[go: up one dir, main page]

EP4278044B1 - Véhicule de compactage dans lequel un système d'entraînement et une unité de vibration sont alimentés en fluide sous pression par un point d'alimentation commun - Google Patents

Véhicule de compactage dans lequel un système d'entraînement et une unité de vibration sont alimentés en fluide sous pression par un point d'alimentation commun Download PDF

Info

Publication number
EP4278044B1
EP4278044B1 EP22700286.2A EP22700286A EP4278044B1 EP 4278044 B1 EP4278044 B1 EP 4278044B1 EP 22700286 A EP22700286 A EP 22700286A EP 4278044 B1 EP4278044 B1 EP 4278044B1
Authority
EP
European Patent Office
Prior art keywords
hydraulic machine
hydraulic
supply point
compacting vehicle
displacement volume
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP22700286.2A
Other languages
German (de)
English (en)
Other versions
EP4278044A1 (fr
Inventor
Karsten Penert
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 EP4278044A1 publication Critical patent/EP4278044A1/fr
Application granted granted Critical
Publication of EP4278044B1 publication Critical patent/EP4278044B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • E—FIXED CONSTRUCTIONS
    • E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
    • E01C—CONSTRUCTION OF, OR SURFACES FOR, ROADS, SPORTS GROUNDS, OR THE LIKE; MACHINES OR AUXILIARY TOOLS FOR CONSTRUCTION OR REPAIR
    • E01C19/00—Machines, tools or auxiliary devices for preparing or distributing paving materials, for working the placed materials, or for forming, consolidating, or finishing the paving
    • E01C19/22—Machines, tools or auxiliary devices for preparing or distributing paving materials, for working the placed materials, or for forming, consolidating, or finishing the paving for consolidating or finishing laid-down unset materials
    • E01C19/23—Rollers therefor; Such rollers usable also for compacting soil
    • E01C19/28—Vibrated rollers or rollers subjected to impacts, e.g. hammering blows
    • E01C19/286—Vibration or impact-imparting means; Arrangement, mounting or adjustment thereof; Construction or mounting of the rolling elements, transmission or drive thereto, e.g. to vibrator mounted inside the roll

