WO2014183941A1 - Mécanisme d'entraînement à vitesse de rotation variable muni de deux pompes et d'un cylindre différentiel - Google Patents

Mécanisme d'entraînement à vitesse de rotation variable muni de deux pompes et d'un cylindre différentiel Download PDF

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Publication number
WO2014183941A1
WO2014183941A1 PCT/EP2014/057468 EP2014057468W WO2014183941A1 WO 2014183941 A1 WO2014183941 A1 WO 2014183941A1 EP 2014057468 W EP2014057468 W EP 2014057468W WO 2014183941 A1 WO2014183941 A1 WO 2014183941A1
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WO
WIPO (PCT)
Prior art keywords
pump
line
pumps
pressure
drive according
Prior art date
Application number
PCT/EP2014/057468
Other languages
German (de)
English (en)
Inventor
Udo Froehlich
Original Assignee
Robert Bosch Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Publication of WO2014183941A1 publication Critical patent/WO2014183941A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D7/00—Controlling wind motors 
    • F03D7/02—Controlling wind motors  the wind motors having rotation axis substantially parallel to the air flow entering the rotor
    • F03D7/022—Adjusting aerodynamic properties of the blades
    • F03D7/0224—Adjusting blade pitch
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2260/00—Function
    • F05B2260/40—Transmission of power
    • F05B2260/406—Transmission of power through hydraulic systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2260/00—Function
    • F05B2260/70—Adjusting of angle of incidence or attack of rotating blades
    • F05B2260/79—Bearing, support or actuation arrangements therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2270/00—Control
    • F05B2270/60—Control system actuates through
    • F05B2270/604—Control system actuates through hydraulic actuators
    • 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
    • F15B1/022—Installations or systems with accumulators used as an emergency power source, e.g. in case of pump failure
    • 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
    • F15B2211/205—Systems with pumps
    • F15B2211/20507—Type of prime mover
    • 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
    • F15B2211/205—Systems with pumps
    • F15B2211/20507—Type of prime mover
    • F15B2211/20515—Electric motor
    • 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
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20538—Type of pump constant capacity
    • 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
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • 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
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20561—Type of pump reversible
    • 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
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • 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
    • F15B2211/212—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being accumulators
    • 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
    • F15B2211/214—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being hydrotransformers
    • 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
    • F15B2211/265—Control of multiple pressure sources
    • 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
    • F15B2211/265—Control of multiple pressure sources
    • F15B2211/2656—Control of multiple pressure sources by control of the pumps
    • 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
    • F15B2211/265—Control of multiple pressure sources
    • F15B2211/2658—Control of multiple pressure sources by control of the prime movers
    • 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
    • F15B2211/27—Directional control by means of the pressure source
    • 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
    • F15B2211/625—Accumulators
    • 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
    • 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
    • F15B2211/6651—Control of the prime mover, e.g. control of the output torque or rotational speed
    • 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
    • F15B2211/6658—Control using different modes, e.g. four-quadrant-operation, working mode and transportation 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/75—Control of speed of the output member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/755—Control of acceleration or deceleration of the output member
    • 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
    • F15B2211/85—Control during special operating conditions
    • 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
    • F15B2211/875—Control measures for coping with failures
    • F15B2211/8752—Emergency operation mode, e.g. fail-safe operation mode
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/70—Wind energy
    • Y02E10/72—Wind turbines with rotation axis in wind direction

Definitions

  • the invention relates to a variable-speed drive with two pumps and with a differential cylinder.
  • Displacement volumes of the pump (eg 10.6 cc and 18 cc) with the area ratio of the Differenziaizylinders (eg 0 80/0 125) matches.
  • (eg 10.6 / 18 (125 2 -80 2 ) / 125 2 )
  • Disadvantage of such drives from the prior art is that the selection of meaningful sizes of Differenziaizylinders by the requirement of the same ratio of its surfaces (ring surface and piston surface) is very limited to the ratio of the delivery volumes of the pump.
  • the invention is based on the object, a drive with two
  • Both claimed drives have a differential cylinder whose annular space or piston rod space is bounded by an annular surface or piston rod surface of a piston and connected to a first pump, and whose piston bottom space is bounded by a piston bottom surface of the piston and connected to a second pump.
