WO2022248153A1 - Hydraulisches Antriebssystem - Google Patents
Hydraulisches Antriebssystem Download PDFInfo
- Publication number
- WO2022248153A1 WO2022248153A1 PCT/EP2022/061355 EP2022061355W WO2022248153A1 WO 2022248153 A1 WO2022248153 A1 WO 2022248153A1 EP 2022061355 W EP2022061355 W EP 2022061355W WO 2022248153 A1 WO2022248153 A1 WO 2022248153A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- hydraulic
- hydraulic machine
- drive system
- machine
- hydraulic cylinder
- Prior art date
Links
- 238000000034 method Methods 0.000 claims abstract description 27
- 238000006073 displacement reaction Methods 0.000 claims description 18
- 238000012360 testing method Methods 0.000 claims description 11
- 239000012530 fluid Substances 0.000 description 20
- 238000010276 construction Methods 0.000 description 5
- 238000013461 design Methods 0.000 description 4
- 238000011161 development Methods 0.000 description 4
- 230000018109 developmental process Effects 0.000 description 4
- 238000010521 absorption reaction Methods 0.000 description 3
- 230000032683 aging Effects 0.000 description 3
- 230000008859 change Effects 0.000 description 3
- 238000012423 maintenance Methods 0.000 description 3
- 238000007792 addition Methods 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 238000004891 communication Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000010720 hydraulic oil Substances 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000002955 isolation Methods 0.000 description 1
- 230000007257 malfunction Effects 0.000 description 1
- 239000002480 mineral oil Substances 0.000 description 1
- 235000010446 mineral oil Nutrition 0.000 description 1
- 239000003921 oil Substances 0.000 description 1
- 230000002028 premature Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000008439 repair process Effects 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
- 239000013589 supplement Substances 0.000 description 1
- 230000001360 synchronised effect Effects 0.000 description 1
- 238000009423 ventilation Methods 0.000 description 1
Classifications
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- 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
- F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
- F15B7/005—With rotary or crank input
- F15B7/006—Rotary pump input
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- 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
- F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
- F15B7/001—With multiple inputs, e.g. for dual control
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- 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
- F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
- F15B7/005—With rotary or crank input
-
- 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
- F15B1/26—Supply reservoir or sump assemblies
- F15B1/265—Supply reservoir or sump assemblies with pressurised main reservoir
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- 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
- F15B19/00—Testing; Calibrating; Fault detection or monitoring; Simulation or modelling of fluid-pressure systems or apparatus not otherwise provided for
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- 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
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- 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
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- 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
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- 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
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- 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
- F15B2211/20569—Type of pump capable of working as pump and motor
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- 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
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- 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
- F15B2211/20584—Combinations of pumps with high and low capacity
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- 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
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- 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
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- 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
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- 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
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- 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
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- 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
- F15B2211/785—Compensation of the difference in flow rate in closed fluid circuits using differential actuators
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- 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
- F15B2211/855—Testing of fluid pressure systems
Definitions
- the invention relates to a hydraulic drive system, a method for adjusting a delivery volume in a hydraulic drive system and the use of the hydraulic drive system to control a hydraulic cylinder.
- Hydraulic drive systems are used in many types of industrial applications. Hydraulic drive systems of this type can be found in forming technology plants such as presses, rolling mills and in general in the construction of hydraulic units.
- a drive system with two mechanically coupled hydraulic machines is known from publication DE 10 2010 020 690 A1. These are made by one
- the Drive system are each fluid-hydraulic connected via a hydraulic connection with a respective side of the hydraulic cylinder and thus the corresponding hydraulic cylinder surface, and with a reservoir.
- the two hydraulic machines can be arranged on the drive shaft in such a way that one of the two hydraulic machines represents the function of a pump and the other hydraulic machine acts as a motor.
- the first hydraulic machine can provide the functionality of a pump for a clockwise direction of rotation, and the second hydraulic machine acts as a motor. By changing the direction of rotation of the hydraulic machine so that it is driven counterclockwise, the first hydraulic machine takes over the functionality of a motor and the second hydraulic machine acts as a pump.
- the fixed connection of one hydraulic machine to a cylinder chamber means that when using a differential cylinder with an exemplary area ratio of 2:1, one hydraulic machine has twice the delivery volume of the other and must be designed accordingly large. This affects the space requirement and the costs of the drive system shown.
