EP3161327A1 - Control device for at least one fluidically actuatable actuator, working machine having a control device of this type, and method for operating same - Google Patents
Control device for at least one fluidically actuatable actuator, working machine having a control device of this type, and method for operating sameInfo
- Publication number
- EP3161327A1 EP3161327A1 EP15730971.7A EP15730971A EP3161327A1 EP 3161327 A1 EP3161327 A1 EP 3161327A1 EP 15730971 A EP15730971 A EP 15730971A EP 3161327 A1 EP3161327 A1 EP 3161327A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- actuator
- control device
- valve
- pressure
- proportional
- 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.)
- Withdrawn
Links
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
- F15B2211/3056—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
- F15B2211/32—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
- F15B2211/415—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
- F15B2211/60—Circuit components or control therefor
- F15B2211/63—Electronic controllers
- F15B2211/6303—Electronic controllers using input signals
- F15B2211/6306—Electronic controllers using input signals representing a pressure
- F15B2211/6313—Electronic controllers using input signals representing a pressure the pressure being a load pressure
-
- 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
- F15B2211/60—Circuit components or control therefor
- F15B2211/665—Methods of control using electronic components
-
- 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
- F15B2211/80—Other types of control related to particular problems or conditions
- F15B2211/86—Control during or prevention of abnormal conditions
- F15B2211/8606—Control during or prevention of abnormal conditions the abnormal condition being a shock
Definitions
- Control device for at least one fluidically actuatable actuator, working machine with such a control device and method for operating the same
- the invention relates to a control device for at least one fluidically actuatable actuator which has at least two mutually separated working spaces, which occupy different pressure levels depending on a load acting on the actuator and to be moved by him and at least for a Um Tavernvorgang the actuator temporarily by means of a connecting device can be connected to each other.
- the invention further relates to a work machine with such a control device and a method for operating the same. Comparable generic solutions as indicated above are freely available on the market. Thus, Fig. 1 of the present patent on a generic control device according to the prior art.
- the known control device has an actuator designed as a hydraulic working cylinder, which as a so-called differential cylinder with its piston-rod unit separates a piston chamber as the one working space from a rod space as the other working space.
- the working spaces separated from one another assume different pressure levels as a function of a load acting on the actuator and to be moved by it. If, for example, the piston-rod unit is moved in the direction of the piston chamber under a load acting from the outside, then it lies on the piston-rod unit a pressing load, the pressure level in the piston chamber increases, and the pressure level in the rod space decreases correspondingly in a gradual manner. Conversely, pulling loads on the rod side lead to an increase in the pressure level in the rod space and to a corresponding gradual reduction in the pressure level in the piston chamber.
- a connecting device connected in the form of an electromagnetically operable 2/2-way switching valve.
- the connecting device In order to keep the amount of fluid to be redirected between the working chambers of the actuator during the movement of the piston-rod unit of the actuator from the actual supply side low, the connecting device is brought into its continuous fluid-conducting switching position, which is in the form of an on-off Switch immediately in pressure-compensating manner between the work rooms with the immediate consequence that at different pressure levels in the work rooms, which is regularly the case under load, there is a pressure surge in the connection line in addition to the connected hydraulic supply circuit.
- This leads to an increased component load in the components of the hydraulic circuit and the pressure surge is also perceived by an operator of the control device as extremely disadvantageous, since this affects the ergonomic operation of the control device, for example by means of a joy stick.
- the connecting device in particular using the said 2/2-way switching valves realized as timely and fast Um horrvortician between the working spaces of the actuator during a load change or other inputs and Ausfahrvorticiann the piston rods Unit of the hydraulic Raulischen working cylinder allows, without introducing on the supply side larger amounts of fluid in the actuator or to pick up, which helps reduce the upstream on the supply side control valves in terms of their dimensioning in the sense of a "down-sizing" helps.Also, the delivery volumes of the supply pumps used Regardless of the pertinent operation of the connecting device but in any case the retraction and extension of the piston-rod unit is also controlled and supported in the load case via the hydraulic supply circuit.