Definitions

  • the invention relates to a compaction vehicle according to the preamble of claim 1.
  • a compaction vehicle in the form of a road roller is known.
  • the compaction vehicle has two circular cylindrical rollers that roll over a subsoil to smooth it. At least one of the rollers can be equipped with a vibration unit to improve subsoil compaction.
  • compaction vehicles are known from the state of the art, and these can comprise up to six hydraulic motors. It would now be logical to supply all of these hydraulic motors with pressurized fluid in an open hydraulic circuit using a common pump, with the direction and speed of each hydraulic motor being controlled by an associated valve. However, the throttling losses arising in such valves are very high. Therefore, the hydraulic motors are usually operated in a closed hydraulic circuit, with the speed and direction of rotation being adjusted by adjusting the displacement of the respective hydraulic machines. However, not an unlimited number of hydraulic motors can be connected to a common pump in a closed hydraulic circuit. Typically, a maximum of two hydraulic motors can be connected to a common pump, and then only if the two hydraulic motors have comparable are exposed to stresses. Accordingly, a compaction vehicle constructed in this way has several pumps, each of which is operated by a few associated hydraulic motors in a closed hydraulic circuit.
  • the invention seeks to create a compaction vehicle with a hydraulic drive, allowing any configuration of hydraulic motors or first and second hydraulic machines. Ideally, only a single pump or third hydraulic machine should be used to supply all hydraulic motors or first and second hydraulic machines with pressurized fluid. Valves and the associated throttling losses in the primary energy transmission from the third hydraulic machine to the first or second hydraulic machines should be eliminated as completely as possible.
  • the at least one first, the at least one second and the third hydraulic machines are each connected on the high-pressure side to a common supply point and on the low-pressure side to a common tank, so that they form an open hydraulic circuit, wherein the said connection to the supply point can be continuously released in such a way that a high pressure in the at least one first, in the at least one second and in the third hydraulic machines is substantially equal to the pressure at the supply point, wherein the at least one first, the at least one second and the third hydraulic machines each have an adjustable displacement volume, wherein a displacement volume of the at least one second hydraulic machine is adjustable in such a way that the desired vibration intensity is achieved while the said connections to the supply point are released.
  • the vibration unit preferably comprises at least one mass rotatable relative to a rotational axis, the center of gravity of which is arranged away from said rotational axis, wherein the at least one mass is connected to an associated second hydraulic machine for rotational drive.
  • the vibration unit is preferably arranged inside the respective roller.
  • a continuously releasable connection should be understood, on the one hand, as a connection that is permanently open and most preferably has a constant, low flow resistance.
  • the continuously releasable connection can also be formed by a switching valve that has at least two discrete switching positions, with the connection having a constant, low flow resistance in each switching position.
  • the switching valve can, for example, be used to reverse the direction of rotation of the associated hydraulic machine without the hydraulic machine having to be adjustable beyond a displacement volume of zero.
  • the supply point is preferably a space filled with pressurized fluid, with essentially the same pressure prevailing throughout the entire space.
  • the supply point is preferably formed by an elongated line.
  • the supply point is preferably not a small, point-like location, but rather has a spatial extension.
  • a hydraulic machine is understood to be a machine that converts hydraulic power into mechanical power in the form of rotary motion and vice versa.
  • the hydraulic machines mentioned are preferably axial piston machines.
  • the at least one first and/or the at least one second hydraulic machine and the third hydraulic machine are preferably designed with a bent-axis design. This means that all hydraulic machines can be designed such that they are adjustable beyond zero displacement.
  • the bent-axis design otherwise preferred for hydraulic motors is not preferred for this very reason.
  • the open hydraulic circuit mentioned is preferably operated with a liquid pressurized fluid, with hydraulic oil being used most preferably.
  • the direction of rotation of the at least one first hydraulic machine can be reversed by adjusting the respective displacement volume, while the flow direction of the respective first hydraulic machine remains constant.
  • the displacement volume of the at least one first hydraulic machine can therefore be adjusted beyond zero displacement volume. This allows the direction of travel of the compaction vehicle to be reversed while the vibration drive continues to run unchanged.