  • the drive is a linear actuator.
  • Both pumps are driven by a common variable speed electric motor.
  • the ratio of the annular surface to the piston bottom surface is equal to the ratio of the delivery volume of the first pump to the delivery volume of the second pump.
  • the requirement for the same ratio of cylinder surfaces and volume flows according to a first inventive concept by adjusting the rotational speeds of the two pumps is realized by a transmission.
  • the ratio of the speed of the first pump to the speed of the second pump is realized via the transmission.
  • the pumps can have the same nominal delivery volume and they can in particular be identical, whereby the assembly cost is reduced.
  • the transmission is driven directly on the input side by an output shaft of the electric motor.
  • the transmission has two output shafts, each driving a pump.
  • the two pumps are mechanically connected in parallel.
  • only one of the pumps is driven directly by the output shaft of the electric motor, wherein the transmission in turn is driven directly by this pump.
  • the transmission has exactly one output shaft, which drives the other pump.
  • a pump with adjustable delivery volume is installed, so that the ratio of the volume flows can be adjusted.
  • the other pump can be a constant pump for device simplification.
  • both pumps are synchronously driven via a one-piece shaft or two mutually coupled shaft sections, the second pump being a variable displacement pump which is permanently adjustable such that the ratio of the annular surface to the piston bottom surface is equal to the ratio of the delivery volume of the first Pump to the delivery volume of the variable is.
  • both pumps are synchronously driven by a one-piece shaft or two coupled shaft portions, wherein the first pump is a variable that is permanently adjustable so that the ratio of the annular surface to the piston bottom surface equal to the ratio of the delivery volume of the variable to the delivery volume of the second pump.
  • both pumps can be arranged in a common housing and thus form a compact double pump.
  • a preferred development of both concepts of the drive according to the invention has a first working line, via which the first pump is connected to the annular space, and a second working line, via which the second pump is connected to the piston bottom space.
  • a high-pressure accumulator is connected to the first working line or directly to the annulus or to the second working line or directly to the piston bottom space
  • the differential cylinder is moved with the pressure medium of the previously loaded high-pressure accumulator. It is particularly preferred if the high-pressure accumulator is connected via an emergency line directly to the piston bottom space, and when the high pressure accumulator is connected via a boost line to the second working line.
  • the emergency function in the direction of extension of the differential cylinder is possible and also a boost function allows, over which the differential cylinder can be extended faster than a supply of the piston head space via the second pump alone.
  • Working line is connected to the boost line or directly to the high-pressure accumulator, and if in the charging line to the boost line opening check valve is arranged, the high-pressure accumulator for emergency function on the first pump, the first
  • a particularly preferred development has a low-pressure line which connects a respective low-pressure connection of the pumps. Then it is to compensate for the difference in volume of the two spaces in the operation of the drive
  • Cylinder creates a negative pressure. Furthermore, it can thus, when the high-pressure accumulator - as described above - via the first pump, the first working line, the charging line (and boost line) is charged, at the same time the revolving second pump via the low pressure line connecting the pumps, the other low pressure line and the second working line pressure medium circulate or circulate without pressure.
  • the differential cylinder is coupled to at least one adjustable rotor blade of a wind turbine, wherein the annular surface of the differential cylinder in the direction of reducing an angle of attack (pitch) of the at least one rotor blade and the piston bottom surface of the differential cylinder in the direction of increasing the pitch (pitch) acts.
  • FIGS. Show it: 1 shows a simplified circuit diagram of a first embodiment of the drive according to the invention
  • FIG. 2 shows a simplified circuit diagram of a second embodiment of the drive according to the invention
  • FIG. 3 shows a simplified circuit diagram of a third exemplary embodiment of the drive according to the invention
  • FIG. 4 shows a simplified circuit diagram of a fourth exemplary embodiment of the drive according to the invention
  • FIG. 5 shows a detailed circuit diagram of a drive according to the invention according to one of the four exemplary embodiments of FIGS. 1 to 4 for a rotor blade adjustment of a wind power plant in a normal mode
  • FIG. 6 shows the circuit diagram of the drive according to FIG. 5 in a normal mode with refilling function
  • FIG. 7 shows the circuit diagram of the drive according to FIG. 5 in a speed boost mode with maximum speed
  • FIG. 8 shows the circuit diagram of the drive according to FIG. 5 in the speed boost mode with minimum speed
  • FIG. 9 shows the circuit diagram of the drive according to FIG. 5 in the speed-boost mode during deceleration, FIG.
