EP2531305B1 - Vibrationsantrieb - Google Patents

Vibrationsantrieb Download PDF

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Publication number
EP2531305B1
EP2531305B1 EP10801138.8A EP10801138A EP2531305B1 EP 2531305 B1 EP2531305 B1 EP 2531305B1 EP 10801138 A EP10801138 A EP 10801138A EP 2531305 B1 EP2531305 B1 EP 2531305B1
Authority
EP
European Patent Office
Prior art keywords
hydraulic motor
pressure accumulator
hydraulic
pressure
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.)
Not-in-force
Application number
EP10801138.8A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2531305A2 (de
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/de
Application granted granted Critical
Publication of EP2531305B1 publication Critical patent/EP2531305B1/de
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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.
  • the unbalance vibration exciter consists of an imbalance shaft which is set in rotation by a separate 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 which are fluid-connected via a hydraulic system to a hydraulic pump driven by an internal combustion engine.
  • the DE 195 14 985 discloses a vibratory hammer with a memory for short-term storage of excess energy.
  • 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 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 to temporarily store the hydraulic fluid delivered by the hydraulic motor (now acting as a hydraulic pump).
  • the high-pressure accumulator is connected to the upstream connection of the hydraulic pump and thus delivers high-pressure fluid to the hydraulic pump. This reduces the energy consumption of the hydro-pressure pump.
  • the hydraulic accumulator is connected to the upstream port of the hydraulic motor.
  • the basic idea of the invention therefore consists in not using the (energy-irrelevant) pushing operation of the vibrating roller from the propulsion motor for energy recovery, but rotatably using the vibration drive of the vibrating roller comprising an unbalance vibration exciter of the vibratory roller driven in at least one preferably driven by the propulsion motor.
  • the unbalance vibration generator is mechanically coupled (preferably via an output shaft) with a hydraulic motor or coupled, which in turn can be supplied by a hydraulic pump with a pressure medium via working lines.
  • this hydrostatic drive of the unbalance vibration exciter i. h.
  • the invention for energy recovery does not provide the propulsion unit, but the vibratory drive as the relevant for the energy recovery drive.
  • This vibratory drive can work independently of the propulsion unit even at a standstill of the vibratory roller. It can be effectively used for energy recovery.
  • 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 (phasing out of unbalance vibration), the downstream connection of the hydraulic motor and in acceleration mode (start of the imbalance vibrator) of the upstream connection 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 is selectively fluid-connectable to the downstream connection of the hydraulic motor or to the upstream connection of the hydraulic motor.
  • a low-pressure accumulator is preferably provided, which can be connected in sliding operation of the hydraulic motor with its upstream connection and which can be connected in its drive operation of the hydraulic motor with its downstream connection.
  • the connection between the downstream port of the hydraulic motor and the upstream port of the hydraulic pump is maintained continuously.
  • the vibration drive has a hydraulic pump 1, whose suction port is fluid-connected to a pressure medium tank 2 and whose Pressure port via a working line 4 with an upstream port of a hydraulic motor 6 is fluidly connected.
  • a spring-biased check valve 8 is interposed, which is set in the present case to a working pressure of about 2 bar.
  • branches off from the working line 4 a branch line 10 to the pressure medium tank 2, in which an electro-proportionally adjustable pressure relief valve 12 is interposed. This can be adjusted, for example, between 8 bar and 250 bar.
  • 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 shift position, this shift valve 22 connects the downstream port of the hydraulic motor 6 to the high pressure accumulator 18.
  • the shift valve 22 connects the high pressure accumulator 18 to an energy return line 24 connected to the upstream port of the hydraulic motor 6 downstream of the check valve 8.
  • this return line 24 is also a spring-biased check valve 26 interposed, which is preferably set to 2 bar opening pressure.
  • a branch line 28 is connected, leading to the pressure medium tank 2 and in which a pressure relief valve 30 (preferably set to 250 bar) is interposed ,
  • the pressure limiting valve 12 is set to a very small value, so that the pressure upstream of the hydraulic motor 6 drops to 6 bar, for example.
  • the unbalance vibration generator 34 oscillates or rotates due to its moment of inertia. In this case, a torque is transmitted via the output shaft 32 to the 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 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.
  • the residual amount that the hydraulic motor does not decrease from the amount of pressure medium delivered by the hydraulic pump 1 flows at low pressure via the pressure relief valve 12 to the tank.
  • 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 can also be switched or adjusted depending on the speed or the change in speed per unit time.
  • FIG. 2 shows a second variant of a vibration drive of a vibratory 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.
  • a proportional pressure relief valve 12 is 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.
  • FIG. 2 An alternative embodiment shows the second variant of the open hydraulic circuit design according to the FIG. 2 , Accordingly, the aforementioned proportional pressure relief valve 12 is replaced by a first fixed pressure relief valve 38, 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 and the spring-biased check valve 8 upstream of the hydraulic motor 6, ie, connects the output port of the hydraulic pump 1 to the output port of the hydraulic motor 6, and in which a 2-position 2-way Switching valve 42 is joined between.
  • This switching valve 42 is biased by a spring in its open position and can be switched electromagnetically in a locked position.
  • upstream of said 2-position 2-way switching valve 42 branches off a further branch line 44 from the bypass line 40, which leads to the pressure medium tank 2.
  • the 2-way 2-position switching valve 46 is arranged, which is spring-biased in a locking position and which is electromagnetically switchable into an open position.
  • the pressure relief valve 48 is arranged downstream, which is preferably set to a value between 10 and 20 bar.
  • 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 in the pressure medium tank 2.