- a hydraulic drive system with a hydraulic machine in a radial piston design with a control pin is known from publication EP 292 1700 A1.
- the hydraulic machine is driven by a variable-speed motor.
- the hydraulic machine has at least three hydraulic connections, with the delivery volume of the hydraulic connections being determined by the control pin.
- the displacement is the volume of hydraulic fluid that flows through the cross-section of a component per revolution of the motor.
- a solution to the differential cylinder adjustment is solved in this publication via the named control pin of the hydraulic machine.
- the solution presented in publication EP 292 1700 A1 also poses the problem that the control pin must be precisely matched to the cylinder area ratio. As a result, the total pressure varies depending on the cylinder stroke.
- Variable displacement pumps are also known in the prior art.
- a hydraulic cylinder is operated by at least two hydraulic machines, with at least one hydraulic machine being a variable displacement pump.
- the adjustment of the stroke ring and thus the vane of the variable displacement pump is moved via a hydraulic cylinder.
- This cylinder must be pressurized and hydraulic fluid applied, necessitating a Proportional valve to control the cylinder results. This results in a high structural and construction-related effort.
- a control system is required for this cylinder, resulting in an increased energy problem since a constant pressure system is required to feed this proportional valve. Therefore, a variable displacement pump is inefficient and correspondingly complicated in terms of its structure and its supply and, due to the additional components, requires maintenance and is less reliable and expensive in terms of acquisition and maintenance, as well as repairs.
- the total pressure in the hydraulic system should remain constant in order to have maximum useful power. If the hydraulic cylinder is operated by a hydraulic drive system that has only one motor, then the volume flow that is applied to the two sides of the hydraulic cylinder must be adjusted precisely to the ratio of the two sides of the hydraulic cylinder. If, for example, a differential cylinder with an area ratio of 2:1 is operated by a hydraulic drive system, the ratio of the delivery volume at the hydraulic connections of the two hydraulic cylinder sides must also be 2:1.
- the problem that arises from this for the hydraulic drive systems known in the prior art is that the delivery volume of the hydraulic connections of the hydraulic machine(s), which are connected to the hydraulic cylinder sides, must be adapted to the hydraulic cylinder. In the prior art, this is done by selecting the two hydraulic machines or the control pin.
- the hydraulic machines here have a non-variable delivery volume.
- the delivery volume provided by the control pin is also not variable. If the hydraulic drive system is now connected to a hydraulic cylinder that does not have the volume ratio for which the hydraulic drive system is designed, at least one of the hydraulic machines or the control pin must be replaced.
- a technical task on which the invention is based can therefore be to at least partially eliminate the disadvantages recognized in the prior art and to provide a hydraulic drive system in which the delivery volume of the hydraulic machine(s) can be adapted to a hydraulic cylinder.
- this object is achieved according to a first aspect by a hydraulic drive system having the features of independent patent claim 1 .
- Advantageous developments of the hydraulic drive system result from the subclaims relating to the hydraulic drive system.
- the hydraulic drive system has a first hydraulic machine and a second hydraulic machine.
- the first hydraulic machine and the second hydraulic machine are mechanically connected to one another.
- the first hydraulic machine and the second hydraulic machine can be mechanically connected to one another via a drive shaft.
- the first hydraulic machine and the second hydraulic machine are hydraulic machines whose stroke volume can be adjusted.
- variable-speed drive can be designed as a variable-speed or variable-direction electric motor.
- variable-speed drives consist of an electric motor, a hydraulic pump and a frequency converter, the software of which continuously adjusts the motor speed depending on the load for the optimum operating point.
- an electrically driven constant pump delivers a demand-oriented volume flow in order to regulate pressure, speed, power, position or force depending on the task.
- first hydraulic machine and the second hydraulic machine are hydraulically connected to at least one first hydraulic cylinder.
- the hydraulic cylinder preferably has a first hydraulic cylinder surface and a second hydraulic cylinder surface.
- the hydraulic cylinder is preferably designed as a differential cylinder.
- the hydraulic cylinder can be designed as a synchronous cylinder.
- the first hydraulic cylinder side and the second hydraulic cylinder side of the hydraulic cylinder can each be designed both as the ring side and as the piston side of the hydraulic cylinder.
