EP2786023B1 - System for improving the energy efficiency in hydraulic systems - Google Patents

System for improving the energy efficiency in hydraulic systems Download PDF

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Publication number
EP2786023B1
EP2786023B1 EP12790418.3A EP12790418A EP2786023B1 EP 2786023 B1 EP2786023 B1 EP 2786023B1 EP 12790418 A EP12790418 A EP 12790418A EP 2786023 B1 EP2786023 B1 EP 2786023B1
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EP
European Patent Office
Prior art keywords
accumulator
piston
pressure
working cylinder
hydraulic
Prior art date
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Active
Application number
EP12790418.3A
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German (de)
French (fr)
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EP2786023A1 (en
Inventor
Frank Schulz
Peter Bruck
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Hydac Fluidtechnik GmbH
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Hydac Fluidtechnik GmbH
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Publication of EP2786023A1 publication Critical patent/EP2786023A1/en
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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
    • F15B3/00—Intensifiers or fluid-pressure converters, e.g. pressure exchangers; Conveying pressure from one fluid system to another, without contact between the fluids
    • 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
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/024—Installations or systems with accumulators used as a supplementary power source, e.g. to store energy in idle periods to balance pump load
    • 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
    • F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
    • F15B11/032—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force by means of fluid-pressure converters
    • 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
    • F15B11/06—Servomotor systems without provision for follow-up action; Circuits therefor involving features specific to the use of a compressible medium, e.g. air, steam
    • F15B11/072—Combined pneumatic-hydraulic systems
    • 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
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/14—Energy-recuperation means
    • 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
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/04—Accumulators
    • F15B1/08—Accumulators using a gas cushion; Gas charging devices; Indicators or floats therefor
    • F15B1/24—Accumulators using a gas cushion; Gas charging devices; Indicators or floats therefor with rigid separating means, e.g. pistons
    • 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
    • F15B2201/00—Accumulators
    • F15B2201/20—Accumulator cushioning means
    • F15B2201/205—Accumulator cushioning means using gas
    • 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
    • F15B2201/00—Accumulators
    • F15B2201/30—Accumulator separating means
    • F15B2201/31—Accumulator separating means having rigid separating means, e.g. pistons
    • 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
    • F15B2201/00—Accumulators
    • F15B2201/40—Constructional details of accumulators not otherwise provided for
    • F15B2201/41—Liquid ports
    • 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
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • F15B2211/216—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being pneumatic-to-hydraulic converters
    • 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
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5151—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and a directional control valve
    • F15B2211/5152—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and a directional control valve being connected to multiple pressure sources