- regeneration valves The above-described production of a fluid-carrying connection between the working spaces of the actuator by means of the connecting device is also referred to in technical language as regeneration and the electromagnetically actuated 2/2-way switching valves frequently used as connecting means in the prior art are designated as regeneration valves.
- the known control device is used regularly in the field of mobile working machines and by the known solution is in any case also a method for operating such a control device, as described above, shown in working machines.
- the invention has the object to provide contrast, improved solutions that make it possible to operate in functionally reliable and cost-effective manner at least one fluid-actuated actuator such that it also in different load conditions a pressure surge free operation of the Actuator connected hydraulic supply circuit along with its control and supply components allows.
- a control device having the features of claim 1, a work machine having the features of claim 1 and a method of operating a pertinent control device having the features of claim 12.
- connection means of at least one of the pressure levels of the respective actuator actuated proportional pressure level compensation between the respective assignable workrooms such that during the Um Kunststoffvorgangs and substantially regardless of the load, the actuator retains its respectively actuated position or moves into defined predefinable positions.
- the mentioned pressure level compensation, respectively the regeneration takes place continuously due to the applied proportional technique and allows a harmonious and continuous balance of the pressure levels between the work spaces of the respective actuator.
- the connecting device is at least partially realized by means of the proportional valve technology using at least one proportional valve for proportional pressure equalization or it can also preferably fast-switching logic valves, particularly preferably in cascade, for the proportional control are used.
- the proportional valve technology together with the proportional valves to be used is known to the skilled person from another context and has proven sufficiently in practice. If logic valves are used to implement the mentioned proportional valve technology, these are structurally simple in design, yet they are more elaborately designed from the control side than the conventional proportional valve technology. Incidentally, however, by means of the logic valves very metered and therefore "quantized" amounts of fluid can be made available for the control of the respective actuator used, which can significantly improve the control accuracy in the context of regeneration.
- the respective proportional valve is part of an overall valve control device with at least one further proportional valve, wherein the one proportional valve is assigned to each one working space and the other proportional valve to the respective other working space of the actuator. This can be during a switching process 2015/001271
- the controls of the mentioned valves are meaningfully adapted to each other, wherein for a continuous transition during the reversal, the one proportional valve is successively closed, while another proportional valve time or adjusted over the pressure curve, for example, using a ramp function, successively opened.
- a particularly reliable operation during regeneration is achieved if a third proportional valve is used.
- All proportional valves used can be designed as equal components in the form of 2/2 proportional directional control valves, which, in addition to cost advantages, also facilitates the retrofitting of existing control devices already on the market.
- Particularly advantageous is the control device according to the invention with an actuator in the form of a hydraulic working cylinder, such as a differential cylinder to design.
- control device according to the invention can also find application for Gleichgangzylinder and for hydraulic motors and conventional hybrid devices.
- the regeneration according to the invention can be used with the use of the proportional control technology.
- control device for controlling the respective valve, a computer unit (CPU) is provided, which is connected on its input side with pressure transducers, which detect the respective value of the pressure level in the actuator working spaces and on its output side forwards control pulses to the control solenoid of the valves.
- CPU computer unit
- pressure transducers which detect the respective value of the pressure level in the actuator working spaces and on its output side forwards control pulses to the control solenoid of the valves.
- control device has been found to be particularly advantageous in the case of mobile working machines, such as trucks equipped with a hook lift system for lifting and depositing a load, such a hook-lift system Characterized in that when discontinuing the respective load whose center of gravity is far out of the center of gravity of the work machine, respectively of the truck, which in particular leads to high pushing and pulling load or force stresses on each used actuator of the control device used But does not need to be limited to such hook-lift systems, but can also find application where loads to lift and / or implement, for example, in telescopic Lastarmsystemen or forklift and other lifting systems ersonen or other occupants of such means of transport take the pressure shock-free load changes when moving and relocating or placing the load therefore hardly or at least little true and the hydraulic components of the supply circuit, including seals, connections and control edges of the valves include less burdened what their Longer life.