- the first hydraulic machine and/or the second hydraulic machine have an adjustable delivery volume.
- an adjustment is to be understood as a manual mechanical stroke setting.
- the delivery volume per pump revolution can be determined by means of the manual mechanical stroke setting.
- the stroke of the pistons or vanes can be set manually using this setting.
- This stroke setting leads to a change in the delivery volume per revolution. Provision is also made for the delivery volume to be mechanically adjustable.
- the stroke setting selected in this way can be locked using a mechanical fixing device. If the stroke is adjusted using an adjusting spindle, locking can take place using a counter nut.
- the delivery volume at the hydraulic connection of the first hydraulic cylinder side and the delivery volume at the hydraulic connection of the second hydraulic cylinder side can thus be adjusted to the volume ratio of the first hydraulic cylinder side and the second hydraulic cylinder side.
- the delivery volume can be set ideally to the cylinder area ratio. A total pressure increase over the cylinder stroke and thus a reduction in useful power can be avoided. Furthermore, it is advantageous that the delivery volume only has to be mechanically adjusted once according to a first adjustment parameter. There is no need for permanent adjustment.
- the present invention provides a reliable and energy-efficient hydraulic drive system by suppressing the system pressure increase, especially in differential cylinders.
- a ratio of the delivery volume of the first hydraulic machine and the second hydraulic machine can be mechanically adjusted to an area ratio of the first hydraulic cylinder area and the second hydraulic cylinder area.
- the ratio of the delivery volume of the first hydraulic machine to the delivery volume of the second hydraulic machine should correspond to the area ratio of the two sides of the hydraulic cylinder.
- the volume flow Q in the hydraulic drive system is provided via the variable speed of the first and the second hydraulic machine and the displacement volume is adjusted via the adjustment parameter.
- the delivery volume corresponds to the volume of hydraulic fluid that is moved in the hydraulic drive system per unit of time.
- the adjustment parameter can be, for example be determined with a method according to the further aspect of the present invention.
- the specific adjustment parameter (specific) results with reference to the connected cylinder. This is determined and set for the cylinder used.
- the specific adjustment parameter results from the area ratio of the cylinder surfaces of the cylinder .
- first hydraulic cylinder area and the second hydraulic cylinder area are different.
- differential cylinders are used that are designed with only one piston rod. This can lead, for example, to a shorter overall length, to a greater force that can be achieved on the piston side and to a simplified seal design on the hydraulic cylinder. It is known that approximately 80% of the hydraulic cylinders used in practice are designed as differential cylinders.
- the first hydraulic machine and/or the second hydraulic machine is selected from a group of pumps which has at least one displacement pump.
- the hydraulic machine can be designed, for example, as an axial piston pump, radial piston pump or vane pump, gear pump, spindle pump and the like.
- the manually adjustable pump is designed as a positive displacement pump, in particular an axial piston pump, radial piston pump, or vane pump.
- the axial piston pump is used in hydraulics to convert mechanical energy into hydraulic energy.
- the volume flow can be adjusted using the axial piston pump.
- the working pistons of the radial piston pump are arranged radially and perpendicularly to the drive shaft.
- the radial piston pump is characterized by its high level of efficiency.
- the vane pump is a displacement pump with a hollow cylinder in which another cylinder rotates.
- the delivery volume is mechanically adjustable and/or adjustable.
- the second hydraulic machine is connected to the second hydraulic cylinder surface of the hydraulic cylinder.
- the second hydraulic machine is preferably connected to a first connection with the second hydraulic cylinder surface of the hydraulic cylinder.
- the volume flow can be made structurally smaller by means of this configuration, the volume of the first hydraulic machine of the hydraulic drive system.
- the structure of the first hydraulic machine is correspondingly smaller and thus more cost-effective and less maintenance-intensive and/or prone to errors and malfunctions.
- the first hydraulic machine is connected to the first hydraulic cylinder surface of the hydraulic cylinder.
- the first hydraulic machine is preferably connected to the first hydraulic cylinder surface of the hydraulic cylinder with a first connection.
- the volume of the first hydraulic machine is designed to be smaller.
- the first hydraulic machine has two connections, one of which can be subjected to the entire working pressure.
- the first hydraulic machine is connected to a reservoir of the hydraulic drive system.
