Machines (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

Système destiné à produire des vibrations dans un rouleau vibrant, qui comporte un vibreur à balourd pouvant être placé dans au moins un tambour, entraîné par un bloc d'entraînement ou d'avance externe, du rouleau vibrant, et rotatif par rapport à ce rouleau dans au moins un sens. Selon l'invention, le vibreur à balourd est couplé mécaniquement à un moteur hydraulique qui peut être alimenté en fluide sous pression par une pompe hydraulique pour faire tourner le vibreur à balourd. Ledit système comporte en outre un réservoir à fluide sous pression destiné à recevoir du fluide sous pression refoulé par le moteur hydraulique dans un fonctionnement en mode de refoulement. En outre, le réservoir à fluide sous pression envoie au moteur hydraulique du fluide sous pression accumulé lors du fonctionnement en mode d'entraînement dudit moteur hydraulique.
EP10801138.8A 2010-02-05 2010-12-22 Système destiné à produire des vibrations Not-in-force EP2531305B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010006993A DE102010006993A1 (de) 2010-02-05 2010-02-05 Vibrationsantrieb
PCT/EP2010/007884 WO2011095200A2 (fr) 2010-02-05 2010-12-22 Système destiné à produire des vibrations

Publications (2)

Publication Number Publication Date
EP2531305A2 true EP2531305A2 (fr) 2012-12-12
EP2531305B1 EP2531305B1 (fr) 2015-03-18

Family

ID=43618041

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10801138.8A Not-in-force EP2531305B1 (fr) 2010-02-05 2010-12-22 Système destiné à produire des vibrations

Country Status (5)

Country Link
US (1) US9782800B2 (fr)
EP (1) EP2531305B1 (fr)
CN (1) CN102791389B (fr)
DE (1) DE102010006993A1 (fr)
WO (1) WO2011095200A2 (fr)

Families Citing this family (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013103722B4 (de) * 2013-04-12 2016-10-13 Thyssenkrupp Tiefbautechnik Gmbh Vibrationsrammanordnung sowie Verfahren zum Betrieb der Vibrationsrammanordnung
US10669677B2 (en) 2013-12-16 2020-06-02 Volvo Construction Equipment Ab Hydraulic system for driving a vibratory mechanism
DE102013227032A1 (de) 2013-12-20 2015-06-25 Hamm Ag Antriebssystem, insbesondere für eine selbstfahrende Baumaschine, insbesondere Bodenverdichter
DE102013227007B4 (de) * 2013-12-20 2024-05-16 Hamm Ag Selbstfahrende Baumaschine, insbesondere Bodenverdichter
CN104195926B (zh) * 2014-08-13 2017-04-19 潍柴动力股份有限公司 压路机液压系统、控制方法及其压路机
CN104329299B (zh) * 2014-10-27 2016-11-16 潍柴动力股份有限公司 一种压路机振动能量回收再利用系统及方法
DE102016201971B4 (de) * 2016-02-10 2021-04-22 Robert Bosch Gmbh Hydraulische Antriebsvorrichtung mit lastabhängigem Druckteiler
US10000895B2 (en) * 2016-10-06 2018-06-19 Caterpillar Inc. Rotating hydraulic gear motor
CA3037196A1 (fr) 2016-12-21 2018-06-28 A & A International, Llc Systeme integre de conversion, de transfert et d'accumulation d'energie
CN110248849B (zh) * 2016-12-21 2022-10-25 A&A国际有限公司 集成式能量转换、传递和存储系统
CN110621825B (zh) * 2017-06-07 2022-09-06 沃尔沃建筑设备公司 用于工程机械的液压系统
US10584449B2 (en) 2018-07-03 2020-03-10 Caterpillar Inc. Start assist for a vibratory system of a compactor
DE102019002439A1 (de) * 2019-04-03 2020-10-08 Bomag Gmbh Bodenverdichtungsmaschine mit elektrischem Motor und Verfahren zum Betrieb
DE102021200285A1 (de) * 2021-01-14 2022-07-14 Robert Bosch Gesellschaft mit beschränkter Haftung Verdichtungsfahrzeug, bei welchem ein Fahrantrieb und eine Vibrationseinheit von einer gemeinsamen Versorgungstelle her mit Druckfluid versorgt werden
CZ309275B6 (cs) 2021-03-03 2022-07-06 Ammann Schweiz Ag Způsob bezpečného řízení hutnicího stroje a hutnicí stroj k uskutečnění tohoto způsobu
DE102021206135A1 (de) 2021-06-16 2022-12-22 Robert Bosch Gesellschaft mit beschränkter Haftung Hydrostatischer Antrieb für eine Walze und Verfahren zur Leistungsverteilung eines derartigen Antriebs

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3867073A (en) 1972-09-20 1975-02-18 Raygo Inc Control for fluid motor
DE4033793A1 (de) 1990-10-24 1992-04-30 Wacker Werke Kg Vibrationswalze
DE19514985A1 (de) 1995-04-24 1996-10-31 Bald Hubert Einrichtung zur Kurzzeit-Energiespeicherung beim Betrieb von hydraulischen Arbeitsgeräten und hydraulisches Leistungsaggregat hierzu
CN2455762Y (zh) * 2000-02-29 2001-10-24 陕西省水利机械厂 单边驱动拖式振动压路机
DE102006060014B4 (de) 2005-12-20 2009-05-14 Bosch Rexroth Aktiengesellschaft Hydrostatischer Antrieb mit Rückgewinnung von Bremsenergie
DE102005060994B4 (de) * 2005-12-20 2009-04-09 Bosch Rexroth Aktiengesellschaft Hydrostatischer Antrieb mit Rückgewinnung von Bremsenergie
DE102006050873A1 (de) * 2006-10-27 2008-04-30 Robert Bosch Gmbh Hydrostatischer Antrieb mit Bremsenergierückgewinnung
CN101265686A (zh) * 2007-03-13 2008-09-17 徐州工程机械科技股份有限公司 一种新型的振动压路机液压电器控制系统
WO2009065556A1 (fr) 2007-11-20 2009-05-28 Robert Bosch Gmbh Entraînement hydrostatique et procédé pour faire fonctionner un véhicule
CN101613987B (zh) * 2009-06-22 2012-01-18 赵铁栓 振动压路辊的无级可调激振器

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2011095200A2 *

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Publication number Publication date
US20130025385A1 (en) 2013-01-31
DE102010006993A1 (de) 2011-08-11
CN102791389A (zh) 2012-11-21
US9782800B2 (en) 2017-10-10
WO2011095200A2 (fr) 2011-08-11
WO2011095200A3 (fr) 2012-04-19
CN102791389B (zh) 2014-11-19
EP2531305B1 (fr) 2015-03-18

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