EP1600643B1 - Dispositif de commande pour un système de manutention hydraulique, en particulier un bras pivotant d'un sytème de levage de benne amovible de camion - Google Patents

Dispositif de commande pour un système de manutention hydraulique, en particulier un bras pivotant d'un sytème de levage de benne amovible de camion Download PDF

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Publication number
EP1600643B1
EP1600643B1 EP05011364A EP05011364A EP1600643B1 EP 1600643 B1 EP1600643 B1 EP 1600643B1 EP 05011364 A EP05011364 A EP 05011364A EP 05011364 A EP05011364 A EP 05011364A EP 1600643 B1 EP1600643 B1 EP 1600643B1
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EP
European Patent Office
Prior art keywords
cylinder
hydraulic
load moving
moving device
rapid
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
EP05011364A
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German (de)
English (en)
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EP1600643A1 (fr
Inventor
Michael Eicheldinger
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Franz Xaver Meiller Fahrzeug und Maschinenfabbrik GmbH and Co KG
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Franz Xaver Meiller Fahrzeug und Maschinenfabbrik GmbH and Co KG
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Publication of EP1600643A1 publication Critical patent/EP1600643A1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/024—Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F15B2211/3051—Cross-check valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
    • F15B2211/3058—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve having additional valves for interconnecting the fluid chambers of a double-acting actuator, e.g. for regeneration mode or for floating mode
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
    • F15B2211/3157—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line
    • F15B2211/31588—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line having a single pressure source and multiple output members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/327—Directional control characterised by the type of actuation electrically or electronically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40507—Flow control characterised by the type of flow control means or valve with constant throttles or orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41581—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F15B2211/7114—Multiple output members, e.g. multiple hydraulic motors or cylinders with direct connection between the chambers of different actuators
    • F15B2211/7128—Multiple output members, e.g. multiple hydraulic motors or cylinders with direct connection between the chambers of different actuators the chambers being connected in parallel

Definitions

  • the invention relates to a hydraulic drive device of a load movement device, in particular a Schwenkarman extract as a lifting device for swap bodies on a load transport vehicle, wherein the hydraulic drive means comprises at least one control device for controlling the same and two hydraulic cylinders, under control by the control device from a pressurized fluid source with hydraulic fluid under pressure be powered to drive the load moving device, wherein the load moving device is different from its normal mode operable in a rapid traverse mode.
  • the invention relates to a drive device according to the preamble of claim 1.
  • Hydraulically driven load-moving devices in the form of swivel arms can be found, for example, in so-called roll-off tipper vehicles (cf., for example, DE 33 32 275 A1, DE 29 03 462 C2 and DE 196 37 891 A1).
  • roll-off tipper vehicles of conventional design have a pivotable load lifting arm provided in the vehicle longitudinal center, which is pivotable about a horizontal pivot axis extending transversely to the vehicle longitudinal direction between a first pivot position and a second pivot position and has a hook arm with a hook provided thereon at its end remote from the pivot axis. which is to be engaged with a complementary eye of a swap body.
  • the swap body In a normal driving position, the swap body is supported on the vehicle body or a base frame, wherein the load lifting arm is substantially horizontal and the hook arm from the load lifting arm extends vertically upwards to the eye of the interchangeable container. Should now such a swap body from the vehicle be unloaded, this is achieved in that the load lifting arm is pivoted from its first pivotal position about its pivot axis and about an approximately upright dead center into a second pivot position. In such a pivoting operation of the swap body to roles that are located at the rear of the vehicle, unroll and gradually remove further from the vehicle body until the swap body has been completely discontinued on the ground behind the rear of the vehicle.
  • swivel drive means for the load-lifting arm two double-acting hydraulic cylinders are normally provided on hook loader vehicles.
  • the hydraulic cylinders are articulated with their opposite ends on the one hand on a frame-fixed structure of the vehicle - and on the other hand on the pivotable load lifting arm, wherein they are arranged substantially parallel to each other and mechanically coupled to synchronous operation.
  • the pivoting of the load lifting arm is carried out by extending or retracting the piston rods of the hydraulic cylinder, for which purpose the double-acting cylinder are acted upon by hydraulic fluid from a hydraulic pump.
  • the hydraulic pump is connected to the cylinders via a hydraulic line system with load-holding valves, etc. inside. Return lines with counter-holding valves located therein serve to return hydraulic fluid displaced from the cylinders to a tank.
  • pivotable lifting arms can be operated in skip vehicles and dump trucks in rapid traverse mode.