- the first Hydraulic machine connected via a second port to a reservoir of the hydraulic drive system.
- the second hydraulic machine is hydraulically connected to the first hydraulic cylinder surface.
- the second hydraulic machine is preferably hydraulically connected to the first hydraulic cylinder surface via a second connection.
- the reservoir is configured to supply additional hydraulic fluid for the hydraulic drive system according to need.
- a suction valve can be provided between the first hydraulic machine and the reservoir. Since the second hydraulic machine is intended to be connected to the first hydraulic cylinder side and the second hydraulic cylinder side, the second hydraulic machine conveys the hydraulic fluid between the two hydraulic cylinder sides, depending on the direction of rotation, from the first hydraulic cylinder side to the second hydraulic cylinder side or from the second hydraulic cylinder side to the first hydraulic cylinder side.
- the first hydraulic machine can be provided to compensate only for the volume ratio of the first hydraulic cylinder side and the second hydraulic cylinder side.
- the required delivery volume of the first hydraulic machine is therefore lower compared to an embodiment in which the second hydraulic machine is not connected to the first hydraulic cylinder side.
- the first hydraulic machine can thus be smaller, which reduces the space for installation and construction and thus the associated technical complexity and costs.
- the second hydraulic machine is hydraulically connected to a reservoir of the hydraulic drive system.
- the second hydraulic machine is preferably hydraulically connected to a reservoir of the hydraulic drive system via a second connection.
- the second connection of the second hydraulic machine is preferably always connected to the reservoir.
- a hydraulic machine can thus be provided comprising a pressure connection.
- the internal structure of the hydraulic machine can be designed in a simplified manner.
- the first The hydraulic machine in contrast to the simplified second hydraulic machine, must provide the complete volume flow requirement of the first cylinder chamber and must therefore be designed to be larger.
- the reservoir can be designed as a tank without excess pressure.
- the reservoir can be under an overpressure.
- the reservoir 6 can be designed as a prestressed reservoir.
- the overpressure can preferably be in a range of 2-25 bar, particularly preferably in a range of 2-10 bar.
- an increased intake of the first hydraulic machine and the second hydraulic machine is made possible.
- this construction results in an advantageous manner in that the hydraulic medium (for example hydraulic fluid) can be separated from the atmosphere and aging of the hydraulic medium can thus be counteracted.
- the prestressed reservoir 6 is subjected to a pressure in a fluctuation range of preferably 22 bar, more preferably 14 bar.
- the hydraulic pumps can advantageously be operated in this fluctuation range without their sealing quality and/or quality being reduced. Furthermore, the hydraulic pumps are operated in an area in which the load limits of the pump housing are observed in order to prevent damage.
- first hydraulic machine and the second hydraulic machine have at least one high-pressure connection.
- the first hydraulic machine or the second hydraulic machine has at least one high-pressure connection.
- a hydraulic connection of the first hydraulic machine and a hydraulic connection of the second hydraulic machine which is connected either to the first hydraulic cylinder side or to the second hydraulic cylinder side, can be designed as a high-pressure connection.
- the first hydraulic machine and/or the second hydraulic machine have a low-pressure connection.
- a hydraulic connection of the first hydraulic machine and a hydraulic connection of the second hydraulic machine with connected to the reservoir can be designed as a low-pressure connection.
- a high-pressure line can be connected via the high-pressure connection.
- a high-pressure line for connection to the hydraulic cylinder can be connected to the high-pressure connection.
- the low pressure port may be permanently connected to a tank line and provide hydraulic communication to the reservoir.
- the first hydraulic machine and/or the second hydraulic machine have a high- and low-pressure accumulator.
- the first hydraulic machine is connected to the second hydraulic cylinder side of the hydraulic cylinder and the second hydraulic machine is connected to the first hydraulic cylinder side of the hydraulic cylinder.
- the first hydraulic machine and/or the second hydraulic machine have a high- and low-pressure accumulator.
- the first hydraulic machine is connected to the first hydraulic cylinder side of the hydraulic cylinder and the second hydraulic machine is connected to the second hydraulic cylinder side of the hydraulic cylinder.
- the present invention relates to a method for adjusting a delivery volume of a hydraulic drive system with the features of independent patent claim 12. Advantageous developments of the method result from the subclaims relating to the method.