Definitions

  • the invention relates to a system for improving the energy efficiency of hydraulic systems having the features in the preamble of claim 1.
  • the efficiency of energy conversion leaves something to be desired.
  • One reason for this is the dependence of the charging and discharging processes of the hydraulic accumulator on the respective system pressure. More specifically, the hydraulic accumulator can be charged only when the system pressure is greater than the gas pressure in the gas side store. If the system pressure in the respective operating situation of the working cylinder can not be established, there is no possibility to absorb energy in the memory. Also the Endlade polish of the memory is subject to a limitation, as always only energy can be fed back from the memory when the storage pressure is still greater than the current system pressure.
  • a fluid control comprises a control device by means of the piston accumulator in a fluid circuit of the working equipment switched on or off, and that the control device for the pertinent switching operations has a monitoring device, the at least system states of the working equipment and / or the piston accumulator is reached, it is achieved that the device for energy saving is used only if an operation of the working equipment in normal working mode makes this seem necessary, whereby special operations with the machine, in which the work equipment is completely relieved or very heavily loaded, are not hindered , This is achieved with the known solution, a favorable energy conversion.
  • the US 5,971,027 A describes a system for improving the energy efficiency of hydraulic systems, preferably in construction machines, with a working cylinder for moving a bucket or similar equipment on a construction machine, the working cylinder operates in an operating state as a consumer of hydraulic energy and another operating state as a generator of hydraulic energy, and with a hydraulic accumulator, which in an operating state of the working cylinder of this can be charged for energy storage and the other operating state for an energy delivery to the working cylinder is discharged, wherein at least one hydraulic accumulator is provided in the form of an adjustable hydropneumatic piston accumulator, in which a plurality of pressure chambers are formed, which adjoin different sized effective surfaces on the fluid side of the accumulator piston, and wherein the system comprises an actuating arrangement for connecting a pressure chamber of the piston accumulator with the working cylinder.
  • the invention has the object to provide a system of the type considered available, which allows an even more favorable energy conversion.
  • a significant feature of the invention is that an adjusting arrangement is provided which connects a selected pressure chamber or a plurality of selected pressure chambers of the piston accumulator with the working cylinder depending on the prevailing on the gas side of the piston accumulator and the working pressure level, and that the actuating arrangement a Assigned control logic that processes the signals from sensor devices for controlling the valves associated with the actuator assembly, which represent the pressure level on the gas side of the piston accumulator and the respective operating state of the working cylinder.
  • multi-stage memory also results in the possibility of influencing the charging time by selecting effective areas. If, for example, a constant volume flow is used to select a small area, the result is a short charging time for the storage tank, while at constant flow rates a larger effective area leads to a longer charging time.
  • a larger effective area leads to a longer charging time.
  • different piston effective areas can be a finer or coarser pressure gradation reach. Also, to achieve a particularly high resolution, more than one memory could be provided with different pressure chambers.
  • the logic controls the energy transformation by deciding according to the load state on the working cylinder and the state of charge at the memory as it is charged or discharged. There is the possibility that the user can influence the logic by his own specifications and thus determine the operating characteristics of the system.
  • the arrangement can be made with advantage so that the accumulator piston is designed to form differently sized effective surfaces as stepped piston and has on its fluid side of cylinder surfaces adjacent piston sub-surfaces, wherein the storage housing has corresponding, adjacent cylinder surfaces mating surfaces, which together with each associated piston sub-areas each delimit separate pressure chambers.
  • active surfaces on the accumulator piston and counter surfaces on the storage housing are arranged in axially spaced-apart stages, and the active surfaces and counter surfaces may be provided in the form of annular surfaces or circular surfaces which are arranged concentrically to the longitudinal axis.
  • the arrangement may advantageously be such that the actuating arrangement has switching valves, via the respective pressure chambers of the piston accumulator, which are selected for charge or discharge, with the working cylinder and the other pressure chambers are connected to the tank. Controlled by the control logic, such a selected pressure chamber or a combination of selected pressure chambers for charging or discharging are connected to the working cylinder, while non-selected pressure chambers during discharge to the tank are depressurized and emptied while charging active pressure chambers from the tank.
  • the arrangement may advantageously be such that the associated sensor device has at least pressure sensors which supply signals for the control logic which represent the filling pressure of the gas side of the piston accumulator and the system pressure on the working cylinder.
  • a displacement sensor is also provided on the working cylinder, which signals piston position and / or piston speed of the working cylinder.
  • the actuating arrangement has a main line connected to the pressure side of a hydraulic pump and from this to the fluid ports of the piston accumulator leading connecting lines, which can be selectively blocked or released by the switching valves or with the tank.
  • hydropneumatic piston accumulator 1 has a storage housing 3 in an axially movable guided storage piston 5, the gas side in the storage housing 3 7, at which a filling port 9 is located, separates from fluid-side pressure chambers.
  • the accumulator piston 5 is designed in the manner of a stepped piston such that, in cooperation with correspondingly stepped parts of the accumulator housing 3, it delimits fluid-side pressure chambers 19, 21, 23 and 25 which adjoin differently sized effective surfaces on the fluid side of the accumulator piston 5.
  • Fig. 1 are these effective areas, from the largest to the smallest, denoted by 11, 13, 15 and 17.
  • the active surfaces 11, 13 and 15 are each formed by concentric annular surfaces to the longitudinal axis, which surround the innermost active surface 17 in the form of a circular area.
  • adjacent pressure chambers 19, 21 and 23 are limited by mating surfaces 27 and 29 and 31 of the storage housing 3 and cylinder surfaces 35 of the cylinder housing 3 and cylinder surfaces 37 on the accumulator piston 5.
  • the adjacent to the active surface 17 pressure chamber 25 is bounded by a mating surface 33 of the storage housing 3 and a cylindrical surface 39 of the accumulator piston 5.
  • a fluid connection 41, 43, 45 and 47 is provided for each pressure chamber 19, 21, 23, 25, a fluid connection 41, 43, 45 and 47 is provided.
  • the associated mating surfaces 27, 29, 31 and 33 are arranged on the storage housing 3 in axially spaced-apart steps.
  • the Fig. 2 shows the piston accumulator 1 in conjunction with associated system components, wherein an actuator 49 is in operative connection with an actuating arrangement 51.
  • a working cylinder 58 (FIG. Fig. 3 ), which is for example part of a lifting-lowering arrangement.
  • the actuator assembly 51 is associated with a control logic 53 which actuates a valve assembly 57 of the actuator assembly 51 by means of a control and regulating unit 55.
  • the valve assembly 57 has, as with reference to Fig. 3 and 4 is more detailed, switching valves, the selected fluid connections between the actuator 49 and the fluid ports 41, 43, 45, 47 of the piston accumulator 1 produce to selectively activate the pressure chambers 19, 21, 23 and 25 for loading or unloading.
  • the control logic 53 processes signals which are supplied by sensor devices and which represent operating states of actuator 49 and piston accumulator 1. Of the sensor devices is in Fig. 2 only a pressure sensor 59 at the filling port 9 of the piston accumulator 1 is shown.
  • the Fig. 3 shows the system according to the invention in conjunction with a lift-lowering arrangement, wherein the actuator has a working cylinder 58 for raising and lowering a load 61.
  • a pressure sensor 63 recognizing the load pressure and a displacement sensor 65 determining the stroke-lowering speed are provided on the working cylinder 58.
  • a hydraulic pump 67 on the output side protected by a pressure relief valve 69, is connected to a system pressure leading main line 71 of the actuator assembly 51. This has for the connection between the main line 71 and the fluid ports 41, 43, 45 and 47 of the piston accumulator 1 each have a connecting line 73, 75, 77 and 80.
  • each valve group is formed of two fast-switching 2/2-way valves, denoted by 79 and 81 and the valve groups v 1 to v 4 are marked with the index 1 to 4.
  • the directional control valves 81 the associated connection line with the associated Fluidanschuss the piston accumulator 1 can be connected or blocked.
  • the main line 71 via a valve which is designed to control the lifting speed as a proportional throttle valve 87, connectable to the working cylinder 58.
  • a fluid filter 85 is flowed through when lowering the working cylinder 58.
  • a pressure relief valve 86 is used to secure the relevant hydraulic circuit. The lifting movement takes place with the aid of the energy stored in the piston accumulator by means of an unloading process from a selected pressure chamber 19, 21, 23, 25 or from a plurality of selected pressure chambers which have the appropriate pressure level for the lifting movement of the load 61.
  • the potential energy of the load 61 is stored as hydraulic energy in the piston accumulator 1 by charging via a lowering speed setting proportional throttle valve 84 and a selected connection line 73, 75, 77, 80 or via a plurality of selected connection lines to a respective fluid port 41 , 43, 45, 47, wherein one or more of the directional control valves 81 is opened, and directional control valves 79 of unselected connection lines connect to the tank 83.
  • a located on the main line 71 directional control valve 88 makes it possible to depressurize or empty the system if necessary.
  • the load pressure on the cylinder 58 is transmitted to the control logic 53 by means of the pressure sensor 63 to lower a load with energy recovery, as well as the gas pressure in the memory 1, which is determined by the pressure sensor 59.
  • the controller can decide how the available potential energy of the cylinder 58 is optimally fed back into the memory 1.
  • a large effective area is chosen to charge the accumulator to a high pressure level. If a high load 61 is applied to the cylinder 58, the memory 1 is charged with a small effective area. The lowering speed of the load is adjusted via the proportional throttle valve 84.
  • the load compensation effected by the system can be discontinuous by selecting and / or switching over the suitable active surfaces, wherein a resolution can be achieved with a sufficiently large number of pressure levels provided in the memory 1 in order to reduce the load without jerking.
  • the corresponding effective area or the corresponding effective areas are selected according to the load 61 on the cylinder 58 as a function of the gas pressure in the accumulator 1.
  • a smaller pressure level is initially selected.
  • the speed for lifting the load 61 is set via the proportional throttle valve 87, wherein the pressure difference is kept as small as possible by the appropriate selection of the effective areas of the memory 1, so that a low-loss conversion of the storage energy in lifting work is possible.
  • Fig. 4 differs from the example of Fig. 3 merely insofar as a pressure compensator 89 or 90 is respectively provided on the proportional throttle valves 84 and 87 in order to generate a constant pressure difference at the associated proportional throttle valve 84, 87. This can be at a switching of the active surfaces of the Memory 1 jumps of the pressure difference at the respective proportional throttle valve 84, 87 compensate.
  • proportional throttle valves 84, 87 when using fast-switching directional valves 79 and 81, these can also be controlled by pulse width modulation, whereby, depending on the pulse modulation, a desired average volume flow is adjustable.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
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Description

Die Erfindung betrifft ein System zur Verbesserung der Energieeffizienz bei Hydrauliksystemen mit den Merkmalen im Oberbegriff von Anspruch 1.The invention relates to a system for improving the energy efficiency of hydraulic systems having the features in the preamble of claim 1.