  • the rapid traverse mode which is usually to be selected over a limited pivot angle range
  • the load lifting arm arrangement can be pivoted at a higher speed than is the case in a normal operating mode.
  • the rapid traverse mode is usually permitted only in the case of low load on the lifting arms. If a container loaded with a heavy load is to be unloaded from the vehicle or charged onto the vehicle by means of a relevant load lifting arm, this will take place in the normal operating mode.
  • the pivoting of the lifting arm without container or with an unloaded Container can be carried out in contrast in rapid traverse mode.
  • the rapid traverse operating mode is characterized in that the cylinder subspaces of each of the two drive cylinders of each of the two drive cylinders are virtually short-circuited during extension of the piston rod, so that pressurized fluid from the cylinder passing through the piston rod Partial space with a correspondingly high pressure via a rapid traverse connection line to the other cylinder subspace, which is exposed in rapid traverse operation of the instantaneous pressurization by the pump, is led to accelerate the extension of the piston rod.
  • differential pressure monitoring means are provided for detecting the difference occurring between the pressure in the first cylinder subspace and the pressure in the second cylinder subspace of the hydraulic cylinder during extension of the piston rod, wherein the control means a Rapid traverse valve assembly controls depending on the pressure difference, to ensure that the rapid traverse mode is suppressed when the load lifting arm, for example is loaded by a heavy container.
  • a hydraulic drive device is known from DE-A-1 556 720.
  • the known drive means controls a multi-purpose bucket loader using two hydraulic cylinders acting in parallel on a drive shaft and operating under control of a control means.
  • To set a rapid traverse mode of the multi-purpose bucket loader at low load of the cylinder is provided to supply only one of the two cylinders with the hydraulic fluid, while the other cylinder is separated from the source of pressurized fluid.
  • the second cylinder is switched on again, so that in case of load both cylinders operate in parallel.
  • Another hydraulic drive device is described in JP 57 072 600 A and comprises two cylinders connected in parallel to one another, which engage a lifting device of a forklift truck.
  • a control device is provided with a plurality of hydraulic valves for controlling the hydraulic fluid flow to the cylinders.
  • the known control device is set up so that only one of the two cylinders is supplied with pressure, while the second cylinder is forcibly moved by the mechanical coupling of the two cylinders.
  • a pressure relief valve switches the second cylinder also, so that in the case of load, the lifting device can be driven by both cylinders simultaneously.
  • JP 63 247 430 describes a further hydraulic drive device in which two hydraulic cylinders are supplied with hydraulic fluid from a pressure fluid source under the control of a control device.
  • the control device of this drive device is switchable between a first switching state, in which both cylinders are connected in parallel and supplied with hydraulic fluid, and a second switching state, in which only one hydraulic cylinder is operated, wherein the switching between these operating states based on the switching state of Sensor switch takes place.
  • the invention has for its object to provide a drive device of the type mentioned, which can be realized in a simple manner, which is a reliable operation of the load moving device both in the normal mode and in the rapid traverse mode and which enables efficient drive of the load movement device even in the rapid traverse mode.
  • a drive device with the features of claim 1 is provided.
  • Such a drive device is adapted to reduce the hydraulic flow from the pressure fluid source to a first of the two cylinders or, if necessary, to block to adjust the rapid traverse mode of the load movement device to increase the hydraulic flow from the pressure fluid source to the other cylinder.
  • the first cylinder is hydraulically decoupled from the source of pressurized fluid when the rapid traverse mode is set.
  • a pressurized fluid source e.g. a simple single-circuit pump may be used, e.g. Pumping oil as hydraulic fluid from a tank.
  • the hydraulic decoupling of the first cylinder thus funded by the pump oil for the application of the other hydraulic cylinder is available, so that the piston rod can be extended or retracted for a given pump power significantly faster than is the case in the normal mode.
  • the control device ensures that in the rapid traverse mode, the two cylinder subspaces of the first cylinder are hydraulically shorted by releasing a bypass line, so that displaced from the cylinder subspace displaced oil in the direction of the other cylinder subspace can flow. In this way, it should be ensured that the cylinder subspaces are always filled with oil.
  • the bypass line may be connected via a return line and a throttle located therein or possibly a bias valve with a collecting tank for hydraulic fluid. Since the first hydraulic cylinder is mechanically coupled to synchronize with the other cylinder, the piston rod makes the first one Cylinder the faster movement of the piston rod of the other cylinder forcibly with.
  • the hydraulic cylinders are double-acting cylinders.