- the method for adjusting a delivery volume in a hydraulic drive system with a first hydraulic machine and/or a second hydraulic machine comprises the following steps:
- this includes the further step:
- Delivery volume can be checked to see whether it meets the requirements of the hydraulic drive system.
- the delivery volume is adjusted by setting an adjustment element with the specific first adjustment parameter.
- the adjustment element is preferably fixed via a counter element.
- the delivery volume of one of the hydraulic machines can be adjusted and thus changed in an efficient manner via the adjusting element. Furthermore, with the present invention, the delivery volume only has to be changed/set once via the adjusting element and can be fixed to this setting by using a counter element.
- the adjusting element is designed at least as a threaded spindle, as a threaded bolt or as a threaded screw.
- the adjusting element can be designed as a corresponding account nut.
- the present invention relates to a hydraulic
- FIG. 1 shows a first embodiment of the hydraulic drive system according to the present invention
- FIG. 2 shows another embodiment of the hydraulic drive system according to the present invention.
- FIG. 3 shows a flow chart of an embodiment of a method according to the present invention.
- the hydraulic drive system 1 comprises a first hydraulic machine 2 and a second hydraulic machine 3.
- the first hydraulic machine 2 and the second hydraulic machine 3 are driven jointly by a variable-speed drive 4 via a shaft.
- Preferably the first Hydraulic machine 2 and the second hydraulic machine are mechanically connected to one another. The mechanical connection can be made via a shaft.
- the first hydraulic machine 2 and the second hydraulic machine 3 are designed as constant pumps.
- the first hydraulic machine 2 is hydraulically connected to a reservoir 6 .
- a suction valve (not shown) can be interposed between the first hydraulic machine 2 and the reservoir 6 .
- a reservoir 6 (compensating tank) is to be understood as meaning a tank which receives the hydraulic oil or the hydraulic medium of the hydraulic drive system 1 .
- the hydraulic fluid or the hydraulic medium can be a special mineral oil.
- the reservoir 6 is intended to store the hydraulic fluid, but otherwise keeps it unpressurized.
- the reservoir is to be understood as a tank without overpressure. As a result, the reservoir 6 can be filled and emptied without risk.
- the reservoir 6 is designed as a closed container which is connected to the surrounding air via ventilation valves. This connection is required so that pressure equalization can take place. Otherwise, returning hydraulic fluid or the hydraulic medium would generate an overpressure and leaking hydraulic fluid would generate a negative pressure.
- the closed system can ensure that no cavitation occurs and thus the quality of the hydraulic medium (e.g. oil) remains the same and that it does not age and/or ages less quickly. This reduces premature replacement and/or maintenance intervals.
- the hydraulic medium e.g. oil
- the reservoir 6 can be designed to be under an overpressure.
- the reservoir 6 can be designed as a prestressed reservoir.
- An overpressure in a range of 2-25 bar, particularly preferably in a range of 2-10 bar, can preferably be provided.
- a positive pressure reservoir allows for increased suction through the first hydraulic machine and the second hydraulic machine. Furthermore, this structure allows the hydraulic medium to be separated from the atmosphere and thus counteract aging of the hydraulic medium.
- the prestressed reservoir 6 with a pressure in a fluctuation range of preferably 22 bar, more preferably from 14 bar applied.
- the hydraulic pumps can advantageously be operated in this fluctuation range without their sealing quality and/or quality being reduced. Furthermore, the hydraulic pumps are operated in an area in which the load limits of the pump housing are observed in order to prevent damage.
- the first hydraulic machine 2 and the second hydraulic machine 3 are hydraulically connected to a first hydraulic cylinder side 5a of a hydraulic cylinder 5 .
- the second hydraulic machine 3 is hydraulically connected to the second hydraulic cylinder side 5b of the hydraulic cylinder 5 .
- variable-speed drive 4 drives the first hydraulic machine 2 and the second hydraulic machine 3
- first hydraulic machine 2 delivers hydraulic fluid from the reservoir 6 into the first hydraulic cylinder side 5a of the hydraulic cylinder and the second hydraulic machine 3 Hydraulic fluid from the second hydraulic cylinder side 5b of the hydraulic cylinder 5 into the first hydraulic cylinder side 5a of the hydraulic cylinder 5.