Angesichts der zunehmenden Verknappung von Ressourcen und den damit zusammenhängenden verstärkten Bemühungen, Energie einzusparen, gewinnen Systeme der vorstehenden Art zunehmend an Bedeutung. Daher kommen solche Systeme bei hydraulischen Einrichtungen und Anlagen, bei denen Aktuatoren in Form von Arbeitszylindern vorgesehen sind, häufig zum Einsatz. Bei Hub-Senk-Anwendungen lässt sich hierbei mittels des Arbeitszylinders die potentielle Energie einer angehobenen Last in hydraulische Energie umsetzen, die gespeichert und rückgespeist werden kann. Auch lässt sich ein derartiges System zur Lastkompensation anwenden.As resources become increasingly scarce and the associated efforts to save energy increase, systems of the above type are becoming increasingly important. Therefore, such systems are often used in hydraulic equipment and systems in which actuators are provided in the form of working cylinders. With lift-lowering applications, the working cylinder can be used to convert the potential energy of a raised load into hydraulic energy, which can be stored and fed back. Also, such a system can be used for load compensation.

Bei den dem Stand der Technik entsprechenden Systemen dieser Art lässt die Effizienz der Energieumsetzung zu wünschen übrig. Eine Ursache hierfür ist die Abhängigkeit der Lade- und Entladeprozesse des Hydrospeichers vom jeweiligen Systemdruck. Genauer gesagt, kann der Hydrospeicher immer nur dann aufgeladen werden, wenn der Systemdruck größer als der im Speicher auf der Gasseite befindliche Gasdruck ist. Wenn der Systemdruck in der jeweiligen Betriebssituation des Arbeitszylinders nicht aufgebaut werden kann, besteht keine Möglichkeit, Energie im Speicher aufzunehmen. Auch der Endladeprozess des Speichers ist insofern einer Einschränkung unterworfen, als immer nur dann Energie aus dem Speicher zurückgespeist werden kann, wenn der Speicherdruck noch größer als der aktuelle Systemdruck ist. Zusätzlich besteht das Problem, dass bei einem Speicherdruck, der größer ist als der am Arbeitszylinder aktuell benötigte Systemdruck, die Druckniveaus von Speicher und System durch Ventile ausgeglichen werden müssen, so dass die Energie, die in dem Differenzdruck zwischen Speicherdruck und Systemdruck steckt, durch Drosselverluste verloren geht.In the prior art systems of this type, the efficiency of energy conversion leaves something to be desired. One reason for this is the dependence of the charging and discharging processes of the hydraulic accumulator on the respective system pressure. More specifically, the hydraulic accumulator can be charged only when the system pressure is greater than the gas pressure in the gas side store. If the system pressure in the respective operating situation of the working cylinder can not be established, there is no possibility to absorb energy in the memory. Also the Endladeprozess of the memory is subject to a limitation, as always only energy can be fed back from the memory when the storage pressure is still greater than the current system pressure. In addition, there is the problem that at a storage pressure that is greater than the system pressure currently required on the working cylinder, the pressure levels of storage and system must be balanced by valves, so that the energy that is in the differential pressure between storage pressure and system pressure, by throttling losses get lost.

Aus der DE 100 06 013 A1 geht eine Vorrichtung zur Energieeinsparung bei hydraulisch betätigbaren Arbeitsgerätschaften hervor unter Einsatz eines Kolbenspeichers. Dadurch, dass bei der bekannten Lösung eine Fluidsteuerung eine Steuerungseinrichtung aufweist, mittels der der Kolbenspeicher in einen Fluidkreis der Arbeitsgerätschaft zu- oder abschaltbar ist, und dass die Steuerungseinrichtung für die dahingehenden Schaltvorgänge eine Überwachungseinrichtung aufweist, die zumindest Systemzustände der Arbeitsgerätschaft und/oder des Kolbenspeichers erfasst, ist erreicht, dass die Vorrichtung zur Energieeinsparung nur dann zum Einsatz kommt, wenn eine Betätigung der Arbeitsgerätschaft im normalen Arbeitsbetrieb dies geboten erscheinen lässt, wobei Sonderarbeitsvorgänge mit der Maschine, bei denen die Arbeitsgerätschaft vollständig entlastet oder sehr stark belastet ist, nicht behindert werden. Damit ist mit der bekannten Lösung eine günstige Energieumsetzung erreicht.From the DE 100 06 013 A1 is a device for energy saving in hydraulically actuated equipment using a piston accumulator. Characterized in that in the known solution, a fluid control comprises a control device by means of the piston accumulator in a fluid circuit of the working equipment switched on or off, and that the control device for the pertinent switching operations has a monitoring device, the at least system states of the working equipment and / or the piston accumulator is reached, it is achieved that the device for energy saving is used only if an operation of the working equipment in normal working mode makes this seem necessary, whereby special operations with the machine, in which the work equipment is completely relieved or very heavily loaded, are not hindered , This is achieved with the known solution, a favorable energy conversion.