  • the control device may comprise a valve arrangement which in a normal mode of the load moving device associated with the first valve switching position, the cylinder subspaces of operated in rapid traverse mode with reduced or possibly stopped hydraulic fluid supply first cylinder with the main lines for the hydraulic fluid inlet and connects the hydraulic fluid return and which in a rapid traction mode associated second valve switching position separates the cylinder subspaces of the first cylinder from the main lines and connects to the common bypass line.
  • This valve arrangement may be e.g. to act two electrically, magnetically, hydraulically or pneumatically controllable directional control valves, in particular 3/2-way valves. With such a valve arrangement can be an existing, previously designed only for the normal mode hydraulic system of a load moving device with little equipment and low installation costs easily retrofitted, so that the system in question can then be operated in a rapid traverse mode.
  • Embodiments of the control device according to the invention enable rapid traverse operation in opposite directions of movement of the load movement device, So approximately in opposite pivot directions of a lifting arm.
  • the hydraulic cylinders are two mechanically-coupled to synchronous, double-acting hydraulic cylinders, each of which comprises a piston displaceably guided in the cylinder interior in question and dividing the cylinder interior into a first cylinder subspace and a second cylinder subspace wherein, for hydraulic loading of the pistons in the normal mode of the load moving device, hydraulic fluid under pressure from the source of pressurized fluid under control of the control means is to be commonly supplied to the first cylinder subspaces or the second cylinder subspaces of the hydraulic cylinders, respectively, while from the respective other cylinder subspaces of the pistons displaced hydraulic fluid is to be derived to a hydraulic fluid sink, wherein the control device is adapted to, in the rapid traverse mode, the hydraulic fluid-emitting cylinder subspace of the second cylinder with due to the Piston displacement enlarging and hydraulic fluid receiving cylinder subspace, the first cylinder to connect and restrict the hydraulic fluid from the hydraulic fluid dispensing cylinder subspace of the second cylinder to the hydraulic fluid sink
  • the pressure fluid source is also in the embodiment considered here, preferably a pump that provides oil from a tank as hydraulic fluid under pressure.
  • the invention is thus based on the concept, in rapid traverse operation, of discriminating the cylinders with regard to their supply of oil from the pump, so that the oil supply to the first cylinder is throttled and possibly blocked in comparison with the oil supply to the second cylinder.
  • An embodiment of the invention is characterized in that the The first cylinder is decoupled hydraulically from the pump in rapid traverse operation, while the second cylinder is supplied solely by the pump. Due to the supply of oil to the currently oil-absorbing cylinder subspace of the second cylinder of the piston located therein is acted upon hydraulically and thus shifted. The thereby displaced from the other cylinder subspace of the second cylinder oil passes in rapid traverse mode via a rapid traverse hydraulic line to the here due to the piston displacement in the first cylinder magnifying cylinder subspace of the first cylinder. The piston of the first cylinder displaces oil from the other cylinder compartment to the tank. It is thus transferred with respect to the hydraulic circuit and supply of the cylinder in the transition from the normal mode to rapid traverse mode of a hydraulic parallel connection to a hydraulic series connection of the cylinder and vice versa.
  • the cylinders in the embodiment considered here are also “hydraulically coupled" in rapid traverse operation.
  • a variant of the invention can be realized in which the ratio of the quantities of oil fed directly from the hydraulic fluid source to the cylinders can be varied continuously or in steps, so that the expressive effect can also be variable in a corresponding manner.
  • the setting of the ratio of the oil supply to the first cylinder and the oil supply to the second cylinder may also be automatically adjustable in dependence on the load state of the load movement device by means of the control device, so that an automatic variable rapid traverse operation is possible.
  • Such a possibility of automatic variable rapid traverse operation is feasible in all basic variants of the present invention.
  • the rapid traverse mode on the piston stroke of the common retraction of the Pistons is limited in the cylinder, it being assumed that the pistons have a respective, the second cylinder subspace of the respective cylinder passing through the piston rod, which is retractable depending on the direction of the piston stroke from the cylinder or retractable into the cylinder.
  • the second cylinder subspace of the first cylinder penetrated by the piston rod is thus hydraulically connected downstream of the cylinder subspace of the second cylinder in the series connection, so that the oil quantity displaced from the first cylinder subspace of the second cylinder is greater than the amount of oil that can accommodate the first cylinder simultaneously in its second cylinder subspace. There is thus always enough oil for the supply of the first cylinder from the second cylinder in rapid traverse operation available.
  • a pressure valve connected to the rapid traverse hydraulic line is preferably provided which, when a limit pressure in the rapid traverse hydraulic line is exceeded, opens to the pressure fluid sink, ie to the tank.