- the piston of the hydraulic cylinder 5 is extended.
- the first hydraulic machine 2 delivers hydraulic fluid from the first hydraulic cylinder side 5a of the hydraulic cylinder 5 into the reservoir 6 and the second hydraulic machine 3 delivers hydraulic fluid from the first hydraulic cylinder side 5a of the hydraulic cylinder into the second hydraulic cylinder side 5b of the hydraulic cylinder 5.
- the piston of the hydraulic cylinder 5 is retracted.
- the delivery volume in the hydraulic drive system 1 can be controlled via the speed of the speed-variable drive 4 .
- the first hydraulic machine 2 only has to compensate for the volume ratio of the first hydraulic cylinder side 5a and the second hydraulic cylinder side 5b.
- the delivery volume of the first hydraulic machine 2 can thus be smaller than in other arrangements.
- the first hydraulic machine 2 can thus be designed to be smaller in terms of its construction.
- the fixed displacement of the first hydraulic machine 2 and / or the second Hydraulic machine 3 changed.
- the delivery volume can be adjusted via the eccentricity of the stroke ring. This leads to an adjustment of the stroke of the pistons or vanes and thus to a change in the delivery volume per pump revolution.
- the eccentricity of the stroke ring can be adjusted and the delivery volume per pump revolution can be adjusted and fixed via a spindle provided accordingly.
- the stroke setting can be locked using a mechanical fixation. If the stroke is adjusted using an adjusting spindle, locking can take place using a counter nut.
- variable displacement pumps have the disadvantage that the control system requires a considerable amount of additional work.
- control pistons which are subjected to a corresponding pressure or hydraulic fluid, which requires an additional proportional valve to regulate the pressure in the control piston.
- a path measuring system is provided to record the position.
- a control system is required to supply the proportional valve. This represents a considerable additional expense.
- the present invention is simpler to implement in terms of its structure and, moreover, more reliable due to the smaller number of components to be supplied.
- the control of the hydraulic drive system is designed to be more efficient and simple, since the delivery volume only has to be set or adjusted once.
- the delivery volume of the second hydraulic machine 3 can be matched to the hydraulic cylinder/area ratio by adjusting the extrinsity of the stroke ring.
- the pumped volume flow in the hydraulic drive system 1 via the speed of the first and second hydraulic machine 2, 3.
- At least one of the hydraulic machines 2, 3 is preferably designed as an axial piston pump, radial piston pump or vane pump and has a manual mechanical stroke setting for the delivery volume.
- the additional hydraulic machine 2, 3 can be designed as a fixed displacement pump or as an adjustable fixed displacement pump.
- the volume of the first hydraulic machine 2 can be smaller than in comparison to the first hydraulic machine 2 used in the embodiment shown in FIG. 2.
- the first hydraulic machine 2 in FIG. 1 can thus be made correspondingly smaller and is reflected in a cost-effective use.
- the second hydraulic machine shown in FIG. 1 has two connections, both of which can be subjected to full working pressure.
- the second hydraulic machine 3 has the adjustment 7 .
- the adjustment 7 is designed to adjust an adjustable delivery volume for the first hydraulic machine 2 and/or the second hydraulic machine 3 .
- the delivery volume can be adjusted mechanically via the adjustment 7 .
- the second hydraulic machine 3 has the adjustment 7 .
- the stroke of the pistons or vanes can be adjusted manually via the adjustment 7 , for example in the case of piston pumps and vane pumps by adjusting the adjustment 7 .
- This stroke setting leads to a change in the delivery volume per revolution.
- the adjustment 7 can be changed with respect to the adjustment according to the determined first adjustment parameter by turning it in or out.
- the adjustment 7 can be locked by means of a mechanical fixing device. This mechanical fixing device can be designed as a counter nut screwed onto the adjustment 7 .
- the hydraulic drive system 1 comprises a first hydraulic machine 2 and a second hydraulic machine 3.
- the first hydraulic machine 2 and the second hydraulic machine 3 are driven together, for example as shown, via a shaft by a variable-speed drive 4.
- the first Hydraulic machine 2 is hydraulically connected to a first hydraulic cylinder side 5a of a hydraulic cylinder 5 .
- the second hydraulic machine 3 is hydraulically connected to a second hydraulic cylinder side 5b of a hydraulic cylinder 5 .