Die US 5 971 027 A beschreibt ein System zur Verbesserung der Energieeffizienz bei Hydrauliksystemen, vorzugsweise bei Baumaschinen, mit einem Arbeitszylinder zum Bewegen eines Baggerlöffels oder einer ähnlichen Gerätschaft an einer Baumaschine, wobei der Arbeitszylinder in einem Betriebszustand als Verbraucher hydraulischer Energie und einem anderen Betriebszustand als Erzeuger hydraulischer Energie arbeitet, und mit einem Hydrospeicher, der bei einem Betriebszustand des Arbeitszylinders von diesem zur Energiespeicherung aufladbar und beim anderen Betriebszustand für eine Energieabgabe an den Arbeitszylinder entladbar ist, wobei mindestens ein Hydrospeicher in Form eines verstellbaren hydropneumatischen Kolbenspeichers vorgesehen ist, in dem mehrere Druckräume gebildet sind, die an unterschiedlich große Wirkflächen an der Fluidseite des Speicherkolbens angrenzen, und wobei das System eine Stellanordnung zum Verbinden eines Druckraumes des Kolbenspeichers mit dem Arbeitszylinder aufweist.The US 5,971,027 A describes a system for improving the energy efficiency of hydraulic systems, preferably in construction machines, with a working cylinder for moving a bucket or similar equipment on a construction machine, the working cylinder operates in an operating state as a consumer of hydraulic energy and another operating state as a generator of hydraulic energy, and with a hydraulic accumulator, which in an operating state of the working cylinder of this can be charged for energy storage and the other operating state for an energy delivery to the working cylinder is discharged, wherein at least one hydraulic accumulator is provided in the form of an adjustable hydropneumatic piston accumulator, in which a plurality of pressure chambers are formed, which adjoin different sized effective surfaces on the fluid side of the accumulator piston, and wherein the system comprises an actuating arrangement for connecting a pressure chamber of the piston accumulator with the working cylinder.

Ausgehend von diesem Stand der Technik stellt sich die Erfindung die Aufgabe, ein System der betrachteten Art zur Verfügung zu stellen, das eine noch günstigere Energieumsetzung ermöglicht.Based on this prior art, the invention has the object to provide a system of the type considered available, which allows an even more favorable energy conversion.

Erfindungsgemäß ist diese Aufgabe durch ein System gelöst, das die Merkmale des Patentanspruchs 1 in seiner Gesamtheit aufweist.According to the invention this object is achieved by a system having the features of claim 1 in its entirety.

Demgemäß besteht eine wesentliche Besonderheit der Erfindung darin, dass eine Stellanordnung vorgesehen ist, die in Abhängigkeit von dem jeweiligen auf der Gasseite des Kolbenspeichers und am Arbeitszylinder herrschenden Druckniveau einen ausgewählten Druckraum oder mehrere ausgewählte Druckräume des Kolbenspeichers mit dem Arbeitszylinder verbindet, und dass der Stellanordnung eine Steuerlogik zugeordnet ist, die für die Ansteuerung von der Stellanordnung zugehörigen Ventilen die Signale von Sensoreinrichtungen verarbeitet, die das Druckniveau auf der Gasseite des Kolbenspeichers und den jeweiligen Betriebszustand des Arbeitszylinders darstellen. Dadurch ergibt sich die Möglichkeit, Energie unabhängig vom Vorfülldruck auf der Gasseite des Speichers und unabhängig vom jeweiligen Lastdruck zu recyceln, weil durch Auswählen einer Wirkfläche passender Größe das jeweilig gewünschte Druckniveau am Speicher für Ladung oder Entladung genutzt werden kann. Dadurch ist bei sämtlichen Betriebszuständen eine optimale Energieumsetzung möglich.Accordingly, a significant feature of the invention is that an adjusting arrangement is provided which connects a selected pressure chamber or a plurality of selected pressure chambers of the piston accumulator with the working cylinder depending on the prevailing on the gas side of the piston accumulator and the working pressure level, and that the actuating arrangement a Assigned control logic that processes the signals from sensor devices for controlling the valves associated with the actuator assembly, which represent the pressure level on the gas side of the piston accumulator and the respective operating state of the working cylinder. This results in the ability to recycle energy regardless of the pre-charge pressure on the gas side of the memory and regardless of the load pressure, because by selecting an effective area of appropriate size, the respective desired pressure level at the memory for charging or discharging can be used. As a result, optimal energy conversion is possible in all operating conditions.

Durch den Einsatz eines derartigen "Mehrstufenspeichers" ergibt sich ferner die Möglichkeit, die Ladezeit durch Auswahl von Wirkflächen zu beeinflussen. Wählt man beispielsweise bei konstantem Volumenstrom eine kleine Fläche, ergibt sich eine kurze Ladezeit des Speichers, während bei konstantem Volumenstrom eine größere Wirkfläche zu längerer Ladezeit führt. Durch Ausbildung einer größeren oder kleineren Anzahl von Druckräumen unterschiedlicher Kolbenwirkflächen lässt sein eine feinere oder gröbere Druckabstufung erreichen. Auch könnte, um eine besonders hohe Auflösung zu erreichen, mehr als ein Speicher mit unterschiedlichen Druckräumen vorgesehen sein.The use of such a "multi-stage memory" also results in the possibility of influencing the charging time by selecting effective areas. If, for example, a constant volume flow is used to select a small area, the result is a short charging time for the storage tank, while at constant flow rates a larger effective area leads to a longer charging time. By forming a larger or smaller number of pressure chambers different piston effective areas can be a finer or coarser pressure gradation reach. Also, to achieve a particularly high resolution, more than one memory could be provided with different pressure chambers.

Dabei steuert die Logik die Energietransformation, indem entsprechend dem Lastzustand am Arbeitszylinder und dem Ladezustand am Speicher entschieden wird, wie dieser geladen oder entladen wird. Dabei besteht die Möglichkeit, dass der Anwender durch eigene Vorgaben die Logik beeinflussen und damit die Arbeits-charakteristik des Systems bestimmen kann.The logic controls the energy transformation by deciding according to the load state on the working cylinder and the state of charge at the memory as it is charged or discharged. There is the possibility that the user can influence the logic by his own specifications and thus determine the operating characteristics of the system.

Hinsichtlich der Bauweise des Kolbenspeichers kann die Anordnung mit Vorteil so getroffen sein, dass der Speicherkolben zur Bildung unterschiedlich großer Wirkflächen als Stufenkolben gestaltet ist und an seiner Fluidseite an Zylinderflächen angrenzende Kolbenteilflächen aufweist, wobei das Speichergehäuse korrespondierende, an Zylinderflächen angrenzende Gegenflächen aufweist, die zusammen mit ihnen zugeordneten Kolbenteilflächen jeweils gesonderte Druckräume begrenzen.With regard to the design of the piston accumulator, the arrangement can be made with advantage so that the accumulator piston is designed to form differently sized effective surfaces as stepped piston and has on its fluid side of cylinder surfaces adjacent piston sub-surfaces, wherein the storage housing has corresponding, adjacent cylinder surfaces mating surfaces, which together with each associated piston sub-areas each delimit separate pressure chambers.