  • the rapid traverse mode is adjustable by means of a manually operated adjusting device of the control device. It is thus the choice of an operator It is up to you if you want to use rapid traverse or normal operation. In this case, however, safety devices can be provided which suppress the rapid traverse operation, for example, because an excessive load on the load moving device is given.
  • control device is set up to automatically set or suppress the rapid traverse mode as a function of the load state of the load movement device.
  • the already mentioned aspect of the automatic variable rapid traverse operation is pointed out.
  • control device can be equipped with pressure monitoring means, in particular differential pressure monitoring means for detecting the pressure, in particular the pressure difference, in the cylinder subspaces of at least one cylinder, in particular of the second cylinder - and be adapted to release the rapid traverse mode depending on the measured pressure or disable.
  • pressure monitoring means in particular differential pressure monitoring means for detecting the pressure, in particular the pressure difference, in the cylinder subspaces of at least one cylinder, in particular of the second cylinder - and be adapted to release the rapid traverse mode depending on the measured pressure or disable.
  • pressure monitoring means in particular differential pressure monitoring means for detecting the pressure, in particular the pressure difference, in the cylinder subspaces of at least one cylinder, in particular of the second cylinder - and be adapted to release the rapid traverse mode depending on the measured pressure or disable.
  • the control device is equipped with means for detecting positions of the load movement device and adapted to enable or disable the rapid traverse mode depending on the achievement of predetermined positions of the load movement device during its movement.
  • the rapid traverse mode can be limited to a limited angular range around a dead center position of the lifting arm.
  • the load moving device is a swivel arm assembly as a reciprocating swap body on a load transport vehicle, such as a swiveling load lifting arm of a container changing device of a hook lift truck or a pair of mechanically coupled swivel arms of a container changing device Dump truck is trading.
  • the invention is in this sense, a load transport vehicle, in particular Abrollkipper poverty or Absetzkipperjan, with a changing device for swap bodies, which has a Schwenkarman extract as a lifting device for the swap body and a hydraulic drive means for the Schwenkarman nie, wherein the hydraulic drive means are two mechanically coupled to each other for synchronization hydraulic Cylinder comprises.
  • a control device for controlling the hydraulic drive device, a control device according to one of the claims is provided.
  • the change device 2 illustrated in FIGS. 1-5 comprises a base frame 1 comprising longitudinal members 4 and transverse struts 6.
  • the pivot arm 10 provided between the longitudinal members 4 extends forwardly from the rearward tilting axis 12 transverse to the vehicle longitudinal direction in the basic position shown in FIG and has at its end remote from the tilting axis 12 an orthogonal upwardly angled hook arm 14 with a hook 16 for engaging a complementary loop 18 of a container 20 (see Figures 3a-3c).
  • the swivel arm 10 has a tilting-arm-proximate swivel-arm section 10a and a second swivel-arm section 10b pivotally mounted at the end remote from the tilting axis 12 about a buckling axis 22 parallel to the tilting axis 12.
  • FIGS. 3a-3c a container 20 accommodated on the vehicle 3 on the base frame of the changing device 2 can be lowered from the vehicle by pivoting the second pivot arm section 10b about the articulated axis 22.
  • the second pivot arm section 10b passes from the basic position shown in FIG. 1 into the boom position shown in FIG. The container rolls when settling on the rollers 24 of the changing device with his container skids 26 from.
  • FIGS. 3a-3c For receiving a standing behind the rear of a vehicle 3 container 20, the movements shown in FIGS. 3a-3c can be reversed.
  • the two swivel arm sections 10a and 10b are rigidly locked together so that the buckling option of the swivel arm 10 used for depositing and picking up a container is suppressed.
  • the container 20 can thus be brought to the vehicle 3 in a tilted position shown in FIG. 5.
  • two hydraulic cylinders 28a, 28b serve as drive means, with their piston rod ends 30 on the second pivot arm portion 10b are articulated.
  • the two hydraulic cylinders 28a, 28b extend in the example parallel between the longitudinal members 4 of the base frame 1 and are hinged with their cylinder housing ends 32 on the base frame 1.
  • the cylinders 28a and 28b are preferably the same type. They are mechanically coupled to the synchronization via the base frame 1 and the second pivot arm section 10b.
  • FIG. 6 shows a hydraulic circuit diagram for a control device 34 according to an illustrative example not designed according to the invention for the hydraulic control of the drive cylinders 28a, 28b.