- the first hydraulic machine 2 and the second hydraulic machine 3 are each connected to a reservoir 6 .
- a suction valve can be provided between the first hydraulic machine 2 and the reservoir 6 and between the second hydraulic machine 3 and the reservoir 6 .
- the first hydraulic machine 2 and the second hydraulic machine 3 are jointly connected to the reservoir 6 via an anti-cavitation valve.
- variable-speed drive 4 drives the first hydraulic machine 2 and the second hydraulic machine 3
- the first hydraulic machine 2 delivers hydraulic fluid from the reservoir 6 into the first hydraulic cylinder side 5a of the hydraulic cylinder 5 and the second hydraulic machine 3 conveys hydraulic fluid from the second hydraulic cylinder side 5b of the hydraulic cylinder 5 into the reservoir 6.
- the piston is moved into an end position, for example the piston of the hydraulic cylinder 5 is extended.
- the drive 4 drives the first hydraulic machine 2 and the second hydraulic machine 3 in the direction other than that described above, the first hydraulic machine 2 delivers hydraulic fluid from the first hydraulic cylinder side 5a of the hydraulic cylinder 5 into the reservoir 6 and the second hydraulic machine 3 delivers hydraulic fluid the second hydraulic cylinder side 5b of the hydraulic cylinder 5 into the reservoir 6.
- the piston of the hydraulic cylinder 5 is retracted.
- the delivery volume (volume) in the hydraulic drive system 1 is controlled by the adjustment parameter.
- the interconnection of the first hydraulic machine 2 and the second hydraulic machine 3, as shown in Figures 1 and 2, when using a differential cylinder with an example area ratio of 2: 1 results in the first hydraulic machine 2 and the second hydraulic machine 3 having the same delivery volume and thus compared to the prior art mentioned at least one hydraulic machine can be made smaller, which leads to a smaller space requirement and lower economic costs.
- the conveyed volume flow can be changed by changing the speed of the primary drive influenced and thus the process speed of the hydraulic cylinder 5 can be changed.
- the 4-quadrant stage can be operated in a 4-quadrant mode with positive torque and positive direction of rotation, with positive torque and negative direction of rotation, with negative torque and positive direction of rotation and with negative torque and negative direction of rotation.
- the volume of the first hydraulic machine 2 is smaller compared to the first hydraulic machine in FIG. 1.
- the second hydraulic machine 2 has two connections, only one of which is subjected to the full working pressure.
- the second connection of the second hydraulic machine 3 is preferably always in fluid connection with the reservoir 6 .
- the second hydraulic machine 3 can thus be designed to be provided with only one pressure connection.
- the first hydraulic machine 2 now provides the complete volume flow requirement of the first cylinder chamber and is therefore larger in comparison to the embodiment of FIG. 1.
- the reservoir 6 can be designed as a tank without excess pressure.
- the reservoir 6 can also be designed as a reservoir under an overpressure.
- Fig. 3 shows a flowchart of a method 10 for adjusting a delivery volume in a hydraulic drive system 1.
- the hydraulic drive system 1 has a first hydraulic machine 2 and a second hydraulic machine 3 on.
- the method shown in FIG. 3 can include the following method steps S1-S3.
- a first step S1 an area ratio between a first hydraulic cylinder surface 5a and a second hydraulic cylinder surface 5b of a hydraulic cylinder 5 of the hydraulic drive system 1 is determined.
- a target delivery volume of the first hydraulic machine and/or the second hydraulic machine of the hydraulic drive system 1 is determined.
- a first adjustment parameter of the first hydraulic machine 2 and/or the second hydraulic machine 3 is determined.
- the delivery volume of the first hydraulic machine 2 and/or the second hydraulic machine 3 of the hydraulic drive system 1 is adjusted using the determined first adjustment parameter.
- the delivery volume of the hydraulic drive system 1 is adjusted by adjusting the delivery volume of the first hydraulic machine 2 and the second hydraulic machine 3 .
- the method comprises a further step.
- the further step includes testing the first hydraulic machine 2 and/or the second hydraulic machine 3 on a test bench.
- the first hydraulic machine 2 and/or the second hydraulic machine 3 can be tested by means of a test run. Testing can be used to determine whether the adjusted delivery volume corresponds to the area ratio of the hydraulic cylinder.