  • Figure 10 shows the circuit diagram of the drive according to Figure 5 in an emergency function with maximum
  • Figure 1 1 shows the circuit diagram of the drive according to Figure 5 in the emergency function with low force
  • Figure 12 shows the circuit diagram of the drive according to Figure 5 when loading the
  • FIG. 1 shows a simplified circuit diagram of a first exemplary embodiment of the drive according to the invention. He has a variable speed electric motor 26, at the output of a gear 18 is coupled. This is on the output side on the one hand to a first
  • the Drive shaft 40 of a first pump 23 and on the other hand to a second drive shaft 42 of a second pump 24 is coupled.
  • the transmission 18 is designed such that the first drive shaft 40 always rotates slower than the second drive shaft 42.
  • the two Pumps 23, 24 are identical constant pumps, wherein the first pump 23 always has a smaller delivery volume than the second pump 24 due to the slower drive.
  • the first pump 23 is connected via a first working line 44 to an annular space 48 of a differential cylinder 9, while the second pump 24 is connected via a second working line 46 to a piston head space 50 of the differential cylinder 9.
  • the annular space 48 is delimited by an annular surface A1 of a piston of the differential cylinder 9, while the piston head space 50 is delimited by a piston bottom surface A2 of the piston.
  • the transmission 18 is designed such that the
  • Figure 2 shows a simplified circuit diagram of a second embodiment of the drive according to the invention. This corresponds largely to the first embodiment shown in FIG 1. Deviating from the first embodiment, the required or
  • the transmission 1 18 is designed such that the speed ratio of the first drive shaft 40 to the second drive shaft 42 and thus the delivery volume flow ratio of the first pump 23 to the second pump 24 corresponds to the area ratio of the annular surface A1 to the piston bottom surface A2.
  • FIG. 3 shows a third exemplary embodiment of the drive according to the invention.
  • the electric motor 26, the working lines 44, 46 and the differential cylinder 9 correspond to those of the two preceding embodiments.
  • the volume flow ratio of the two pumps 223, 224 required by the area ratio A1 to A2 is realized in that the first pump 223 is a constant displacement pump, while the second pump 224 is a variable displacement pump whose volume is correspondingly greater than the first Pump 223 is set to increase.
  • the electric motor 26, the fixed displacement pump 223 and the variable displacement pump 224 are mechanically "in series" connected.
  • Figure 4 shows a fourth embodiment of the drive according to the invention, which is in principle similar to the third embodiment.
  • the working lines 44, 46 and the differential cylinder 9 correspond to those of the previous embodiments.
  • the first pump 323 is a variable displacement pump and the second pump 324 is a constant displacement pump, wherein the delivery volume of the first pump 323 is set reduced in the required manner.
  • the electric motor 26, the variable displacement pump 323 and the fixed displacement pump 324 are mechanically "in series" connected.
  • FIG. 5 to 12 each show a detailed circuit diagram of a
  • the two pumps shown correspond to those of one of the preceding embodiments 23, 24; 223, 224; 323, 324.
  • the first pump 23; 223; 323 is connected via the first working line 44 with the annular space 48 of the Differenziaizylinders 9, while the second pump 24; 224; 324 is connected via the second working line 46 with the piston head space 50 of the Differenziaizylinders 9.
  • first working line 44 is one of the first pump 23; 223; 323 provided to the annular space 48 hydraulically unlockable check valve 4a, while in the second working line 46 one of the second pump 24; 224; 324 to the piston head space 50 opening hydraulically entprechbares check valve 5 is provided.
  • second working line 46 one of the second pump 24; 224; 324 to the piston head space 50 opening hydraulically entprechbares check valve 5 is provided.