Vorzugsweise sind Wirkflächen am Speicherkolben und Gegenflächen am Speichergehäuse in im axialen Abstand voneinander befindlichen Stufen angeordnet, und die Wirkflächen und Gegenflächen können in Form von Ringflächen oder Kreisflächen vorgesehen sein, die konzentrisch zur Längsachse angeordnet sind.Preferably, active surfaces on the accumulator piston and counter surfaces on the storage housing are arranged in axially spaced-apart stages, and the active surfaces and counter surfaces may be provided in the form of annular surfaces or circular surfaces which are arranged concentrically to the longitudinal axis.

Hinsichtlich der Ansteuerung der Druckräume des Kolbenspeichers kann die Anordnung mit Vorteil so getroffen sein, dass die Stellanordnung Schaltventile aufweist, über die jeweilige Druckräume des Kolbenspeichers, die für Ladung oder Entladung ausgewählt sind, mit dem Arbeitszylinder und die übrigen Druckräume mit dem Tank verbindbar sind. Durch die Steuerlogik gesteuert, sind so ein ausgewählter Druckraum oder eine Kombination ausgewählter Druckräume für Ladung oder Entladung mit dem Arbeitszylinder verbindbar, während nicht ausgewählte Druckräume während der Entladung zum Tank hin drucklos entleerbar sind und während der Ladung aktiver Druckräume aus dem Tank nachfüllbar sind.With regard to the control of the pressure chambers of the piston accumulator, the arrangement may advantageously be such that the actuating arrangement has switching valves, via the respective pressure chambers of the piston accumulator, which are selected for charge or discharge, with the working cylinder and the other pressure chambers are connected to the tank. Controlled by the control logic, such a selected pressure chamber or a combination of selected pressure chambers for charging or discharging are connected to the working cylinder, while non-selected pressure chambers during discharge to the tank are depressurized and emptied while charging active pressure chambers from the tank.

Hinsichtlich der Signalversorgung der Steuerlogik kann die Anordnung mit Vorteil so getroffen sein, dass die zugeordnete Sensoreinrichtung zumindest Drucksensoren aufweist, die für die Steuerlogik Signale liefern, die den Fülldruck der Gasseite des Kolbenspeichers und den Systemdruck am Arbeitszylinder darstellen. Vorzugsweise ist außerdem am Arbeitszylinder ein Wegsensor vorgesehen, der Kolbenstellung und/oder Kolbengeschwindigkeit des Arbeitszylinders signalisiert.With regard to the signal supply of the control logic, the arrangement may advantageously be such that the associated sensor device has at least pressure sensors which supply signals for the control logic which represent the filling pressure of the gas side of the piston accumulator and the system pressure on the working cylinder. Preferably, a displacement sensor is also provided on the working cylinder, which signals piston position and / or piston speed of the working cylinder.

Bei besonders vorteilhaften Ausführungsbeispielen weist die Stellanordnung eine mit der Druckseite einer Hydropumpe in Verbindung stehende Hauptleitung sowie von dieser zu den Fluidanschlüssen des Kolbenspeichers führende Verbindungsleitungen auf, wobei diese jeweils durch die Schaltventile wahlweise sperrbar oder freigebbar oder mit dem Tank verbindbar sind.In particularly advantageous embodiments, the actuating arrangement has a main line connected to the pressure side of a hydraulic pump and from this to the fluid ports of the piston accumulator leading connecting lines, which can be selectively blocked or released by the switching valves or with the tank.

Nachstehend ist die Erfindung anhand der Zeichnung im Einzelnen erläutert. Es zeigen:

Fig. 1
in einem stark schematisch vereinfachten Längsschnitt ein Ausführungsbeispiel eines hydropneumatischen Kolbenspeichers in einer Mehrstufenausführung für den Einsatz bei dem erfindungsgemäßen System;
Fig. 2
eine Prinzipdarstellung, die den Kolbenspeicher von Fig. 1 in Verbindung mit zugehörigen Systemkomponenten des erfindungsgemäßen Systems zeigt;
Fig. 3
den Kolbenspeicher in Verbindung mit einem in Symboldarstellung gezeigten hydraulischen Schaltplan eines Ausführungsbeispiels des Systems für eine Hub-Senk-Anwendung; und
Fig. 4
eine der Fig. 3 entsprechende Darstellung eines abgewandelten Ausführungsbeispiels der Hub-Senk-Anwendung.
The invention is explained in detail below with reference to the drawing. Show it:
Fig. 1
in a highly schematically simplified longitudinal section of an embodiment of a hydropneumatic piston accumulator in a multi-stage design for use in the system according to the invention;
Fig. 2
a schematic representation of the piston accumulator of Fig. 1 in connection with associated system components of the system according to the invention;
Fig. 3
the piston accumulator in conjunction with a hydraulic circuit diagram shown in a symbolic representation of an embodiment of the system for a lifting-lowering application; and
Fig. 4
one of the Fig. 3 corresponding representation of a modified embodiment of the lifting-lowering application.

Der in Fig. 1 in schematisch vereinfachter Darstellung gezeigte hydropneumatische Kolbenspeicher 1 weist einen in einem Speichergehäuse 3 axial bewegbar geführten Speicherkolben 5 auf, der im Speichergehäuse 3 eine Gasseite 7, an der sich ein Füllanschluss 9 befindet, von fluidseitigen Druckräumen trennt. Der Speicherkolben 5 ist in der Art eines Stufenkolbens derart gestaltet, dass er in Zusammenwirkung mit entsprechend gestuften Teilen des Speichergehäuses 3 fluidseitige Druckräume 19, 21, 23 und 25 begrenzt, die an unterschiedlich große Wirkflächen an der Fluidseite des Speicherkolbens 5 angrenzen. In Fig. 1 sind diese Wirkflächen, von der größtflächigen bis zur kleinstflächigen, mit 11, 13, 15 und 17 bezeichnet. Dabei sind die Wirkflächen 11, 13 und 15 jeweils durch zur Längsachse konzentrische Kreisringflächen gebildet, die die innerste Wirkfläche 17 in Form einer Kreisfläche umgeben. An die Wirkflächen 11, 13 und 15 angrenzende Druckräume 19, 21 bzw. 23 sind durch Gegenflächen 27 bzw. 29 bzw. 31 des Speichergehäuses 3 sowie durch Zylinderflächen 35 des Zylindergehäuses 3 und Zylinderflächen 37 am Speicherkolben 5 begrenzt. Der an die Wirkfläche 17 angrenzende Druckraum 25 ist durch eine Gegenfläche 33 des Speichergehäuses 3 sowie eine Zylinderfläche 39 des Speicherkolbens 5 begrenzt.The in Fig. 1 in a simplified schematic representation shown hydropneumatic piston accumulator 1 has a storage housing 3 in an axially movable guided storage piston 5, the gas side in the storage housing 3 7, at which a filling port 9 is located, separates from fluid-side pressure chambers. The accumulator piston 5 is designed in the manner of a stepped piston such that, in cooperation with correspondingly stepped parts of the accumulator housing 3, it delimits fluid-side pressure chambers 19, 21, 23 and 25 which adjoin differently sized effective surfaces on the fluid side of the accumulator piston 5. In Fig. 1 are these effective areas, from the largest to the smallest, denoted by 11, 13, 15 and 17. In this case, the active surfaces 11, 13 and 15 are each formed by concentric annular surfaces to the longitudinal axis, which surround the innermost active surface 17 in the form of a circular area. To the active surfaces 11, 13 and 15 adjacent pressure chambers 19, 21 and 23 are limited by mating surfaces 27 and 29 and 31 of the storage housing 3 and cylinder surfaces 35 of the cylinder housing 3 and cylinder surfaces 37 on the accumulator piston 5. The adjacent to the active surface 17 pressure chamber 25 is bounded by a mating surface 33 of the storage housing 3 and a cylindrical surface 39 of the accumulator piston 5.