- the invention also relates to a method for operating the above-described control device, wherein in an alternating attack of pulling and pushing loads the mutually separated working spaces of the respective actuator via a proportionally acting connection device in the regeneration operation pressure shock-free connectable to each other.
- a switch between a towing load and a pressing load displacements of the load can be effected with a low engagement force.
- the work to be used which is necessary for shifting the load, can be kept low in the range of change from a pulling load to a pushing load and vice versa. This has an overall positive effect on the energy balance when moving the load using the respective work machine and the necessary drive units, regularly formed from conventional motor-pump combinations can be designed to save power and space.
- FIGS. 2 to 6 show a truck as an example of a mobile working machine with a "hook-lift system” as load lifting and lowering system in various traversing or operating steps;
- FIG. 7 shows a control device with a single fluid-operated actuator, for example for operating a hook-lift system according to FIGS. 2 to 6; and a corresponding control device of FIG. 7, however, two actuators are used fluidly operable.
- Fig. 1 shows in the form of a hydraulic circuit diagram with conventional
- the control device shown in FIG. 1 is used to control an actuator 10 in the form of a hydraulic working cylinder, which is also referred to as a differential cylinder as its piston-rod unit 12 two working spaces 14, 16 separated from each other with different surface ratios and / or volumes ,
- the one, first working space 14 is also referred to as the piston chamber and the other, second working space 16 as a rod space.
- the two working chambers 14, 16 different pressure levels to each other.
- connecting line 18 together with connecting device 20 in the form of an electromagnetically operable 2/2-way switching valve, the two working chambers 14, 16 can be connected to one another in a fluid-conducting manner upon actuation of the valve.
- the pertinent arrangement is also referred to technical language with regeneration device.
- the pertinent regeneration device 18, 20 is connected to a hydraulic supply circuit 22 which can be supplied with fluid from a pressure supply source 24, for example in the form of a constant-displacement pump with hydraulic fluid from a storage tank 26.
- a 4/3-proportional directional control valve 28 To control the entry and exit movement for the actuator 10 is used in a conventional manner, a 4/3-proportional directional control valve 28.
- the directional control valve 28 is shown in Fig. 1 in its locked center position and upon actuation of the valve 28 in the direction of the Fig. 1 seen in its right switching position moves the piston-rod unit 12 and decreases For example, the right extended position shown in FIG. 1 a.
- valve 28 When the valve 28 is actuated into its left-hand valve position, when the safety valve 30 is actuated, the piston-rod unit 12 moves in the direction of a left-hand displacement position. Any excess displaced fluid from the working space 14, 16, which in each case becomes smaller in volume, is brought to the tank side T via the valve 28. Furthermore, the respective working space 14, 16 of the actuator 10 on the inlet or outlet side is provided with a compensating or preloading valve 32, which are also referred to in technical language as "counter balance valves.”
- the valves 20, 30 and 32 shown are an integral part a designated as a whole with 34 valve control device.
- connection device 20 Upon actuation of this connection device 20, a relief of the working chambers 14, 16 is prevented to the storage tank by the safety valve 30 is transferred into the fluidblockie- rende switching position.
- the hydraulic working cylinder shown in FIG. 1 assumes the function of a conventional a small plunger cylinder.
- the actual retraction and extension movement of the piston-rod unit 12 of the actuator 10 by means of the pressure supply device take place with the inclusion of the pressure supply source 24, the storage tank 26 and the valve 28 and the valve control device 34th
- a settling process of the container load 40 is explained in more detail below with reference to various traversing or operating steps.
- the container 40 is raised starting from the Fig. 2 by means of the hook-lift system 38 in the position of FIG. 3 in a first Verahroder operating step, moves the piston-rod unit 12 of the actuator or cylinder 10 and must In doing so, apply the full pushing-out force to raise the container 40, respectively by means of the hook-lift system 38 as shown in FIG. 3 to pivot about the pivot axis PP in a clockwise direction.