  • the by their pistons 36a, 36b in two cylinder subspaces 38a, 40a; 38b, 40b are divided at the hydraulic connection points 42a, 42b, 44a, 44b with branch lines 46a, 46b, 48a, 48b of hydraulic main lines 46, 48 for the hydraulic fluid inlet and the hydraulic fluid return.
  • load holding valves with check function and counter-holding valves are provided, which are represented in Fig. 6 by the block 50.
  • a directional control valve 52 can be actuated by means of an adjusting device (proportional generator) by the driver of the unrolling vehicle.
  • an adjusting device proportional generator
  • the main line 48 In a first switching position of the directional control valve 52, the main line 48 to the pressure line 54, whereas the main line 46 is connected to the return line 56.
  • the hydraulic main line 46 In a second switching position of the directional control valve 52, the hydraulic main line 46 is connected to the pressure line 54, whereas the main line 48 is connected to the return line 56.
  • the main lines 46 and 48 are separated from the lines 54, 56.
  • the pressure line 54 is connected to a one-circuit pump 55, which is driven by a power take-off of the vehicle and from a hydraulic tank 57 oil promotes.
  • the return line 56 is connected to the hydraulic tank.
  • the directional control valve 52 is in to adjust the first switching position, so that the main line 48 is connected to the pressure line 54 and the main line 46 is connected to the return line 56.
  • the pump may then deliver oil under pressure to the cylinder subspaces 38a, 38b to urge the pistons 36a, 36b.
  • the directional control valve 52 is to be transferred to the second switching position.
  • control device 34 has referred to the normal mode of the swing arm 10, which is then to choose when a heavy container is coupled to the pivot arm 10 and is to be handled with the changing device.
  • the rapid traverse option is very simple in the described control device Means feasible, as can be seen from the example in Fig. 6.
  • the valves 62, 64 connect the ports 42b, 44b via a bridging line 66 with each other.
  • the two cylinder subspaces 38b, 40b are then decoupled from the main lines 46, 48.
  • the amount of oil delivered by the pump is then essentially exclusively available for the operation of the other hydraulic cylinder 28a, so that its piston rod 60a can be extended or retracted faster for a given pumping power than is the case in the normal operating mode. Since the cylinders 28a and 28b are mechanically coupled for synchronism, the piston rod 60b of the hydraulically shorted cylinder 28b decoupled from the pump 55 forcibly communicates the movement of the piston rod 60a of the cylinder 28a.
  • the bypass line 66 is connected in the example of FIG. 6 via a return branch 68 to the return line 56 and thus to the tank.
  • a return branch 68 is a throttle valve or possibly biasing valve 70th
  • the rapid traverse valves 62, 64 may be electromagnetically actuated valves, which can be manually activated by means of an adjusting device. In alternative embodiments, it may be provided that respective rapid traverse valves are hydraulically or pneumatically vor Kunststoffbar.
  • control device 34 may comprise means which are adapted to release the rapid traverse mode automatically depending on the load state of the pivot arm 10 and to suppress.
  • Fig. 7 shows a hydraulic circuit diagram for an embodiment of the invention. Elements in FIG. 7 which correspond objectively or functionally to elements in FIG. 6 are identified by corresponding reference numerals, but those in FIG. 7 are preceded by 1. Therefore, to explain the exemplary embodiment according to FIG 6, so that the following explanations can be limited essentially to the differences of the embodiment according to FIG. 7 to the illustration example according to FIG. 6. These differences relate in particular to the valve arrangement for switching between normal operation and rapid traverse operation of the load movement device. It should also be noted that in Fig. 7, the first cylinder 128 b on the left side - and the second cylinder 128 a are shown on the right side of the drawing. In Fig. 6, it is reversed.
  • the directional control valve 152 is set in the switching position in which the main line 148 is connected to the pressure line 154 and the main line 146 with the return line 156th is connected.
  • the pump 155 may then deliver oil under pressure to the cylinder subspaces 138a, 138b to hydraulically pressurize the pistons 136a, 136b in the first cylinder subspaces 138a, 138b.
  • the directional control valve 152 is to be transferred to the other active switching position, so that the pressure line 154 is connected to the main line 146 and the return line 156 communicates with the main line 148.
  • Whether the retraction of the piston rods 160a, 160b takes place in the normal mode or in the rapid traverse mode depends on the respective setting the controllable by means of the control valve assembly from the directional control valves 80, 82 and 84 from. If the piston rods 160a, 160b in the normal mode and thus are usually drawn slowly and under external load, the valves 80, 82 are switched from the normal switching position shown in the alternative switching position, so that via the main line 146 oil both to the line branch 146a can also pass to the line branch 146b and thus parallel to the second cylinder subspaces 140a, 140b of the cylinders 128a, 128b and on the other hand, the branch lines 148a, 148b are connected via the main line 148 to the return line 156, so that oil from the first cylinder Subspaces 138a, 138b can be removed from the main line 148a to the return line 156.