Für jeden Druckraum 19, 21, 23, 25 ist ein Fluidanschuss 41, 43, 45 bzw. 47 vorgesehen. Wie die Wirkflächen 11, 13, 15 und 17 am Speicherkolben 5 sind die zugeordneten Gegenflächen 27, 29, 31 bzw. 33 am Speichergehäuse 3 in axial zueinander beabstandeten Stufen angeordnet.For each pressure chamber 19, 21, 23, 25, a fluid connection 41, 43, 45 and 47 is provided. Like the active surfaces 11, 13, 15 and 17 on the accumulator piston 5, the associated mating surfaces 27, 29, 31 and 33 are arranged on the storage housing 3 in axially spaced-apart steps.

Die Fig. 2 zeigt den Kolbenspeicher 1 in Verbindung mit zugeordneten Systemkomponenten, wobei ein Aktuator 49 in Wirkverbindung mit einer Stellanordnung 51 ist. Wie bereits bemerkt, kann als Aktuator 49 ein Arbeitszylinder 58 (Fig. 3) vorgesehen sein, der beispielsweise Bestandteil einer Hub-Senk-Anordnung ist. Der Stellanordnung 51 ist eine Steuerlogik 53 zugeordnet, die mittels einer Steuer- und Regeleinheit 55 eine Ventilanordnung 57 der Stellanordnung 51 betätigt. Die Ventilanordnung 57 weist, wie anhand der Fig. 3 und 4 näher ausgeführt wird, Schaltventile auf, die ausgewählte Fluidverbindungen zwischen Aktuator 49 und den Fluidanschlüssen 41, 43, 45, 47 des Kolbenspeichers 1 herstellen, um wahlweise die Druckräume 19, 21, 23 und 25 für Lade- oder Entladevorgänge zu aktivieren. Hierfür verarbeitet die Steuerlogik 53 Signale, die von Sensoreinrichtungen geliefert sind und die Betriebszustände von Aktuator 49 und Kolbenspeicher 1 darstellen. Von den Sensoreinrichtungen ist in Fig. 2 lediglich ein Drucksensor 59 am Füllanschluss 9 des Kolbenspeichers 1 gezeigt.The Fig. 2 shows the piston accumulator 1 in conjunction with associated system components, wherein an actuator 49 is in operative connection with an actuating arrangement 51. As already noted, as the actuator 49, a working cylinder 58 (FIG. Fig. 3 ), which is for example part of a lifting-lowering arrangement. The actuator assembly 51 is associated with a control logic 53 which actuates a valve assembly 57 of the actuator assembly 51 by means of a control and regulating unit 55. The valve assembly 57 has, as with reference to Fig. 3 and 4 is more detailed, switching valves, the selected fluid connections between the actuator 49 and the fluid ports 41, 43, 45, 47 of the piston accumulator 1 produce to selectively activate the pressure chambers 19, 21, 23 and 25 for loading or unloading. For this purpose, the control logic 53 processes signals which are supplied by sensor devices and which represent operating states of actuator 49 and piston accumulator 1. Of the sensor devices is in Fig. 2 only a pressure sensor 59 at the filling port 9 of the piston accumulator 1 is shown.

Die Fig. 3 zeigt das erfindungsgemäße System in Verbindung mit einer Hub-Senk-Anordnung, wobei der Aktuator einen Arbeitszylinder 58 zum Heben und Senken einer Last 61 aufweist. Zur Erzeugung der von der Steuerlogik 53 zu verarbeitenden Signale sind am Arbeitszylinder 58 ein den Lastdruck erkennender Drucksensor 63 und ein die Hub-Senk-Geschwindigkeit ermittelnder Wegsensor 65 vorgesehen. Eine Hydropumpe 67, ausgangsseitig abgesichert durch ein Druckbegrenzungsventil 69, ist mit einer den Systemdruck führenden Hauptleitung 71 der Stellanordnung 51 verbunden. Diese weist für die Verbindung zwischen der Hauptleitung 71 und den Fluidanschlüssen 41, 43, 45 und 47 des Kolbenspeichers 1 jeweils eine Verbindungsleitung 73, 75, 77 und 80 auf. In jeder der Verbindungsleitungen befindet sich eine von der Steuerlogik 53 betätigbare Ventilgruppe, symbolhaft bezeichnet mit v1, v2, usw., wobei jede Ventilgruppe aus zwei schnellschaltenden 2/2-Wege-Ventilen gebildet ist, die mit 79 und 81 bezeichnet und bei den Ventilgruppen v1 bis v4 mit dem Index 1 bis 4 gekennzeichnet sind. Über die Wegeventile 81 ist die zugehörige Verbindungsleitung mit dem zugehörigen Fluidanschuss des Kolbenspeichers 1 verbindbar oder sperrbar. Über die Wegeventile 79 ist die jeweilige Verbindungsleitung 73, 75, 77, 80 mit dem Tank 83 verbindbar.The Fig. 3 shows the system according to the invention in conjunction with a lift-lowering arrangement, wherein the actuator has a working cylinder 58 for raising and lowering a load 61. For generating the signals to be processed by the control logic 53, a pressure sensor 63 recognizing the load pressure and a displacement sensor 65 determining the stroke-lowering speed are provided on the working cylinder 58. A hydraulic pump 67, on the output side protected by a pressure relief valve 69, is connected to a system pressure leading main line 71 of the actuator assembly 51. This has for the connection between the main line 71 and the fluid ports 41, 43, 45 and 47 of the piston accumulator 1 each have a connecting line 73, 75, 77 and 80. In each of the connecting lines is a actuatable by the control logic valve group 53, symbolically denoted by v 1 , v 2 , etc., each valve group is formed of two fast-switching 2/2-way valves, denoted by 79 and 81 and the valve groups v 1 to v 4 are marked with the index 1 to 4. About the directional control valves 81, the associated connection line with the associated Fluidanschuss the piston accumulator 1 can be connected or blocked. About the directional valves 79, the respective connecting line 73, 75, 77, 80 connected to the tank 83.

