EP2531305B1 - Vibratory drive - Google Patents

Description

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. Thus, the vibratory roller has the ability to initiate additional energy in addition to its own weight in the underground.

From the prior art, for example, according to the DE 40 33 793 C2 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. There are also vibratory rollers in which the drive motor of at least one first hydraulic pump and the vibrator drive motor are supplied by at least one further hydraulic pump with pressure medium.

The DE 195 14 985 discloses a vibratory hammer with a memory for short-term storage of excess energy.

Furthermore, from the prior art, for example, according to the DE 10 2006 050 873 A or according to the DE 10 2006 060 014 A1 Hydrostatic drives with braking energy recovery in open or closed 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.

In the case of a drive mode of operation, 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. 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. In this particular case, 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).

As soon as the shift operation again turns into the drive mode and thus the hydraulic motor is again to deliver a torque to the drive shaft, 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. In other known hydraulic drives with energy recovery, the hydraulic accumulator is connected to the upstream port of the hydraulic motor.

Such regenerative hydrostatic drive systems are used in the prior art to recover energy from vehicles in coasting mode. However, this is not possible with vibratory rollers of the present type in this form, since vibratory rollers essentially do not reach an energy-relevant pushing operation in practical use.

In view of this situation, it is the object of the present invention to provide a possibility for energy recovery for vibratory rollers of this type.

This object is achieved by a vibration drive of a vibrating roller having the features of patent claim 1. Advantageous developments of the invention are the subject of the dependent claims.

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. can be used. 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. According to the invention, in this hydrostatic drive of the unbalance vibration exciter, i. h., Provided in the vibration drive at least one high-pressure accumulator, which is for receiving from the hydraulic motor in a pushing operation, d. h., In a discontinued operation of the unbalance vibration generator promoted pressure medium is used.

In other words, 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.

Alternatively, 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.

In the case of the open hydraulic circuit design, 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. In the case of the closed hydraulic circuit construction, 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. Preferably, the connection between the downstream port of the hydraulic motor and the upstream port of the hydraulic pump is maintained continuously.

The invention will be explained in more detail below with reference to two exemplary embodiments with reference to the accompanying figures.

• Figur 2 zeigt einen hydrostatischen Vibarationsantrieb einer Vibrationswalze gemäß dem ersten bevorzugten Ausführungsbeispiel in einer zweiten offenen Hydraulikkreis-Variante,
• Figur 3 zeigt einen hydrostatischen Vibrationsantrieb einer Vibrationswalze gemäß einem zweiten bevorzugten Ausführungsbeispiel der Erfindung in einer ersten geschlossenen Hydraulikkreis-Variante,
• Figur 4 zeigt einen hydrostatischen Vibrationsantrieb einer Vibrationswalze gemäß dem zweiten bevorzugten Ausführungsbeispiel in einer zweiten geschlossenen Hydraulikkreis-Variante und
• Figur 5 schematische Darstellung einer Vibrationswalze.

The FIG. 1 shows a hydrostatic vibration drive of a vibrating roller with energy recovery according to a first preferred embodiment of the invention in a first open hydraulic circuit variant,

• FIG. 2 shows a hydrostatic Vibrationationsantrieb a vibratory roller according to the first preferred embodiment in a second open hydraulic circuit variant,
• FIG. 3 shows a hydrostatic vibration drive of a vibratory roller according to a second preferred embodiment of the invention in a first closed hydraulic circuit variant,
• FIG. 4 shows a hydrostatic vibration drive of a vibratory roller according to the second preferred embodiment in a second closed hydraulic circuit variant and
• FIG. 5 schematic representation of a vibrating roller.

According to the FIG. 1 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. In the working line 4 while a spring-biased check valve 8 is interposed, which is set in the present case to a working pressure of about 2 bar. Furthermore, 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. Between the switching valve 14 and the downstream port of the hydraulic motor 6 branches off an energy recovery line 16, which leads to a biased (biasing pressure, for example, 150 bar) high-pressure accumulator 18. In this energy recovery line 16 in the present case, 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. In a third shift position, 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. In this return line 24 is also a spring-biased check valve 26 interposed, which is preferably set to 2 bar opening pressure.

Finally, in the energy recovery line 16 between the stormabwärtigen connection of the hydraulic pump 1 and the 3-way 3-position switching valve 22, 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 ,

In the case of a drive operation of the hydraulic motor 8, via an output shaft 32 with a in FIG. 5 unbalanced vibration exciter 34 is shown connected in principle, which is preferably arranged in a bandage 36 of a vibratory roller, is initially the 3-way 3-position switching valve 22 in its according to the FIG. 1 shown first switching position in which the high-pressure accumulator 18 is separated from the open hydraulic circuit. 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 is supplied from the hydraulic pump 1 via the spring-biased check valve 8 to the upstream port of the hydraulic motor 6 to drive it. From there, the now pressure-released pressure medium passes through the 2-way 2-position switching valve 14, which is in this situation in the open position back into the tank. 2

In order to switch off the unbalance vibration generator 34, 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, 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. In this case, 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. Decisive here is that the output shaft 32 of the hydraulic motor 6 is connected to the unbalance vibration exciter 34 of the vibratory roller, ie, the tracking energy of the unbalance vibration exciter 34 is used to recover energy in the form of hydraulic pressure in the high-pressure accumulator 18.