- the lever arm between the center of gravity COG of the container 40 and the pivot axis PP of the hook-lift system 38 is maximum.
- the lever arm between the piston-rod unit 12 of the respective actuator 10 and the pivot axis PP however, in contrast to this minimal executed.
- the leverage ratios effective on the hook-lift system 38 are required to reduce the amount required on the actuator 10 for further extension of the piston-rod unit 12 Force changed by the container 40 is moved with its focus COG means of a non-illustrated further working cylinder beyond the pivot axis PP out in the direction of the rear end of the vehicle.
- the actuator 10 is further extended with its piston-rod unit 12 and required for this, further oppressive force goes to zero and is replaced by an increasingly pulling load on the actuator 10, as soon as the center of gravity COG of the container 40 the swivel axis PP of the hook-lift system 38 moves backwards.
- the lever arm between the center of gravity COG and pivot axis PP is thereby reduced, and the lever arm between the actuator 10 and the pivot axis PP automatically becomes correspondingly longer.
- the container 40 is deposited on the ground or other subsurface and under the load, in particular the center of gravity COG of the container 40 learns the respective actuator 10, the largest pulling force on him, which leads to an increase in the load in the rod space 16 while relieving the pressure level in the piston or working space 14.
- the lever arm between the center of gravity COG and pivot axis PP increases, and the lever arm between the actuator 10 and the pertinent pivot axis PP initially increases likewise, and then subsequently decreases again.
- an additional pressure force is then required, if required, applied by the respective actuator 10 in order to push the container 40 back into its final setting-down position.
- the pushing force is initially lower than the required compressive force at the end of the aforementioned first movement or operation, it steadily increases during the recoil movement, and at the end thereof the pushing force of the actuator 10 is at a maximum value reached.
- the lever arm extends between the center of gravity COG and pivot axis PP, whereas the lever arm of the actuator 10 to the pivot axis PP is reduced in length again.
- proportional pressure equalization designated as a whole with 20 connecting device according to FIG. 7, three proportional valves 201, 202 and 203.
- these are electromagnetically controllable 2/2 proportional directional control valves which, in their switching representation shown in FIG. 7, include a spring-loaded check valve function.
- the electromagnetic actuation of the valves 201, 202 and 203 takes place via a central computer unit CPU which, on its processing control input side, receives the voltage values of the pressure sensors MA and MB which are once inserted into the hydraulic supply unit.
- Circuit 22 on the piston side and once on the side of the piston rod fluidly connected to the respective assignable working space 14 and 16 are connected.
- the illustrated in Fig. 7 the first valve 202 is the input side connected to the piston side, respectively the piston or working chamber 14 of the actuator 10 and the output side to the connecting line 18.
- the second valve 203 in turn is the input side to the rod side, respectively the rod or Working chamber 16 of the actuator 10 and the output side connected to the connecting line 18.
- the third valve 201 is connected on the input side to the connecting line 18 and on the output side to a discharge line 42, which leads to the storage tank 26.
- a spring-loaded check valve 44 is connected in each of the two supply lines of the hydraulic supply circuit 22 between the directional control valve 28 and the actuator 10 in the direction of the directional control valve 28 in its blocking position according to the illustration of FIG Fig. 7 is held.
- the actuator 10 extends in a slow travel mode and the regeneration function is switched off, ie the valves 201, 202 and 203 are in their in Fig. 7 shown basic position.
- the pressure transducer MA and MB measure the current pressure on the piston and the rod side of the actuator 10.
- the pressure supply source 24 via the corresponding circuit of the proportional directional valve 28 with the piston side in the form of the working space 14 with the actuator 10 fluid leading connected.
- the rod side of the actuator 10, respectively Bar or working space 16 is then switched by opening or pressing the proportional valves 203 and 201 via the discharge line 42 to the storage tank 26 and thus to the low pressure side of the system.