  • Low pressure line 52 connected to each other. Between the low-pressure line 52 and the first working line 44, a non-return valve 19 opening from the low-pressure line 52 to the first working line 44 is provided. In the low pressure line 52 open via a common filter 22 and a common check valve 21 leakage lines of the two pumps 23, 24; 223, 224; 323, 324. At the low pressure line 52 is a
  • Low pressure accumulator 28 connected.
  • the low-pressure accumulator 28 is connected via a further low-pressure line 54 to the second working line 46.
  • a non-return valve 20 opening from the low-pressure accumulator 28 to the second working line 46 is provided in the further low-pressure line 54.
  • a high pressure accumulator 27 is connected via an emergency line 56 to the piston head space 50 of the Differenziaizylinders 9.
  • a flow control valve 7 and a hydraulically releasable check valve 2 are arranged in the emergency line 56, the opening direction of the high-pressure accumulator 27 is directed to the piston head space 50.
  • a pressure sensor 35 is provided on the emergency line 56 in the vicinity of the differential cylinder 9.
  • the emergency line 56 and thus the high-pressure accumulator 27 are connected via a boost line 58 to the second working line 46.
  • the boost line 48 opens in the vicinity of the Differenziaizylinders 9 in the second working line 46.
  • a standard open shut-off valve 29 a hydraulically lockable check valve 1, a throttle 6 and a check valve 15 are arranged.
  • the opening directions of the two check valves 1, 15 are directed from the high-pressure accumulator 27 to the second working line 46.
  • To the boost line 58 is in the vicinity of the high-pressure accumulator 27 a
  • Pressure sensor 37 connected.
  • the high-pressure accumulator 27 is above a
  • Parallel to a standard closed shut-off valve 8 is provided.
  • a charging line 60 is connected to the first working line 44, which opens into the boost line 58 between the shut-off valve 29 and the check valve 1.
  • a check valve 17 opening from the first working line 44 to the boost line 58 is provided in the charging line 60.
  • a pressure limiting valve 33 is arranged, via which the charging line 60 to the low pressure line 52 is relieved.
  • a hydraulically releasable check valve 3 is provided, whose
  • Opening direction of the charging line 60 is directed to the low pressure line 52.
  • the second working line 46 is connected via a pressure relief valve 10 to
  • a pressure booster 31 is provided, the input side on the one hand with the low pressure line 52 and on the other hand via a respective pressure to the translator 31st opening check valve 13, 14 is connected to the two working lines 44, 46. In this case, between the two check valves 13, 14 on the one hand and the
  • a throttle 36 and serving as a shut-off valve seat 32 is provided.
  • the annular space 48 can be connected to the low-pressure accumulator 28 via a further emergency line 62 and via a section of the further low-pressure line 54.
  • a flow control valve 34 designed as a 2/2-way valve shut-off valve 30 and a hydraulically releasable check valve 4 are arranged in the further emergency line 62, wherein the opening direction of the check valve 4 is directed from the annular space 48 to the low pressure accumulator 28.
  • the actuation of the hydraulically releasable check valves 2, 4, 4a and 5 is carried out jointly via a designed as a 3/2 way valve fail-safe valve 38.
  • the fail-safe valve 38 On the input side, the fail-safe valve 38 is supplied with control pressure medium, the optional from
  • Low-pressure accumulator 28 can be tapped.
  • the two hydraulically releasable check valves 1 and 3 can be unlocked together via a 3/2-way seat valve 12, wherein the input-side control pressure means of the 3/2-way seat valve 12 can be tapped either from the low pressure line 52 or from the charging line 60.
  • FIGS. 5 to 12 indicate the size and direction of the volume flows.