Is switched over from the shift mode back to a drive mode, d. That is, in an operation in which the hydraulic motor 6 outputs a torque to the output shaft 32, the 2-way 2-position switching valve 14 is switched to the open position and the 3-way 3-position switching valve 22 in the switched third switching position in which the connection between the downstream port of the hydraulic motor 6 and the high-pressure accumulator 18 is blocked and instead a connection between the high pressure accumulator 18 and the upstream port of the hydraulic motor 6 is made. In this switching position, therefore, the high pressure accumulator 18 pressure medium under pressure to the input side of the hydraulic motor 6, so that it accelerates the unbalance vibration generator 34 independent of the hydraulic pump. At this stage, the hydraulic pump initially still circulates at low pressure. After a lying in the range of seconds period, which can be determined by experiment or by calculation, 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.

If the speed of the hydraulic motor detected by a speed sensor, the valves 22 and 12 can also be switched or adjusted depending on the speed or the change in speed per unit time.

The 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.

In the above first variant, as already stated, 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. With him, 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 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. In addition, 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. Furthermore, 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. In this branch line 44, 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. This further 2-way 2-position switching valve 46, the pressure relief valve 48 is arranged downstream, which is preferably set to a value between 10 and 20 bar. The remaining structure of the hydraulic circuit of the open design according to FIG. 2 corresponds to the hydraulic circuit of the first variant, as already described above with reference to the FIG. 1 has been described, so that reference can be made at this point to the corresponding description text passages.

Also in the vibration drive of the vibratory roller according to the FIG. 2 promotes the hydraulic pump 1, a pressure medium via the spring-biased check valve 8 for upstream connection of the hydraulic motor 6, so that this torque an output shaft 32 for driving an in FIG. 5 shown unbalance vibration generator 34 outputs. The pressure-released pressure medium is then discharged via the biased in the open position 2-position 2-way switching valve in the pressure medium tank 2. In this drive phase, the two valves 42 and 46 are in their blocking position.

If the vibration drive is turned off, the 2-way 2-position switching valve 46 is switched from its closed position to the open position. In this case, 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 , For this purpose, 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. 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.

At this point it should be noted that 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. In other words, for the startup of the hydraulic motor 6, at least for a short time, an excessive power is demanded by the hydraulic pump drive. In order to bring this power, usually the drive for the hydraulic pump 1 must be designed so that the starting peak power is applied by this. In this respect, the hydraulic pump drive is oversized for the normal operating state of the vibration drive.

Due to the arrangement of the high-pressure accumulator 18, which is loaded as part of an energy recovery by the leakage of the unbalance vibration exciter 34 and the associated drive of the hydraulic motor 6, this can briefly feed energy for starting the hydraulic motor 6 in the system and thus the hydraulic pump. 1 relieve. This has the consequence that the hydraulic pump drive can be reduced accordingly in terms of its maximum power.

In the following, a second preferred embodiment of the invention with reference to two variants according to the Figures 3 and 4 described in more detail.

The 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.

Furthermore, with a hydraulic drive in a closed circuit, 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, beispeisweise 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. Optionally, 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.

It should be noted at this point that 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. 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. To the recovery line 16, a biased high-pressure accumulator 18 is 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. In the feed line 56, 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.

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.

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. Finally, 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.

Finally, 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.

Specifically, 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. Between the discharge point of the compensating pump 66 in the compensation line 68 and the working line 4, a check valve 70 is interposed, which allows only a flow from the balance pump 66 to the working line 4. Parallel to the check valve 70, 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.

In normal operation, 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. In normal operation, 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

If now the at least one hydraulic motor 6 are switched off, 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. As a result of the inertia of the at least one unbalance vibration generator 34, however, 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

In this case, 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. As soon as this follow-on or overrun operation of the hydraulic motor 6 has ended, 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. In other words, the pressure medium temporarily stored in the high-pressure accumulator 18 is compensated in the closed hydraulic circuit via the low-pressure accumulator 60, but additionally also by the compensating pump 66.

As soon as the normal drive operation of the at least one hydraulic motor 6 is to start, 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. Accordingly, 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.

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.

In the 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 FIG. 3 different embodiments discussed in more detail.