  • the back and forth movement of the compaction vehicle which is frequently encountered when compacting a road surface while the vibration unit continues to run, can therefore be carried out without problems.
  • the change in direction of travel can be very smooth.
  • the direction of rotation of the at least one second hydraulic machine can also be reversible by adjusting the displacement volume. Depending on the design of the vibration unit, different vibration properties can thereby be achieved.
  • the supply point is connected to a hydraulic accumulator.
  • the pressure at the supply point essentially maintains a constant predefined value.
  • This predefined value can change if the desired operating state changes; it is therefore only temporarily constant as long as the desired operating state does not change.
  • this pressure value is preferably set by adjusting the displacement volume of the third hydraulic machine.
  • this control reacts comparatively sluggishly if the pressure at the supply point changes abruptly due to rapidly changing external loads on the at least one first or at least one second hydraulic machine. With the hydraulic accumulator, such abrupt changes in the pressure at the supply point can be mitigated so that the pressure control by means of the third hydraulic machine operates sufficiently quickly.
  • the filling and discharging speed of the hydraulic accumulator is preferably set in such a way that the entire compaction vehicle has optimally low energy consumption.
  • a valve unit can be assigned to the hydraulic accumulator, which controls the exchange of pressurized fluid between the supply point and the hydraulic accumulator depending on the pressure at the supply point. This is intended, in particular, to prevent the hydraulic accumulator from being overfilled. It must be avoided that an empty hydraulic accumulator interferes with the function of the hydraulic drive.
  • Two or more rollers may be provided, each connected to its own first hydraulic machine for rotational drive, with all first and second hydraulic machines connected to the same supply point and the same tank.
  • Each roller is preferably assigned a separate first hydraulic machine.
  • Each roller is preferably assigned its own vibration unit with its own second hydraulic machine.
  • the present invention is particularly useful because, compared to a conventional compaction vehicle, a particularly large number of pumps or third hydraulic machines can be dispensed with.
  • the supply point is connected to a pressure sensor, whereby the displacement volume of at least one second hydraulic machine can be adjusted depending on the pressure measured by the pressure sensor and the desired vibration intensity.
  • the corresponding relationship is preferably stored in a characteristic map.
  • the adjustment preferably takes place in the form of a control or pilot control. This eliminates the need for expensive controllers.
  • the achievable positioning accuracy is often sufficient for a vibration unit.
  • the supply point is connected to a pressure sensor, whereby the displacement volume of the third hydraulic machine can be adjusted depending on the pressure measured by the pressure sensor.
  • a pressure control system operating with a hydraulic pressure regulator would be preferred at this point, as this has proven itself and operates very reliably.
  • the hydraulic pressure control system can also cope well with the strong pressure fluctuations often encountered in a hydraulic drive. Nevertheless, within the scope of the present invention, an electronic pressure control system is preferred, even though a high level of computing power must be installed in the control device in order to achieve a control quality comparable to that of conventional hydraulic pressure control.
  • the setpoint of this control system should be very flexible and adapt to the current operating conditions of the
  • the pressure sensor can be adjusted to the compaction vehicle's operating conditions. This is much easier to achieve with electronic pressure control than with hydraulic pressure control.
  • the proposed pressure sensor can be used in the adjustment of the at least one first and at least one second hydraulic machine, which represents a preferred embodiment of the invention.
  • the single pressure sensor can thus be used for three different purposes.
  • a first control loop can be provided, the actual value of which is the pressure measured by the pressure sensor, and the manipulated variable of which is the displacement volume of the third hydraulic machine. Subsequently, the pressure at the supply point is regulated to a value specified by a target value. This pressure is thus no longer dependent on the driving resistance that the compaction vehicle must overcome during travel. It is also not dependent on the set vibration intensity or the drive torque of the at least one second hydraulic machine.