Für einen Hubvorgang ist die Hauptleitung 71 über ein Ventil, das zur Steuerung der Hubgeschwindigkeit als proportionales Drosselventil 87 ausgebildet ist, mit dem Arbeitszylinder 58 verbindbar. Ein Fluidfilter 85 wird beim Senken des Arbeitszylinders 58 durchströmt. Ferner ist zur Sicherung des diesbezüglichen Hydraulikreises ein Druckbegrenzungsventil 86 eingesetzt. Die Hubbewegung erfolgt mit Hilfe der im Kolbenspeicher gespeicherten Energie durch einen Entladevorgang aus einem ausgewählten Druckraum 19, 21, 23, 25 oder aus mehreren ausgewählten Druckräumen, die das passende Druckniveau für die Hubbewegung der Last 61 besitzen. Bei Absenkbewegungen wird die potentielle Energie der Last 61 als hydraulische Energie im Kolbenspeicher 1 gespeichert, indem ein Ladevorgang über ein die Senkgeschwindigkeit einstellendes Proportional-Drosselventil 84 und eine ausgewählte Verbindungsleitung 73, 75, 77, 80 oder über mehrere ausgewählte Verbindungsleitungen zu einem betreffenden Fluidanschluss 41, 43, 45, 47 erfolgt, wobei eines oder mehrere der Wegeventile 81 geöffnet ist bzw. sind und Wegeventile 79 nicht gewählter Verbindungsleitungen die Verbindung zum Tank 83 herstellen. Durch diese Verbindung sind nicht gewählte Druckräume 19, 21, 23, 25 des Kolbenspeichers 1 bei Entladevorgängen drucklos und bei Ladevorgängen aus dem Tank 83 nachfüllbar. Ein an der Hauptleitung 71 befindliches Wegeventil 88 ermöglicht es, das System bei Bedarf drucklos zu machen oder zu entleeren.For a lifting operation, the main line 71 via a valve which is designed to control the lifting speed as a proportional throttle valve 87, connectable to the working cylinder 58. A fluid filter 85 is flowed through when lowering the working cylinder 58. Furthermore, a pressure relief valve 86 is used to secure the relevant hydraulic circuit. The lifting movement takes place with the aid of the energy stored in the piston accumulator by means of an unloading process from a selected pressure chamber 19, 21, 23, 25 or from a plurality of selected pressure chambers which have the appropriate pressure level for the lifting movement of the load 61. During lowering movements, the potential energy of the load 61 is stored as hydraulic energy in the piston accumulator 1 by charging via a lowering speed setting proportional throttle valve 84 and a selected connection line 73, 75, 77, 80 or via a plurality of selected connection lines to a respective fluid port 41 , 43, 45, 47, wherein one or more of the directional control valves 81 is opened, and directional control valves 79 of unselected connection lines connect to the tank 83. By this connection are not selected pressure chambers 19, 21, 23, 25 of the piston accumulator 1 depressurized during discharging and refillable during loading from the tank 83. A located on the main line 71 directional control valve 88 makes it possible to depressurize or empty the system if necessary.

Im Betrieb wird zum Senken einer Last mit Energie-Rückgewinnung der Lastdruck am Zylinder 58 mittels des Drucksensors 63 an die Steuerlogik 53 übermittelt, ebenso wie der Gasdruck im Speicher 1, der durch den Drucksensor 59 ermittelt ist. Durch diese Informationen kann die Regelung entscheiden, wie die zur Verfügung stehende potentielle Energie des Zylinders 58 optimal in den Speicher 1 zurückgespeist wird. Bei geringen Lasten wird eine große Wirkfläche gewählt, um den Speicher auf ein hohes Druckniveau zu laden. Liegt eine hohe Last 61 am Zylinder 58 an, wird mit einer kleinen Wirkfläche der Speicher 1 geladen. Die Senkgeschwindigkeit der Last wird über das proportionale Drosselventil 84 eingestellt.In operation, the load pressure on the cylinder 58 is transmitted to the control logic 53 by means of the pressure sensor 63 to lower a load with energy recovery, as well as the gas pressure in the memory 1, which is determined by the pressure sensor 59. Through this information, the controller can decide how the available potential energy of the cylinder 58 is optimally fed back into the memory 1. At low loads, a large effective area is chosen to charge the accumulator to a high pressure level. If a high load 61 is applied to the cylinder 58, the memory 1 is charged with a small effective area. The lowering speed of the load is adjusted via the proportional throttle valve 84.

Die durch das System bewirkte Lastkompensation kann durch Anwählen und/oder Umschalten der geeigneten Wirkflächen unstetig erfolgen, wobei mit einer genügend großen Anzahl an im Speicher 1 zur Verfügung gestellten Druckstufen eine Auflösung erreichbar ist, um die Last ruckfrei zu senken. Um eine Last 61 bei geladenem Kolbenspeicher 1 mit oder ohne Hilfe der Pumpe 67 zu heben, werden entsprechend der Last 61 am Zylinder 58 in Abhängigkeit vom Gasdruck im Speicher 1 die entsprechende Wirkfläche oder die entsprechenden Wirkflächen gewählt. Um die Bewegung der Last 61 ruckfrei anzufahren, wird vorzugsweise zunächst ein kleineres Druckniveau gewählt. Die Geschwindigkeit zum Anheben der Last 61 wird über das proportionale Drosselventil 87 eingestellt, wobei die Druckdifferenz durch die geeignete Auswahl der Wirkflächen des Speichers 1 möglichst klein gehalten bleibt, so dass eine verlustarme Umwandlung der Speicherenergie in Hubarbeit möglich ist.The load compensation effected by the system can be discontinuous by selecting and / or switching over the suitable active surfaces, wherein a resolution can be achieved with a sufficiently large number of pressure levels provided in the memory 1 in order to reduce the load without jerking. In order to lift a load 61 when the piston accumulator 1 is loaded with or without the aid of the pump 67, the corresponding effective area or the corresponding effective areas are selected according to the load 61 on the cylinder 58 as a function of the gas pressure in the accumulator 1. In order to approach the movement of the load 61 smoothly, preferably a smaller pressure level is initially selected. The speed for lifting the load 61 is set via the proportional throttle valve 87, wherein the pressure difference is kept as small as possible by the appropriate selection of the effective areas of the memory 1, so that a low-loss conversion of the storage energy in lifting work is possible.