Like from the FIG. 4 in comparison to FIG. 3 can be seen, is now that according to the FIG. 3 provided 3-way 3-position switching valve 58 by two separately electromagnetically switchable 2-way 2-position switching valves 78, 80 replaced. In concrete terms, the low-pressure accumulator 60 is fluid-connected to the feed line 56 at a point of confluence. Between the junction and the working line 4, 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 operation of both valves 78, 80 correspond to that operation of the 3-way 3-position switching valve 58 according to FIG. 3 , D. h., That in a shift operation of the hydraulic motor 6, in which the hydraulic motor 6 feeds pressure medium into the high-pressure accumulator 18, the switching valve 78 between the working line 4 and the discharge point is open, so that a corresponding pressure medium amount from the low-pressure accumulator 60 to the working line. 4 can flow. In the event of a restart of the unbalance vibration generator 34, the switching valve 80 between the discharge point and the return line 50 is opened to allow the now excess and pressure-consuming pressure medium from the downstream port of the hydraulic motor 6 to flow back into the low-pressure accumulator 60. All other functions of the closed hydraulic circuit according to FIG. 4 correspond to those of FIG. 3 , so that at this point on the corresponding text passages can be referenced.

With the vibration drive according to the invention, which has been described with reference to the above two embodiments, the following advantages can be achieved:

An energy recovery in a vibratory roller is now possible by storing the rotational energy from the vibration drive or from the imbalance masses.

The stored energy can preferably be used to accelerate the rotating masses of the vibratory drive in vibratory rollers to compensate for power peaks.

There is no hydraulic connection / coupling between the vibration drive and the drive of a vibrating roller instead.

There is no use of the translational energy of the vehicle, which is energetically irrelevant because vehicles such as the vibratory roller in the working medium without drive are immediately delayed independently.

A storage and release of the returned energy can also be done at standstill of the vehicle.

A realization of the vibration drive with energy feedback is possible with simple commercially available valves.

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.

There is a lesser need for installation space required by a smaller internal combustion engine.

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.

When accelerating the unbalance vibration exciter, the pressure medium supply of the hydraulic motor from the hydraulic accumulator and from the hydraulic pump is preferably carried out sequentially.

Disclosed is 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. Furthermore, 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.

Claims (10)

1. Vibratory drive of a vibrating roller, comprising an unbalance vibrator (34) which can be inserted so as to be relatively rotatable in at least one direction in at least one drum (36), driven by an external drive unit, of the vibrating roller, wherein the unbalance vibrator (34) is mechanically coupled to a hydraulic motor (6) which can be supplied with a pressure medium by a hydraulic pump (1) in order to rotate the unbalance vibrator (34), characterized in that at least one high pressure accumulator (18) is provided for accommodating pressure medium which is delivered by the hydraulic motor (6) in an overrun mode.
2. Vibratory drive according to Claim 1, characterized in that in a drive mode of the hydraulic motor (6) the high pressure accumulator (18) feeds stored pressure medium to the hydraulic motor (6).
3. Vibratory drive according to Claim 1 or 2, characterized in that the hydraulic pump (1) and the hydraulic motor (6) are arranged in an open circuit in which the downstream connection of the hydraulic motor (6) can be optionally fluidically connected to a tank (2) or to the high pressure accumulator (18).
4. Vibratory drive according to Claim 3, characterized in that the high pressure accumulator (18) can be fluidically connected to the tank (2) via a pressure-limiting valve (30).
5. Vibratory drive according to one of the preceding claims, characterized by a valve arrangement (20) via which the high pressure accumulator (18) can be optionally fluidically connected to the downstream connection of the hydraulic motor (6) or to the upstream connection of the hydraulic motor (6).
6. Vibratory drive according to Claim 1 or 2, characterized in that the hydraulic pump (1) and the hydraulic motor (6) are arranged in a closed circuit in which the downstream connection of the hydraulic motor (6) is fluidically connected to the high pressure accumulator (18) in the overrun mode, and the upstream connection of the hydraulic motor (6) is connected to the high pressure accumulator (18) in the drive mode.
7. Vibratory drive according to Claim 6, characterized by a low pressure accumulator (60) which, in the overrun mode of the hydraulic motor (6) can be connected to the upstream connection thereof, and in the drive mode of the hydraulic motor (6) can be connected to the downstream connection thereof.
8. Vibratory drive according to claim 6 or 7, characterized in that a recovery valve arrangement (20) is connected upstream of the high pressure accumulator (18), in order to optionally fluidically connect the high pressure accumulator (18) to the upstream or downstream connection of the hydraulic motor (6).
9. Vibratory drive according to one of Claims 6 to 8, characterized in that a pressure medium-equalizing valve arrangement (82) is connected upstream of the low pressure accumulator (60) in order to optionally fluidically connect the low pressure accumulator (60) to the upstream or downstream connection of the hydraulic motor (6).
10. Vibratory drive according to Claims 8 and 9, characterized by a valve controller for controlling the pressure medium-equalizing valve arrangement (82) as a function of the switched position of the recovery valve arrangement (20).

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