  • the corresponding target value is preferably selected such that the desired speed can be achieved at the at least one first hydraulic machine, wherein said speed determines the travel speed of the compaction vehicle.
  • the aim is to keep the pressure at the supply point as low as possible in order to save energy.
  • the speed of the at least one first hydraulic machine is preferably measured at least indirectly using a first speed sensor. It should be noted that all rollers typically rotate at the same peripheral speed, which is equal to the travel speed of the compaction vehicle. Accordingly, a single first speed sensor is normally sufficient. If slippage on the rollers is to be feared, several first speed sensors are preferably used to detect this slippage.
  • the speed of the third hydraulic machine is preferably measured using a third speed sensor, wherein the corresponding measured value is taken into account in the aforementioned control, in particular when determining the target value of the first control loop.
  • Protection is accordingly claimed for a method in which a setpoint value of the first control loop depends on the desired driving speed of the The value is selected depending on the compaction vehicle and/or the desired vibration intensity.
  • the travel speed for example, the drive torque of the rollers required to achieve the travel speed can be determined.
  • the maximum displacement volume of the first hydraulic machine determines the minimum required pressure at the supply point. The same procedure can be applied to the vibration intensity. The highest of the pressures determined in this way is decisive for determining the target value.
  • the setting of the target value of the first control loop is preferably carried out in the form of a control system, i.e. without feedback.
  • At least one second hydraulic machine is assigned a second speed sensor, by means of which a speed of the respective second hydraulic machine can be measured, wherein a second control loop is provided, the actual variable of which is a measured value of the second speed sensor, the manipulated variable of which is the displacement volume of the respective second hydraulic machine.
  • the target variable of the second control loop corresponds to the speed desired on the respective second hydraulic motor. This, in turn, is proportional to the desired vibration intensity.
  • the second control loop is preferably combined with the characteristic map explained above, which then operates as a so-called feedforward control.
  • the supply point may be formed by a line that extends at least 50% of the compaction vehicle's length in the direction of travel. This allows all hydraulic machines of the compaction vehicle to be easily connected to the supply point. It is understood that the free cross-sectional area of said line is preferably selected to be large enough to ensure essentially the same pressure at all points along the line.
  • the at least one first hydraulic machine, the at least one second hydraulic machine and/or the third hydraulic machine each comprise an actuating device which is designed to adjust the displacement volume of the respective hydraulic machine substantially proportionally to an actuating signal
  • the aforementioned actuating device preferably operates hydraulically. It preferably comprises an actuating cylinder, a control valve, and a position sensor. It preferably comprises a fourth control circuit, which, using the aforementioned components, adjusts the displacement volume to a setpoint predetermined by the actuating signal.
  • At least one first hydraulic machine is assigned a third control loop, the actual variable of which is the speed of the respective first hydraulic machine, the manipulated variable of which is the displacement volume of the respective first hydraulic machine. If several first hydraulic machines are provided, their displacement volumes are set either equally or in a fixed, predetermined ratio. Thus, in this case too, only a single third control loop is provided. This allows the travel speed to be set particularly precisely. Alternatively, it is conceivable to set the displacement volume of at least one first hydraulic machine by means of a further characteristic map which has the desired travel speed and the measured value of the pressure sensor at the supply point as input variables.
  • Fig. 1 shows a roughly schematic side view of a compaction vehicle 10 according to the invention.
  • the present compaction vehicle 10 is designed in the form of a road roller, with which a subsoil 11 in the form of a freshly asphalted road can be smoothed.
  • the compaction vehicle 10 has two rotatable, circular-cylindrical rollers 20, which roll on the subsoil to smooth it. In this case, only the front roller 20 is driven by a first hydraulic machine 21.
  • Fig. 1 shows an extraordinarily simple embodiment of a compaction vehicle according to the invention.
  • the present invention saves particularly significant costs when many first and second hydraulic machines 21; 31 are used, for example, when all rollers 20 are driven and simultaneously equipped with a vibration unit 30.
  • the compaction vehicle can also have more than two rollers 20.