- the proportional valve 203 remains partially closed in order to be able to exercise at least a minimal braking function on the rod side of the piston rod unit 12 such. Due to the resulting bias cavitation phenomena are excluded, and an unimpeded operation is ensured.
- the container 40 is raised by pivoting the hook-lift system about the pivot axis PP continues at a slow speed.
- the regeneration function is triggered by the proportional valve 201 being closed. This corresponds to a high-speed mode of the system, with the cylinder load being measured from the
- the closing of the proportional valve 201 preferably takes place with a predetermined ramp function, for example in the form of a predefinable ramp time, determined via the computer unit CPU.
- the pump pressure is in turn brought via the 4/3 proportional directional valve 28 to the piston side 14 of the actuator 10.
- the 17 tor 10 is connected to move the pendulum volume on the piston side of the actuator by opening the proportional valve 203 while closing the proportional valves 201 and 202, wherein the valve 201 may be by already preceding switching in its closed or locked switching position. Due to the non-return valve function of the proportional valve 202, the described volume flow compensation between the two working spaces 16, 14 can be made so far. Again, the proportional valve 203 is only partially closed so as to maintain a minimum braking function, or a minimum brake pressure on the rod side, to avoid cavitation in the hydraulic system.
- the valve control device 34 and the addressed connection device 20 are controlled by the computer unit CPU such that the pressure on the piston side of the actuator 10 is between two predeterminable Pressure thresholds (min and max) is operated.
- a pressure supply between the pump pressure side P and the piston or working chamber 14 of the actuator 10 is again established via the valve 28.
- the rod side is in turn fluid-conductively connected to the piston side by corresponding activation of the second proportional valve 203 with simultaneous closing of the proportional valves 202 and 201.
- the fluid may pass the first proportional valve 202 due to its valve check function.
- the proportional valve 201 maintains a pressure at the pressure transducer MA, which lies between two predefinable pressure threshold values (min / max). As soon as the upper pressure threshold value (max) is exceeded at the pressure transducer MA, the proportional valve 201 is opened proportionally. If, on the other hand, the lower pressure threshold value (min) is set at the pressure transducer MA Stepped, the proportional valve 201 is proportionally closed. If the Porportionalventil 201 already be completely closed and the pressure at the pressure transducer MA still fall below the lower pressure threshold (min), the proportional valve 203 is actuated proportionally in the closing direction, otherwise the piston-rod unit 12 extends too fast.
- the proportional valve 203 can regulate the extension speed of the piston-rod unit 12, while the proportional valve 201 is completely closed, so that the fluid flow from the rod chamber 16 via the proportional valves 203 and 202 flows to the piston chamber 14.
- the computer unit CPU controls the proportional directional control valve 28 via electrical lines, which are not shown in detail, so that it throttles the supply pressure P coming from the pressure supply source 24 in a variable manner .
- the Druckversorgunsetti 24 thus must feed only a portion of the fluid, so that the energy consumption can be reduced in such an alternative embodiment.
- the entire system is switched to a slow speed mode by the proportional valve 203 is slightly closed and somid throttles the fluid flow.
- the pump pressure P is directed via the valve 28 to the piston side of the actuator 10, and the rod side is switched to the tank side T by controlling the second proportional valve 203 and opening the third valve 201 together with closing of the first valve 202. Due to the resulting pressure difference, no fluid flows through the first proportional valve 202.
- the control function of the control device according to FIG. 7 can be summarized as follows. If the actuator 10 is extended and thereby increases the pressing load on the piston side of the actuator 10, the regeneration function can be switched to connect the rod side (working chamber 16) with the piston side (working chamber 14) without the necessary fluid supply on the pump side P increased. In this case, the actuator 10 can be actuated in the non-regeneration mode with low traversing speeds and in the regeneration mode with high speeds or graduated in a predefinable minimum and maximum speed range.
- the actuator speed can be adjusted via the proportional valve 203 on the rod side.