  • the valves 80 and 82 should be left in the normal position shown, whereas, however, the directional control valve 84 moves out of the illustrated normal position into the alternative shift position is to switch.
  • the directional control valve 84 is in a rapid traverse hydraulic line 86 which is connected between the valve 82 and the second cylinder 128a at the port 144a of the first cylinder subspace 138a at 88.
  • the other connection point 90 of the rapid traverse hydraulic line is located in a connection line 92 between the ports 142b and 144b of the first cylinder 128b.
  • connection line 92 a non-return valve 94 which opens in the direction of the connection 142b is also provided between the connection point 90 and the cylinder connection 142b.
  • a pressure valve 96 is further provided between the connection point 90 and the cylinder port 144b and the main line 148, which opens when exceeding a limit pressure in the rapid traverse hydraulic line to the main line 148 and thus in rapid traverse operation to the tank 157 out.
  • the second cylinder subspace 140a of the second cylinder 128a becomes oil from the pump 155 via the main line 146 supplied so that the piston 160a is shifted in Fig. 7 in the downward direction.
  • the thereby shrinking cylinder subspace 138a of the cylinder 128a are from the piston 136a displaced oil to the rapid traverse hydraulic line 86 from.
  • the oil may then pass through the open valves 84 and 94 to the second cylinder subspace 140b of the cylinder 128b to urge the piston 136b displaceable therein.
  • the piston 136b is thus displaced not only due to the mechanical synchronism coupling of the piston rods 160a and 160b of the preferably identically constructed cylinders 128a and 128b but also due to the hydraulic loading in the hydraulic series connection of the cylinders 128a and 128b set in rapid traverse operation.
  • the oil displaced from the first cylinder subspace 138b by the piston 136b can flow out to the tank via the main line 148.
  • the pressure valve 96 ensures that excess oil is discharged directly into the main conduit 148 toward the tank 157.
  • an important aspect of the invention is also the feasible in other variants possibility of possibly stepwise, but preferably continuous setting of the ratio of the cylinders of the pump supplied oil quantities.
  • the second cylinder 28a, 128a in rapid traverse operation is usually supplied with a larger amount of oil directly from the pump than the first cylinder 28b, 128b; however, the first cylinder is not completely disconnected from the pump.
  • the larger the ratio between the amount of oil supplied directly from the pump to the second cylinder and the amount of oil supplied directly from the pump to the first cylinder the more effective (faster) is the rapid traverse operation.
  • the smaller this ratio the slower the pistons of the cylinders move, but the system allows for a heavier load on the load moving device.
  • This load can be monitored with the already mentioned detection means or possibly other detection means and used as a parameter for the control of the hydraulic drive means.
  • This load can be monitored with the already mentioned detection means or possibly other detection means and used as a parameter for the control of the hydraulic drive means.
  • variable rapid traverse operation also on the basis of manual settings, ie, for example, by adjusting an actuator from an operator.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Motor Power Transmission Devices (AREA)
  • Arrangement And Mounting Of Devices That Control Transmission Of Motive Force (AREA)

Claims (14)

  1. Dispositif d'entraînement hydraulique d'un appareil (10) de manutention de charges, en particulier d'un système de bras pivotants (10) servant de dispositif de levage pour des bennes amovibles (20) sur un véhicule (3) de transport de charges, le dispositif d'entraînement hydraulique présentant un dispositif de commande pour commander le dispositif d'entraînement hydraulique et au moins deux vérins hydrauliques (28a, 28b ; 128a, 128b) qui, sous le contrôle du dispositif de commande (34 ; 134) doivent être alimentés en fluide hydraulique sous pression depuis une source (55 ; 155) de fluide sous pression, afin d'entraîner l'appareil (10) de manutention de charges; l'appareil (10) de manutention de charges pouvant être entraîné, à la différence de son mode de fonctionnement normal, dans un mode de fonctionnement rapide,