  • the rear roller 20 is equipped with a vibration unit 30.
  • the vibration unit 30 is intended to exert a pulsating force perpendicular to the subsoil 11 on the associated roller 20, so that the subsoil 11 is more effectively compacted.
  • a rotatably mounted mass 33 can be used, the center of gravity of which is arranged off the axis of rotation or eccentrically. This mass 33 is connected to a second associated hydraulic machine 31 for rotational drive.
  • the supply point 50 is in the form of a line 54, which extends over at least 50% of the length of the compaction vehicle 10 in the direction of travel 15. This allows all Fig. 2 and 3 shown connections to the first and second hydraulic machines 21; 31 are established. Nevertheless, the pressure in line 54 is essentially the same everywhere.
  • Fig. 2 shows a circuit diagram of the hydraulic drive of the compaction vehicle 10 according to Fig. 1
  • the hydraulic drive comprises a supply point 50 in the form of an elongated line 54.
  • the first, second and third hydraulic machines 21; 31; 41 are connected to this with their high pressure side, wherein a permanently open, low-resistance fluid exchange connection is present. In this connection, no valves, throttles or the like are installed, so that the high pressure in the aforementioned hydraulic machines 21; 31; 41 is essentially the same as the pressure at the supply point 50.
  • the first, second and third hydraulic machines 21; 31; 41 are each designed as axial piston machines with an adjustable displacement volume.
  • the first and second axial piston machines 21; 31 are preferably designed as a swash plate design, wherein they are operated as a motor for the majority of the operating time. They are preferably adjustable above a displacement volume of zero.
  • the third hydraulic machine 41 is preferably designed as a swash plate design, wherein it is operated as a pump for the majority of the time. All hydraulic machines 21; 31; 41 are equipped with an actuating device 13 which is designed such that it adjusts the displacement volume of the respective hydraulic machine 21; 31; 41 is adjusted essentially proportionally to an associated control signal 14. Accordingly, no hydraulic pressure and/or power control takes place on the hydraulic machine 21; 31; 41 itself. Instead, the hydraulic drive is controlled as described below, preferably using an electronic control device.
  • the third hydraulic machine 41 is set in rotation by an associated drive motor 43.
  • the drive motor 43 is preferably a diesel engine, although any other type of engine, in particular an electric motor, can be used.
  • the drive motor 43 preferably runs with a fixed, predetermined direction of rotation.
  • the third hydraulic machine 41 pumps pressurized fluid from the tank 12 to the supply point 50, acting as a pump.
  • pressurized fluid flows from the supply point 50 via the third hydraulic machine 41 to the tank, with the third hydraulic machine 41 acting as a motor and thus temporarily relieving the load on the drive motor 43.
  • the low-pressure sides of the first, second, and third hydraulic machines 21; 31; 41 are each connected to the tank 12, resulting in an open hydraulic circuit. These connections to the tank are also permanently open and low-resistance, and preferably no valves, throttles, or the like are located there.
  • the entire hydraulic drive thus comes basically without valves, whereby the desired movement is brought about solely by adjusting the stroke volumes of the hydraulic machines 21; 31; 41.
  • a valve unit 52 is assigned to the supply point 50, which is connected between the supply point 50 and an optional hydraulic accumulator 51.
  • the hydraulic accumulator 51 is used to compensate for peaks in power requirements, for example when accelerating the vibration drive (No. 30 in Fig. 1 ), so that they do not place excessive strain on the drive motor 43, meaning that the latter does not have to be designed to be excessively large. Furthermore, pressure peaks at the supply point 50 are absorbed by the hydraulic accumulator 51.
  • the valve unit 52 initially adjusts a high pressure in the hydraulic accumulator 51 to a lower pressure at the supply point 50, so that the hydraulic accumulator 51 is discharged when it is sufficiently filled.
  • the valve unit 52 can be designed to be purely hydromechanical. It is preferably electrically adjustable, being adjusted by the electronic control device 16.
  • the hydraulic accumulator 51 is preferably provided with a pressure sensor (not shown) which is connected to the electronic control device 16, so that electronic control of the pressure in the hydraulic accumulator 51 can take place.
  • the first control circuit 60 regulates a pressure at the supply point 50 which is equal to the target value 63 of the first control circuit 60.
  • This target value 63 is dependent on the desired driving speed of the compaction vehicle and the desired vibration intensity of the vibration drive (No. 30 in Fig. 1 ).
  • the setpoint value 63 of the first control circuit 60 is preferably selected to be so small that the adjustment range of the first and second hydraulic machines 21; 31 is just sufficient to achieve the desired operating parameters (driving speed, vibration intensity).