  • FIG. 6 normal operation as in FIG. 5, but with refilling function of FIG
  • High-pressure accumulator 27 At the theoretically tight seat valves used, it is possible that practically creates some leakage. This leakage leads to a decrease in the pressure in the high-pressure accumulator 27, which jeopardizes its function and thus the safety of the system. So that any leakages do not compromise safety is one
  • Recharging device consisting of the check valve 13 and 14, pressure booster 31, directional seat valve 32, throttle 36 and pressure sensor 37 executed. If an excessively low accumulator pressure is detected on the pressure sensor 37 in the normal operating mode on the high-pressure accumulator 27, the directional seat valve 32 is switched to the illustrated position. As a result, oil flows from the higher pressure side (in this case from the second working line 46 - with the Differenziaizylinder 9 retracting the first working line 44 could be the higher pressure side) via the check valve 13, the throttle 36 and the directional control valve 32 for
  • Compressor 31 In this, the volume flow with input pressure (from the second working line 46) translated into a smaller volume flow with outlet pressure and the high-pressure accumulator 27 is supplied.
  • the inlet pressure (from the second working line 46) has a pressure level corresponding to the friction of the system (at least 40 bar).
  • Input pressure forms the drive of the pressure booster 31 which has a maximum transmission ratio.
  • Pressure reducer 31 must be greater than the maximum pressure in the high-pressure accumulator 27.
  • the extension speed of the differential cylinder decreases 9.
  • the drop in speed is increased by increasing the speed of the electric motor 26th (see Figures 1 to 4) balanced. So that a small amount of oil is removed, the
  • FIG. 7 shows the maximum speed of the differential cylinder 9 in the speed boost mode.
  • the differential cylinder 9 is moved out quickly over a short distance.
  • the 3/2-way seat valve 12 is switched to the position shown.
  • the hydraulically releasable check valves 1 and 3 are unlocked. From the high-pressure accumulator 27 now oil flows through the boost line 58
  • FIG. 8 shows the minimum speed of the differential cylinder 9 in the speed boost mode. This occurs when the process is initiated as described above, wherein the direction of rotation of the electric motor 26 is reversed. Oil then flows from
  • Differenziaizylinder 9 via the check valve 5 to the pump 24; 224; 324 and thus reduces their speed.
  • the speed in the speed boost mode can be adjusted continuously between maximum speed (according to FIG. 7) and minimum speed (according to FIG. 8) by changing the direction of rotation and speed of the electric motor 26.
  • Differenziaizylinder 9 Pressure conditions in Differenziaizylinder 9 reverse, it is braked. This process can be superimposed on the pump drive. Depending on the direction of rotation of the electric motor 26, the extension movement is decelerated until the speed set by the electric motor 26 is reached and is then continued at this speed in the extension direction. In the other case, the Differenziaizylinder 9 is braked to the state and it reverses its direction of movement and then moves with that of the electric motor 26th
  • FIG. 10 shows an emergency function with maximum force. This drives the Differenziaizylinder 9. It must be ensured that the Differenziaizylinder 9 can always reach this position. For this purpose, 27 high pressure oil is stored in the high-pressure accumulator. In order to extend the Differenziaizylinder 9 in an emergency, the fail-safe valve 38 is drawn in the
  • Flow control valve 7 the speed is specified.
  • the outflowing oil flows over Flow control valve 34, shut-off valve 30 to the low pressure accumulator 28.
  • the downstream flow control valve 34 is set to a higher cylinder speed than arranged in the flow control valve 7. When the differential cylinder 9 tensile forces act the flow control valve 34, the cylinder speed.
  • Figure 1 1 shows the emergency function with low power. This is only possible if the pressure sensor 35 measures a sufficiently small pressure. , To save little oil from the
  • High-pressure accumulator 27 can be seen, the shut-off valve 30 is switched to its illustrated position. As a result, the path of the outflowing oil changes in the manner shown. The outflowing oil is thus under pressure and flows to the high-pressure accumulator 27.
  • the pressure in the differential cylinder 9 is now approximately constant. In the piston head space 50, it is slightly lower by the control pressure difference at the flow control valve 7.
  • Differential cylinder 9 extends with less force, since only the area difference A2- Aleffective. From the high-pressure accumulator 27 less oil is removed.
  • FIG. 12 shows how the
  • High-pressure accumulator 27 is reloaded.
  • the shut-off valve 30 is switched to its illustrated position and the pumps 23, 24; 223, 224; 323, 324 are driven by the electric motor 26 in a drawn manner.