Das Ausführungsbeispiel von Fig. 4 unterscheidet sich vom Beispiel von Fig. 3 lediglich insofern, als an den Proportional-Drosselventilen 84 und 87 jeweils eine Druckwaage 89 bzw. 90 vorgesehen ist, um eine konstante Druckdifferenz am zugeordneten Proportional-Drosselventil 84, 87 zu erzeugen. Dadurch lassen sich bei einem Umschalten der Wirkflächen des Speichers 1 Sprünge der Druckdifferenz am jeweiligen Proportional-Drosselventil 84, 87 kompensieren.The embodiment of Fig. 4 differs from the example of Fig. 3 merely insofar as a pressure compensator 89 or 90 is respectively provided on the proportional throttle valves 84 and 87 in order to generate a constant pressure difference at the associated proportional throttle valve 84, 87. This can be at a switching of the active surfaces of the Memory 1 jumps of the pressure difference at the respective proportional throttle valve 84, 87 compensate.

Anstelle der Proportional-Drosselventile 84, 87 können bei Verwendung schnellschaltender Wegeventile 79 und 81 diese auch durch Pulsweitenmodulation angesteuert werden, wodurch, abhängig von der Impulsmodulation, ein gewünschter mittlerer Volumenstrom einstellbar ist.Instead of the proportional throttle valves 84, 87, when using fast-switching directional valves 79 and 81, these can also be controlled by pulse width modulation, whereby, depending on the pulse modulation, a desired average volume flow is adjustable.

Claims (7)

  1. A system for improving the energy efficiency in hydraulic systems, having at least one working cylinder (58) which operates as a consumer of hydraulic energy in one operating state, and as a generator of hydraulic energy in another operating state, and having a hydraulic accumulator (1) which can be charged by the working cylinder for storing energy in one operating state of the working cylinder (58), and which can be discharged for delivering energy to the working cylinder (58) in another operating state, at least one hydraulic accumulator being provided in the form of an adjustable hydropneumatic piston accumulator (1) in which a plurality of pressure chambers (19, 21, 23, 25) are formed which adjoin effective surfaces (11, 13, 15, 17) of different sizes on the fluid side of the accumulator piston (5), characterised in that an adjustment assembly (51) is provided which is designed such that it connects a selected pressure chamber (19, 21, 23, 25) or a number of selected pressure chambers (19, 21, 23, 25) of the piston accumulator (1) to the working cylinder (58) dependently upon the respective pressure level that prevails on the gas side of the piston accumulator (1) and at the working cylinder (58), and that a control logic unit (53) that forms part of the system is associated with the adjustment assembly (51), which control logic unit processes the signals from sensor devices (59, 63) for the control of the valves (79, 81) associated with the adjustment assembly (51), which sensor devices display the pressure level on the gas side of the piston accumulator (1) and the respective operating state of the working cylinder (58).
  2. The system according to Claim 1, characterised in that the accumulator piston (5) is configured as a step piston for the formation of different active surfaces (11, 13, 15, 17) and has partial piston surfaces that are adjacent to cylinder surfaces (35, 37, 39) on the fluid side thereof, and in that the accumulator housing (3) has corresponding mating surfaces (27, 29, 31, 33) that are adjacent to cylinder surfaces (35, 37), which mating surfaces together with partial piston surfaces associated therewith, each delimit separate pressure chambers (19, 21, 23, 25).
  3. The system according to any of the preceding claims, characterised in that active surfaces (11, 13, 15, 17) on the accumulator piston (5) and mating surfaces (27, 29, 31, 33) on the accumulator housing (3) are disposed an axial distance apart from one another.
  4. The system according to any of the preceding claims, characterised in that the active surfaces (11, 13, 15, 17) and the mating surfaces (27, 29, 31, 33) are provided in the form of annular surfaces or circular surfaces which are arranged concentrically to the longitudinal axis.
  5. The system according to any of the preceding claims, characterised in that the adjustment assembly (51) has selector valves (79, 81) by means of which respective pressure chambers (19, 21, 23, 25), which are selected for charging or discharging, can be connected to the working cylinder (58), and the remaining pressure chambers (19, 21, 23, 25) can be connected to the tank (83).
  6. The system according to any of Claims 2 to 6, characterised in that the sensor devices have at least pressure sensors (59, 63) which provide signals to the control logic unit (53), which signals indicate the filling pressure on the gas side of the piston accumulator (1) and the system pressure at the working cylinder (58).
  7. The system according to any of the preceding claims, characterised in that the adjustment assembly (51) comprises a main line (71) that is connected to the pressure side of a hydraulic pump (67), as well as connecting lines (73, 75, 77, 80) that run from the latter to the fluid ports (41, 43, 45, 47) of the piston accumulator (1), and that these connecting lines are each able to be selectively blocked, released or connected to the tank (83) by means of the switching valves (79, 81).
EP12790418.3A 2011-12-03 2012-11-09 System for improving the energy efficiency in hydraulic systems Active EP2786023B1 (en)

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DE102011120226A DE102011120226B4 (en) 2011-12-03 2011-12-03 System for improving the energy efficiency of hydraulic systems
PCT/EP2012/004654 WO2013079151A1 (en) 2011-12-03 2012-11-09 System for improving the energy efficiency in hydraulic systems

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EP2786023A1 EP2786023A1 (en) 2014-10-08
EP2786023B1 true EP2786023B1 (en) 2017-08-23

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EP (1) EP2786023B1 (en)
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WO (1) WO2013079151A1 (en)

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WO2013079151A1 (en) 2013-06-06
US20150152889A1 (en) 2015-06-04
DE102011120226B4 (en) 2013-08-14
US10323657B2 (en) 2019-06-18
DE102011120226A1 (en) 2013-06-06
EP2786023A1 (en) 2014-10-08

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