  • the corresponding first controller 64 is embodied as a PID controller, although a PI or I controller may also be used.
  • the first controller 64 is preferably implemented by an electronic control device 16, which comprises a programmable digital computer.
  • the first controller 64 is assigned the The difference between the above-explained target variable 63 and the actual variable 61 is fed to the control circuit 60, with a manipulated variable 62 being present at its output, which forms the control signal 14 of the third hydraulic machine 41.
  • the actual variable 61 of the first control circuit 60 is the measured value of a pressure sensor 53, which is connected to the supply point 50.
  • Fig. 3 shows the Fig. 2 missing control of the second hydraulic machine 31.
  • Fig. 2 and 3 together they show a uniform hydraulic drive.
  • Fig. 3 shows the most complex control variant, in which a pre-control is carried out using a characteristic map 80, with the pre-control being superimposed on a closed-loop control with the second control loop 70.
  • a pre-control is carried out using a characteristic map 80, with the pre-control being superimposed on a closed-loop control with the second control loop 70.
  • the pre-control alone, without the second control loop 70 results in sufficiently good system behavior.
  • the second control loop 70 alone, without the pre-control results in sufficiently good system behavior.
  • the second control loop 70 comprises a second controller 74, which in this case is designed as a PID controller, although it can also be designed as a PI or I controller.
  • the difference between the actual variable 71 and the target variable 73 is fed to its input.
  • the actual variable 71 is formed from the measured value of the second speed sensor 32, i.e., the speed of the second hydraulic machine 31.
  • the target variable 73 corresponds to the speed of the second hydraulic machine 31 at which the desired vibration intensity 81 is achieved.
  • this control basically has an integral control behavior, whereby it subsequently reacts comparatively sluggishly to changes in the target variable 73. This problem can be remedied with feedforward control.
  • the pilot control comprises a characteristic map 80, which has as input variables the desired vibration intensity 81 and the measured value of the pressure sensor 53, i.e. the pressure at the supply point. As an output variable, the characteristic map 80 provides the displacement volume to be set on the second hydraulic machine 31, with which the desired vibration intensity 81 is achieved at the current pressure at the supply point.
  • the characteristic map 80 preferably comprises a corresponding value table, from which intermediate values are most preferably obtained by interpolation. This pilot control does not take into account, for example, that Changing ambient temperatures also affect the required setting of the second hydraulic machine 31. This problem is counteracted by the second control circuit 70.
  • the output variables of the characteristic map 80 and the second controller 74 are added, resulting in the control signal 14 for the second hydraulic machine 31. This is also referred to as a superposition of a feedforward control with a closed-loop control.
  • Fig. 4 shows an alternative connection of the second hydraulic machine 31 with the supply point 50 and the tank 12. In the embodiment according to Fig. 2 These connections were permanently open.
  • the embodiment according to Fig. 4 is intended for cases in which the direction of rotation of the second hydraulic machine 31 is to be reversible, whereby in order to save costs no hydraulic machine adjustable beyond the displacement volume zero is to be used.
  • the second hydraulic machine 31 is therefore connected to a switching valve 34, which is designed as a 4/3-way valve.
  • the switching valve 43 thus has four connections and three switching positions. These switching positions are discrete switching positions, with essentially no intermediate positions in which the opening cross-sections of the various connections change continuously.
  • the middle position is a locked position in which the respective second hydraulic machine 31 cannot move because it is hydraulically clamped.
  • the connections to the tank 12 and the supply point 50 are blocked.
  • the second hydraulic machine rotates clockwise, for example, whereby it is in the Fig. 4 right position of the switching valve 34 rotates counterclockwise.
  • the displacement volume is preferably set to zero or almost zero on the second hydraulic machine 31, while the switching valve 34 is adjusted.
  • the connections between the second hydraulic motor 31 and the tank 12 or the supply point 50 are thus continuously released.
  • a continuous adjustment of the corresponding opening cross-sections preferably does not take place, while the vibration unit (No. 30 in Fig. 1 ) running.
  • the first hydro machine (No. 21 in Fig. 2 ) can be connected in an analogous manner to the supply point 50 and the tank 12 using an analog switching valve.