    dans lequel, afin d'instaurer le mode de fonctionnement rapide, le dispositif de commande (34 ; 134) est conçu pour réduire ou éventuellement bloquer l'arrivée de fluide hydraulique depuis la source (55 ; 155) de fluide sous pression en direction d'un premier (28b; 128b) des deux vérins (28a, 28b ; 128a, 128b), dans le but d'augmenter l'arrivée de fluide hydraulique depuis la source (55 ; 155) de fluide sous pression en direction de l'autre vérin (28a ; 128a),
    dans lequel les deux vérins hydrauliques (128a, 128b) sont des vérins hydrauliques (128a, 128b) double effet, couplés mécaniquement pour être un mouvement synchronisé, dont chacun comprend un piston (136a, 136b) guidé de manière mobile dans l'intérieur de vérin concerné et divisant l'intérieur de vérin en une première chambre de vérin (138a, 138b) et une deuxième chambre de vérin (140a, 140b), dans lequel, pour solliciter hydrauliquement le piston (136a, 136b) dans le mode de fonctionnement normal de l'appareil de manutention de charges, du fluide hydraulique doit être introduit sous pression depuis la source (155) de fluide sous pression sous le contrôle du dispositif de commande à chaque fois en commun en direction des premières chambres de vérin (138a, 138b) et des deuxièmes chambres de vérin (140a, 140b) des vérins hydrauliques (128a, 128b), tandis que le fluide hydraulique repoussé par le piston hors de l'autre chambre de vérin respective (140a, 140b, resp. 138a, 138b) doit être évacué vers un collecteur (157) de fluide hydraulique,
    caractérisé en ce que
    le dispositif de commande est agencé pour, dans le mode de fonctionnement rapide, relier la chambre de vérin (138a) du deuxième vérin (128a) délivrant le fluide hydraulique à la chambre de vérin (140b) du premier vérin (128b), cette dernière s'agrandissant en raison du déplacement du piston et recevant du fluide hydraulique, et pour réduire ou éventuellement bloquer l'écoulement de fluide hydraulique depuis la chambre de vérin (138a) du deuxième vérin (128a) délivrant le fluide hydraulique vers le collecteur (157) de fluide hydraulique.
  2. Dispositif d'entraînement hydraulique d'un appareil de manutention de charges selon la revendication 1,
    dans lequel les pistons (136a, 136b) présentent une tige de piston respective (160a, 160b) traversant la deuxième chambre de vérin (140a, 140b) du vérin concerné, tige qui, selon la direction de déplacement du piston, peut être extraite du vérin (128a, 128b) ou rentrée dans le vérin,
    caractérisé en ce que le mode de fonctionnement rapide est limité à la course de piston correspondant à la rentrée commune des tiges de piston (160a, 160b) dans les vérins.
  3. Dispositif d'entraînement hydraulique d'un appareil de manutention de charges selon la revendication 2, caractérisé en ce que le dispositif de commande (134) comprend, dans un système de conduites hydrauliques, un système de vannes (80, 82, 84, 92, 96) qui, dans une position de vanne associée au mode de fonctionnement rapide,
    - relie la première chambre de vérin (138a) du deuxième vérin (128a) à la deuxième chambre de vérin (140b) du premier vérin (128b) par l'intermédiaire d'une conduite hydraulique de marche rapide (86),
    - relie la deuxième chambre de vérin (140a) du deuxième vérin (128a) à la source (155) de fluide sous pression, et
    - relie la première chambre de vérin (138b) du premier vérin (128b) au collecteur de fluide sous pression (157).
  4. Dispositif d'entraînement hydraulique d'un appareil de manutention de charges selon la revendication 3, caractérisé en ce que le système de vannes comprend un réducteur de pression (96) raccordée à la conduite hydraulique de marche rapide (86), réducteur qui s'ouvre en direction du collecteur de fluide sous pression en cas de dépassement d'une pression limite dans la conduite hydraulique de marche rapide.
  5. Dispositif d'entraînement hydraulique d'un appareil de manutention de charges selon l'une des revendications précédentes, caractérisé en ce que le dispositif de commande est adapté pour envoyer aux deux vérins (128a, 128b), dans le mode de fonctionnement rapide, du fluide hydraulique depuis la source de fluide sous pression (155), la quantité de fluide hydraulique envoyée au deuxième vérin (128a) étant plus grande que la quantité de fluide hydraulique envoyée au premier vérin (128b).
  6. Dispositif d'entraînement hydraulique d'un appareil de manutention de charges selon la revendication 5, caractérisé en ce que le rapport entre la quantité de fluide hydraulique envoyée au deuxième vérin (128a) et la quantité de fluide hydraulique envoyée au premier vérin (128b) dans le mode de fonctionnement rapide peut être modifié.