  • the energy recovery from the outgoing unbalance vibration generator 34 which applies a torque to the hydraulic motor 6 in this state via the output shaft 32, takes place in Accordance with the vibration drive described above according to the FIG. 1 ,
  • the acceleration also takes place according to the exemplary embodiment FIG. 1 ,
  • the directional control valve 22 is brought into the switching position, in which the hydraulic accumulator is connected via the check valve 26 to the upstream connection of the hydraulic motor 6.
  • 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 FIG. 1 as well as the FIG. 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.
  • the hydraulic pump drive is oversized for the normal operating state of the vibration drive.
  • FIG. 3 shows a vibration drive of a vibratory roller in closed hydraulic circuit design. While the basis of the FIGS. 1 and 2 described 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 vibration 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 vibration drive according to the FIG. 3 has a zero adjustable hydraulic pump 1, which with a drive unit M, beispei mecanic one 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 an output shaft 32 with a in FIG. 5 shown unbalance vibration exciter 34 is coupled.
  • further hydraulic motors can be inserted serially to the above-mentioned hydraulic motor in the working line, such as in the FIG. 3 is shown by the dashed shown second hydraulic motor.
  • 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 to drive them.
  • An output connection of the at least one hydraulic motor 6 is fluid-connected via a return line 50 to an input connection 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.
  • an energy recovery line 16 is arranged, which bypasst the input terminal and the output terminal of the hydraulic motor 6.
  • a biased high-pressure accumulator 18 is connected at a branch point.
  • 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.
  • 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 fluid in the lateral switch positions the low-pressure accumulator 60 selectively with the working line 4 or with the return line 50 and in the spring-centered middle position the hydraulic accumulator 60 and the lines 4 and 50 against each other shuts off.
  • 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 are fluidly connected on one side with the working line and on the other side with the return line.
  • 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 FIG. 3 provided with a compensation pump 66 which is connected to compensate for oil leakage to the hydraulic circuit of the closed design.
  • 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 fluidly connects the working line 4 and the return line 50 in parallel to the feed line 56 and the recovery line 16.
  • a check valve 70 is interposed, which allows only a flow from the balance pump 66 to the working line 4.
  • a 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 point of discharge 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 relief valve 76 is arranged, which opens in the direction of the discharge point in the event that in the return line 50, an excessively high pressure. By the balancing pump 66, a pressure of 25 to 30 bar is maintained in the respective low pressure line 4 or 50.
  • the motor-driven hydraulic pump 1 promotes a working medium via the working line 4 to the upstream connection of the at least one hydraulic motor 6 in order to drive an unbalance vibration generator 34 via its output shaft 32.
  • the pressure-released pressure medium is then returned from the downstream end of the at least one hydraulic motor 6 via the return line 50 to the input port of the hydraulic pump 1.
  • the two switching valves 52, 54 are in their blocking position.
  • the switching valve 58 is due to the pressure in the working line 4 in its third switching position and connects the low pressure accumulator 60 to the return line 50th
  • the displacement-variable hydraulic pump 1 is withdrawn (set to zero) with respect to its delivery rate, so that the hydraulic motor 6 no longer outputs torque to the output shaft 32.
  • this temporarily (after-running operation) outputs a torque via the output shaft 32 to the hydraulic motor 6, as a result of which it temporarily assumes the function of a pump.
  • D. h. 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.
  • 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 is brought into its blocking position and the hydraulic pump 1 is pivoted from zero and adjusted to the corresponding speed of the hydraulic motor corresponding delivery volume. The adjustment can in turn be time-dependent or depending on the speed or the speed change of the hydraulic motor. An appropriate speed sensor is in FIG. 4 located.
  • the hydraulic pump 1 and its drive M can be designed only for average operation and not for expected peak power, which can occur when starting the hydraulic motor 6.
  • the now additionally fed into the closed hydraulic circuit from the high-pressure accumulator 18 pressure medium causes the 3-position 3-way switching valve 58 moves in the feed line 56 in a switching position in which 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.
  • FIG. 4 Now, a second variant of a hydraulic circuit of the closed design according to the second preferred embodiment is shown. For reasons of simplification, only the variant according to FIG. 3 different embodiments discussed in more detail.
  • the stored energy can preferably be used to accelerate the rotating masses of the vibratory drive in vibratory rollers to compensate for power peaks.
  • a storage and release of the returned energy can also be done at standstill of the vehicle.
  • the vibration drive allows a reduction (reduction) of the maximum drive power to be installed of an internal combustion engine as a drive unit of the hydraulic pump.
  • the fuel consumption of a downsized internal combustion engine is reduced.
  • 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.
  • the pressure medium supply of the hydraulic motor from the hydraulic accumulator and from the hydraulic pump is preferably carried out sequentially.
  • a vibration drive a vibratory roller with an unbalance vibration exciter, which is at least one rotatable by at least one driven by an external drive or propulsion aggregate bandage of the vibratory roller relative thereto in at least one direction.
  • the unbalance vibration generator according to the invention is mechanically coupled to a hydraulic motor, which is supplied by a hydraulic pump with a pressure medium for rotation of the unbalance vibration exciter.
  • at least one high-pressure accumulator is provided for receiving pressure medium conveyed by the hydraulic motor in a pushing operation. Furthermore, the high-pressure accumulator feeds pressure medium stored in a drive operation of the hydraulic motor to the hydraulic motor.