Landscapes

  • Engineering & Computer Science (AREA)
  • Architecture (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Road Paving Machines (AREA)

Claims (13)

  1. Véhicule de compactage (10) avec au moins un rouleau (20) pour le compactage dynamique d'un sol (11), le véhicule de compactage (10) étant en liaison d'entraînement de déplacement avec au moins une première machine hydraulique (21), une unité vibrante (30) étant associée à au moins un rouleau (20), laquelle est en liaison d'entraînement avec une deuxième machine hydraulique (31) associée, caractérisé en ce que l'au moins une première, l'au moins une deuxième et une troisième machine hydraulique (21 ; 31 ; 41) sont respectivement raccordées, côté haute pression, à un point d'alimentation commun (50) et, côté basse pression, à un réservoir (12), de telle sorte qu'elles forment un circuit hydraulique ouvert, ladite liaison au point d'alimentation pouvant être respectivement libérée en permanence de telle sorte qu'une haute pression dans l'au moins une première, dans l'au moins une deuxième et dans la troisième machine hydraulique (21 ; 31 ; 41) est essentiellement égale à la pression au niveau du point d'alimentation (50), l'au moins une première, l'au moins une deuxième et la troisième machine hydraulique (21 ; 31 ; 41) ayant chacune un volume de refoulement réglable, un volume de refoulement de l'au moins une deuxième machine hydraulique (31) étant ajustable de manière à obtenir l'intensité de vibration souhaitée (81) tandis que lesdites liaisons au point d'alimentation (50) sont libérées.
  2. Véhicule de compactage (10) selon la revendication 1, dans lequel un volume de refoulement de l'au moins une première machine hydraulique (21) est ajustable de manière à obtenir la vitesse de déplacement souhaitée, de telle sorte que la vitesse de déplacement et l'intensité de vibration souhaitées peuvent être obtenues simultanément.
  3. Véhicule de compactage (10) selon la revendication 1 ou 2, dans lequel une direction de rotation de l'au moins une première machine hydraulique (21) peut être inversée par réglage du volume de refoulement concerné, la direction d'écoulement de la première machine hydraulique (21) concernée restant respectivement constant.
  4. Véhicule de compactage (10) selon l'une quelconque des revendications précédentes, dans lequel le point d'alimentation (50) est raccordé à un accumulateur hydraulique (51).
  5. Véhicule de compactage (10) selon l'une quelconque des revendications précédentes, dans lequel il est prévu deux ou plus de deux rouleaux (20) qui sont chacun en liaison d'entraînement en rotation avec leur propre première machine hydraulique (21), toutes les premières et toutes les deuxièmes machines hydrauliques (21 ; 31) étant raccordées au même point d'alimentation (50) et au même réservoir (12).
  6. Véhicule de compactage (10) selon l'une quelconque des revendications précédentes, dans lequel le point d'alimentation (50) est raccordé à un capteur de pression (53), dans lequel le volume de refoulement d'au moins une deuxième machine hydraulique (31) est ajustable en fonction de la pression mesurée avec le capteur de pression (53) et en fonction de l'intensité de vibration souhaitée (81).
  7. Véhicule de compactage (10) selon l'une quelconque des revendications précédentes, dans lequel le point d'alimentation (50) est raccordé à un capteur de pression (53), dans lequel le volume de refoulement de la troisième machine hydraulique (41) est ajustable en fonction de la pression mesurée avec le capteur de pression (53).
  8. Véhicule de compactage (10) selon la revendication 7, dans lequel il est prévu un premier circuit de régulation (60) dont la grandeur réelle (61) est la pression mesurée avec le capteur de pression (53), dans lequel sa grandeur de réglage (62) est le volume de refoulement de la troisième machine hydraulique (41).
  9. Véhicule de compactage (10) selon la revendication 8, dans lequel un deuxième capteur de vitesse de rotation (32) est associé à au moins une deuxième machine hydraulique (31), au moyen duquel une vitesse de rotation de la deuxième machine hydraulique (31) concernée peut être mesurée, dans lequel il est prévu un deuxième circuit de régulation (70) dont la grandeur réelle (71) est une valeur de mesure du deuxième capteur de vitesse de rotation (32), dans lequel sa grandeur de réglage (72) est le volume de refoulement de la deuxième machine hydraulique (31) concernée.
  10. Véhicule de compactage (10) selon l'une quelconque des revendications précédentes, dans lequel le point d'alimentation (50) est formé par une conduite (54) qui s'étend sur au moins 50 % de la longueur du véhicule de compactage (10) dans la direction de déplacement (15).
  11. Véhicule de compactage (10) selon l'une quelconque des revendications précédentes, dans lequel l'au moins une première machine hydraulique (21), l'au moins une deuxième machine hydraulique (31) et/ou la troisième machine hydraulique (41) comprennent chacune un dispositif de réglage (13) qui est adapté pour ajuster le volume de refoulement de la machine hydraulique concernée (21 ; 31 ; 41) essentiellement proportionnellement à un signal de réglage (14).
  12. Véhicule de compactage (10) selon l'une quelconque des revendications précédentes, dans lequel un troisième circuit de régulation est associé à au moins une première machine hydraulique (21), dont la grandeur réelle est la vitesse de rotation de la première machine hydraulique (21) concernée, dans lequel sa grandeur de réglage est le volume de refoulement de la première machine hydraulique (21) concernée.
  13. Procédé, dans lequel un véhicule de compactage (10) selon la revendication 8 est utilisé, dans lequel une grandeur de consigne (63) du premier circuit de régulation (60) est choisie en fonction de la vitesse de déplacement souhaitée du véhicule de compactage (10) et/ou en fonction de l'intensité de vibration souhaitée (81).
EP22700286.2A 2021-01-14 2022-01-05 Véhicule de compactage dans lequel un système d'entraînement et une unité de vibration sont alimentés en fluide sous pression par un point d'alimentation commun Active EP4278044B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102021200285.4A DE102021200285A1 (de) 2021-01-14 2021-01-14 Verdichtungsfahrzeug, bei welchem ein Fahrantrieb und eine Vibrationseinheit von einer gemeinsamen Versorgungstelle her mit Druckfluid versorgt werden
PCT/EP2022/050103 WO2022152596A1 (fr) 2021-01-14 2022-01-05 Véhicule de compactage dans lequel un système d'entraînement et une unité de vibration sont alimentés en fluide sous pression par un point d'alimentation commun

Publications (2)

Publication Number Publication Date
EP4278044A1 EP4278044A1 (fr) 2023-11-22
EP4278044B1 true EP4278044B1 (fr) 2025-05-21

Family

ID=79731040

Family Applications (1)

Application Number Title Priority Date Filing Date
EP22700286.2A Active EP4278044B1 (fr) 2021-01-14 2022-01-05 Véhicule de compactage dans lequel un système d'entraînement et une unité de vibration sont alimentés en fluide sous pression par un point d'alimentation commun

Country Status (3)

Country Link
EP (1) EP4278044B1 (fr)
DE (1) DE102021200285A1 (fr)
WO (1) WO2022152596A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102022209497B4 (de) 2022-09-12 2025-10-30 Robert Bosch Gesellschaft mit beschränkter Haftung Verfahren zur Steuerung eines hydrostatischen Antriebs