  • the first pump 23, 223, 323 conveys oil to the high-pressure accumulator 27, while it is supplied by the low-pressure accumulator 28.
  • the second pump 24; 224; 324 pumps or circulates the oil without pressure.
  • Differential cylinder 9 is held in the extended position, so that the rotor blade is low in resistance and thus low in force.
  • a linear actuator with a double pump and a differential cylinder whose annular space or piston rod space of an annular surface or piston rod surface a piston is limited and connected to a first pump, and whose piston bottom space is bounded by a piston bottom surface of the piston and connected to a second pump. Both pumps are driven by a common variable speed electric motor.
  • Piston bottom surface is equal to the ratio of the delivery volume of the first pump to the delivery volume of the second pump. In a first variant, this is done by
  • Delivery volume is executed. According to a third variant, this is realized in that at the same pump speed, the ratio of the displacement volume of the pump corresponds to the ratio of the cylinder surfaces.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

L'invention concerne un mécanisme de réglage linéaire muni de deux pompes (23, 24) et d'un cylindre différentiel (9), dont l'espace de segment (48) ou l'espace de tige de piston est délimité par une surface de segment (A1) ou une surface de tige de piston d'un piston et est relié à une première pompe (23), et dont l'espace de fond de piston (50) est délimité par une surface de fond de piston (A2) du piston et est relié à une deuxième pompe (24). Les deux pompes sont entraînées par un moteur électrique commun (26) à vitesse variable. Le rapport entre la surface de segment et la surface de fond de piston est égal au rapport entre le volume de refoulement de la première pompe et le volume de refoulement de la deuxième pompe. Selon une première variante, ceci est réalisé par une adaptation des vitesses de rotation des deux pompes par une transmission (26). Selon une deuxième variante, ceci est réalisé en ce qu'une pompe présente un volume de refoulement variable. Selon une troisième variante, ceci est réalisé en ce que, pour une même vitesse de rotation des pompes, le rapport entre les volumes de compression des pompes correspond au rapport entre les surfaces de cylindre.
PCT/EP2014/057468 2013-05-13 2014-04-14 Mécanisme d'entraînement à vitesse de rotation variable muni de deux pompes et d'un cylindre différentiel WO2014183941A1 (fr)

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DE102013008047.9A DE102013008047A1 (de) 2013-05-13 2013-05-13 Drehzahlvariabler Antrieb mit zwei Pumpen und einem Differenzialzylinder

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CA3110135C (fr) 2018-08-21 2023-09-05 Siemens Energy, Inc. Actionneur hydraulique a double effet avec differentes pompes pour chaque direction d'actionnement
JP7273485B2 (ja) * 2018-11-19 2023-05-15 川崎重工業株式会社 液圧システム
DE102021113665A1 (de) * 2021-05-27 2022-12-01 HMS - Hybrid Motion Solutions GmbH Hydraulisches Antriebssystem

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Cited By (10)

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Publication number Priority date Publication date Assignee Title
WO2017063655A1 (fr) * 2015-10-14 2017-04-20 Vestas Wind Systems A/S Système de commande de calage pour le calage d'une pale d'éolienne
CN108368828A (zh) * 2015-10-14 2018-08-03 维斯塔斯风力系统集团公司 用于变桨风力涡轮机叶片的变桨控制系统
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CN108368828B (zh) * 2015-10-14 2020-05-19 维斯塔斯风力系统集团公司 用于控制变桨力系统的变桨控制系统和方法
CN106351894A (zh) * 2016-10-21 2017-01-25 燕山大学 一种开式泵控负载容腔独立控制非对称缸动力单元
DE102017106700B3 (de) 2017-03-29 2018-05-17 Voith Patent Gmbh Vorrichtung zum Regeln einer hydraulischen Maschine
DE102017106693B3 (de) 2017-03-29 2018-05-30 Voith Patent Gmbh Vorrichtung zum Regeln einer hydraulischen Maschine
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DE102022203979A1 (de) 2022-04-25 2023-10-26 Robert Bosch Gesellschaft mit beschränkter Haftung Hydraulischer Linearantrieb

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