- the travel speed of the actuator 10 can be specified via the proportional valve 202.
- the overall system operates in the regeneration mode with a working pressure on the piston side of the actuator 10 which is almost equal to the working pressure when the actuator 10 moves in a basic travel speed.
- the control device according to FIG. 8 will now be described only insofar as it is substantially different from the preceding embodiment. Form according to FIG. 7 differs. In this case, the same reference numerals are used for the same components, and the extent hitherto taken so far apply to the extent of the embodiment of FIG. 8.
- the essential difference consists in the solution according to FIG. 8 only in that, instead of an actuator 10, two actuators 10 are used, which are separated from one another on the piston and rod side to the connecting device 20 and thus to the valve control device 34 as a whole.
- actuators can also be used, for example in the form of hydraulic motors or hybrid systems, in which work spaces of different pressure levels are at least given during the working operation.
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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)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102014009564.9A DE102014009564A1 (en) | 2014-06-27 | 2014-06-27 | Control device for at least one fluidically actuatable actuator, working machine with such a control device and method for operating the same |
PCT/EP2015/001271 WO2015197191A1 (en) | 2014-06-27 | 2015-06-24 | Control device for at least one fluidically actuatable actuator, working machine having a control device of this type, and method for operating same |
Publications (1)
Publication Number | Publication Date |
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EP3161327A1 true EP3161327A1 (en) | 2017-05-03 |
Family
ID=53483770
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP15730971.7A Withdrawn EP3161327A1 (en) | 2014-06-27 | 2015-06-24 | Control device for at least one fluidically actuatable actuator, working machine having a control device of this type, and method for operating same |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP3161327A1 (en) |
DE (1) | DE102014009564A1 (en) |
WO (1) | WO2015197191A1 (en) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102018119315A1 (en) | 2018-08-08 | 2020-02-13 | Terex Global Gmbh | Attachment transport unit for transporting an attachment, in particular the main boom of a mobile crane |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1186783A2 (en) * | 2000-09-08 | 2002-03-13 | Husco International, Inc. | Hydraulic system with cross function regeneration |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6467264B1 (en) * | 2001-05-02 | 2002-10-22 | Husco International, Inc. | Hydraulic circuit with a return line metering valve and method of operation |
DE10340505B4 (en) * | 2003-09-03 | 2005-12-15 | Sauer-Danfoss Aps | Valve arrangement for controlling a hydraulic drive |
DE10340504B4 (en) * | 2003-09-03 | 2006-08-24 | Sauer-Danfoss Aps | Valve arrangement for controlling a hydraulic drive |
DE102004025928A1 (en) * | 2004-05-27 | 2005-12-22 | Franz Xaver Meiller Fahrzeug- Und Maschinenfabrik - Gmbh & Co Kg | Control device for controlling a hydraulic drive device of a load movement device, in particular a Schwenkarmanordnung as a lifting device for swap bodies on a load transport vehicle |
GB2437615B (en) * | 2006-04-04 | 2011-04-13 | Husco Int Inc | Fluid metering mode transitioning technique for a hydraulic control system |
US8096227B2 (en) * | 2008-07-29 | 2012-01-17 | Caterpillar Inc. | Hydraulic system having regeneration modulation |
-
2014
- 2014-06-27 DE DE102014009564.9A patent/DE102014009564A1/en not_active Withdrawn
-
2015
- 2015-06-24 EP EP15730971.7A patent/EP3161327A1/en not_active Withdrawn
- 2015-06-24 WO PCT/EP2015/001271 patent/WO2015197191A1/en active Application Filing
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1186783A2 (en) * | 2000-09-08 | 2002-03-13 | Husco International, Inc. | Hydraulic system with cross function regeneration |
Non-Patent Citations (1)
Title |
---|
See also references of WO2015197191A1 * |
Also Published As
Publication number | Publication date |
---|---|
WO2015197191A1 (en) | 2015-12-30 |
DE102014009564A1 (en) | 2015-12-31 |
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