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10210049B4 (de) 2002-03-07 2004-03-25 Abg Allgemeine Baumaschinen-Gesellschaft Mbh Verdichtungswalze
US8374766B2 (en) * 2007-11-29 2013-02-12 Caterpillar Paving Products Inc. Power management system for compaction vehicles and method
US20110158745A1 (en) 2009-12-31 2011-06-30 Caterpillar Paving Products Inc. Vibratory system for a compactor
DE102010006993A1 (de) * 2010-02-05 2011-08-11 Robert Bosch GmbH, 70469 Vibrationsantrieb
DE102013227007B4 (de) * 2013-12-20 2024-05-16 Hamm Ag Selbstfahrende Baumaschine, insbesondere Bodenverdichter
US20170121917A1 (en) * 2015-10-30 2017-05-04 Caterpillar Paving Products Inc. Compaction System and Method for Determining Roller Decoupling
WO2018224135A1 (fr) 2017-06-07 2018-12-13 Volvo Construction Equipment Ab Système hydraulique destiné à une machine de chantier
JP6749351B2 (ja) * 2018-01-19 2020-09-02 酒井重工業株式会社 建設車両

Also Published As

Publication number Publication date
EP4278044A1 (fr) 2023-11-22
WO2022152596A1 (fr) 2022-07-21
DE102021200285A1 (de) 2022-07-14

Similar Documents

Publication Publication Date Title
DE2733870C2 (fr)
EP2531305B1 (fr) Système destiné à produire des vibrations
DE2352739C2 (fr)
DE3202015C2 (de) Hydraulisches Antriebssystem
DE202007011783U1 (de) Hydraulikantrieb insbesondere eines Baggers insbesondere für ein Drehwerk
EP3748168B1 (fr) Système d'entraînement hydraulique à deux pompes et à récupération d'énergie
EP3077674B1 (fr) Système hydraulique
DE1450778B1 (de) Stellgerät für die Übersetzungseinstellung eines hydrostatischen Getriebes
DE2342450A1 (de) Anordnung zum steuern von hydrostatischen getrieben
EP1656224B1 (fr) Systeme pour commander le processus d'etirage dans une presse de transfert
EP4278044B1 (fr) Véhicule de compactage dans lequel un système d'entraînement et une unité de vibration sont alimentés en fluide sous pression par un point d'alimentation commun
DE102018211586A1 (de) Radantriebsanordnung für einen hydrostatischen Fahrantrieb und hydrostatischer Fahrantrieb
EP0719947B1 (fr) Circuit de détection de charge
DE3806194A1 (de) Automotive antriebseinrichtung fuer maschinen und fahrzeuge
DE19804374B4 (de) Axialkolbenmaschine mit Mitteldrucköffnung
DE4416723A1 (de) Antriebssystem für einen hydraulischen Verbraucher, insbesondere einen Arbeitszylinder
DE102022209497B4 (de) Verfahren zur Steuerung eines hydrostatischen Antriebs
EP0229330B1 (fr) Mécanisme pivotant entraîné par deux cylindres séparés à bielle-manivelle
DE2303014C3 (de) Kombinierte Steuereinrichtung für ein hydrostatisches Getriebe und eine dieses antreibende Brennkraftmaschine, insbesondere eines Kraftfahrzeuges
DE2403110A1 (de) Steuervorrichtung fuer einen vibrator
DE102007049413B3 (de) Anordnung zur Veränderung des Volumenstroms einer Verdrängermaschine
DE69805157T2 (de) Lenkung für ein fahrzeug mit knickrahmen
DE3146540C2 (fr)
DE1550929B1 (de) Hydrostatisches getriebe fuer lasten grosser traegheit
DE4140860C2 (de) Steuereinrichtung für ein hydrostatisches Getriebe

Legal Events

Date Code Title Description
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: UNKNOWN

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE INTERNATIONAL PUBLICATION HAS BEEN MADE

PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20230814

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

DAV Request for validation of the european patent (deleted)
DAX Request for extension of the european patent (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTG Intention to grant announced

Effective date: 20250306

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502022004031

Country of ref document: DE

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20250521

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20250521

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20250922

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20250521

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG9D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20250822

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20250821

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20250521

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20250521

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20250521

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20250521

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20250821

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20250921

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20250521