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  • Engineering & Computer Science (AREA)
  • Architecture (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Road Paving Machines (AREA)
  • Fluid-Pressure Circuits (AREA)
EP10801138.8A 2010-02-05 2010-12-22 Vibrationsantrieb Not-in-force EP2531305B1 (de)

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 (de) 2010-02-05 2010-12-22 Vibrationsantrieb

Publications (2)

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

Family

ID=43618041

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10801138.8A Not-in-force EP2531305B1 (de) 2010-02-05 2010-12-22 Vibrationsantrieb

Country Status (5)

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

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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
US11128136B2 (en) * 2016-12-21 2021-09-21 A & A International, Llc Integrated energy conversion, transfer and storage system
CN115638142A (zh) 2016-12-21 2023-01-24 A&A国际有限公司 集成式能量转换、传递和存储系统
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

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CN101613987B (zh) * 2009-06-22 2012-01-18 赵铁栓 振动压路辊的无级可调激振器

Also Published As

Publication number Publication date
DE102010006993A1 (de) 2011-08-11
US9782800B2 (en) 2017-10-10
WO2011095200A2 (de) 2011-08-11
WO2011095200A3 (de) 2012-04-19
CN102791389B (zh) 2014-11-19
CN102791389A (zh) 2012-11-21
US20130025385A1 (en) 2013-01-31
EP2531305A2 (de) 2012-12-12

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