  7. Dispositif d'entraînement hydraulique d'un appareil de manutention de charges selon la revendication 6, caractérisé en ce que le rapport entre la quantité de fluide hydraulique envoyée au deuxième vérin (128a) et la quantité de fluide hydraulique envoyée au premier vérin (128b) peut être modifié en fonction de paramètres de service de l'appareil de manutention de charges, en particulier en fonction de l'état de charge de l'appareil de manutention de charges, sous le contrôle du dispositif de commande, en particulier de façon automatique.
  8. Dispositif d'entraînement hydraulique d'un appareil de manutention de charges selon l'une des revendications précédentes, caractérisé en ce que le mode de fonctionnement rapide peut être réglé au moyen d'un dispositif de réglage à actionnement manuel du dispositif de commande.
  9. Dispositif d'entraînement hydraulique d'un appareil de manutention de charges selon l'une des revendications précédentes, caractérisé en ce que le dispositif de commande est adapté pour régler le mode de fonctionnement rapide automatiquement en fonction de l'état de charge de l'appareil de manutention de charges.
  10. Dispositif d'entraînement hydraulique d'un appareil de manutention de charges selon l'une des revendications précédentes, caractérisé en ce que le dispositif de commande comprend des moyens de surveillance de pression, en particulier des moyens de surveillance de pression différentielle pour relever la pression, en particulier la différence de pression, dans les chambres de vérin d'au moins un vérin, en particulier du deuxième vérin, et adapté pour autoriser ou désactiver le mode de fonctionnement rapide en fonction de la pression mesurée.
  11. Dispositif d'entraînement hydraulique d'un appareil de manutention de charges selon l'une des revendications précédentes; caractérisé en ce que le dispositif de commande comprend des moyens pour relever des positions de l'appareil de manutention de charges et est adapté pour autoriser ou désactiver le mode de fonctionnement rapide en fonction du fait qu'on atteint des positions prédéterminées de l'appareil de manutention de charges pendant ses déplacements.
  12. Dispositif d'entraînement hydraulique d'un appareil de manutention de charges selon l'une des revendications précédentes, caractérisé en ce que l'appareil de manutention de charges est un bras pivotant (10) d'un dispositif (2) de changement de bennes d'un véhicule à benne amovible.
  13. Dispositif d'entraînement hydraulique d'un appareil de manutention de charges selon l'une des revendications précédentes, caractérisé en ce que l'appareil de manutention de charges est une paire de bras de pivotement, couplés mécaniquement pour un pivotement commun, d'un dispositif de changement de benne d'un véhicule multibenne.
  14. Véhicule de transport de charges, en particulier véhicule à benne amovible ou véhicule multibenne, avec un dispositif de changement (2) pour des bennes amovibles (20), qui présente un système de bras pivotants (10) servant de dispositif de levage pour les bennes amovibles (20) et un dispositif d'entraînement hydraulique pour le système de bras pivotants, dans lequel l'unité d'entraînement hydraulique comprend deux vérins hydrauliques (28a, 28b) couplés mécaniquement pour un fonctionnement synchronisé, caractérisé en ce qu'il présente un dispositif d'entraînement hydraulique selon l'une des revendications précédentes.
EP05011364A 2004-05-27 2005-05-25 Dispositif de commande pour un système de manutention hydraulique, en particulier un bras pivotant d'un sytème de levage de benne amovible de camion Active EP1600643B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004025928 2004-05-27
DE102004025928A DE102004025928A1 (de) 2004-05-27 2004-05-27 Steuereinrichtung zur Steuerung einer hydraulischen Antriebseinrichtung eines Lastenbewegungsgerätes, insbesondere einer Schwenkarmanordnung als Hubgerät für Wechselbehälter auf einem Lastentransportfahrzeug

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EP1600643A1 EP1600643A1 (fr) 2005-11-30
EP1600643B1 true EP1600643B1 (fr) 2007-06-06

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DE102008020777A1 (de) * 2008-04-25 2009-10-29 Franz Xaver Meiller Fahrzeug- Und Maschinenfabrik - Gmbh & Co Kg Absetzkipper mit Überladungssicherung
DE102014009564A1 (de) * 2014-06-27 2015-12-31 Hydac B.V. Steuerungsvorrichtung für mindestens einen fluidisch ansteuerbaren Aktuator, Arbeitsmaschine mit einer solchen Steuerungsvorrichtung nebst Verfahren zum Betrieb derselben

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DE102004025928A1 (de) 2005-12-22
ATE364139T1 (de) 2007-06-15
EP1600643A1 (fr) 2005-11-30

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