- the delivery volume is adjusted by setting an adjustment element, preferably a threaded spindle, threaded bolt or a threaded screw with the specific first adjustment parameter. Provision is preferably made to fix the adjusting element by means of a counter element, preferably a counter nut.
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- Engineering & Computer Science (AREA)
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Abstract
Description
Claims
Priority Applications (2)
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CN202280037995.1A CN117396679A (zh) | 2021-05-27 | 2022-04-28 | 液压驱动系统 |
EP22726613.7A EP4348063A1 (de) | 2021-05-27 | 2022-04-28 | Hydraulisches Antriebssystem |
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DE102021113665.2 | 2021-05-27 | ||
DE102021113665.2A DE102021113665A1 (de) | 2021-05-27 | 2021-05-27 | Hydraulisches Antriebssystem |
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PCT/EP2022/061355 WO2022248153A1 (de) | 2021-05-27 | 2022-04-28 | Hydraulisches Antriebssystem |
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EP (1) | EP4348063A1 (de) |
CN (1) | CN117396679A (de) |
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Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
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JP2002039110A (ja) * | 2000-07-27 | 2002-02-06 | Kobelco Contstruction Machinery Ltd | 油圧シリンダ回路 |
DE102010020690A1 (de) | 2010-05-15 | 2011-11-17 | Robert Bosch Gmbh | Hydraulisches Antriebssystem |
DE102011056894A1 (de) * | 2011-05-06 | 2012-11-08 | Internationale Hydraulik Akademie Gmbh | Hydraulischer Linearantrieb |
DE102013008047A1 (de) * | 2013-05-13 | 2014-11-13 | Robert Bosch Gmbh | Drehzahlvariabler Antrieb mit zwei Pumpen und einem Differenzialzylinder |
EP2857696A1 (de) * | 2012-05-24 | 2015-04-08 | Hitachi Construction Machinery Co., Ltd. | Hydraulisches geschlossenes umlaufsystem |
EP2921700A1 (de) | 2014-03-21 | 2015-09-23 | MOOG GmbH | Hydrostatische Radialkolbenmaschine mit drei hydraulischen Anschlüssen und Steuerfenstern zur Ansteuerung eines Differentialzylinders |
WO2020105560A1 (ja) * | 2018-11-19 | 2020-05-28 | 川崎重工業株式会社 | 液圧システム |
Family Cites Families (2)
Publication number | Priority date | Publication date | Assignee | Title |
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DE102013003338A1 (de) | 2013-02-27 | 2014-08-28 | Man Truck & Bus Ag | Antriebssystem für ein Kraftfahrzeug mit verstellbarer Konstant-Pumpeneinrichtung |
DE102013212937A1 (de) | 2013-07-03 | 2014-07-10 | Voith Patent Gmbh | Vorrichtung zum Öffnen und Schließen der Leitschaufeln einer hydraulischen Maschine |
-
2021
- 2021-05-27 DE DE102021113665.2A patent/DE102021113665A1/de active Pending
-
2022
- 2022-04-28 EP EP22726613.7A patent/EP4348063A1/de active Pending
- 2022-04-28 WO PCT/EP2022/061355 patent/WO2022248153A1/de active Application Filing
- 2022-04-28 CN CN202280037995.1A patent/CN117396679A/zh active Pending
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2002039110A (ja) * | 2000-07-27 | 2002-02-06 | Kobelco Contstruction Machinery Ltd | 油圧シリンダ回路 |
DE102010020690A1 (de) | 2010-05-15 | 2011-11-17 | Robert Bosch Gmbh | Hydraulisches Antriebssystem |
DE102011056894A1 (de) * | 2011-05-06 | 2012-11-08 | Internationale Hydraulik Akademie Gmbh | Hydraulischer Linearantrieb |
EP2857696A1 (de) * | 2012-05-24 | 2015-04-08 | Hitachi Construction Machinery Co., Ltd. | Hydraulisches geschlossenes umlaufsystem |
DE102013008047A1 (de) * | 2013-05-13 | 2014-11-13 | Robert Bosch Gmbh | Drehzahlvariabler Antrieb mit zwei Pumpen und einem Differenzialzylinder |
EP2921700A1 (de) | 2014-03-21 | 2015-09-23 | MOOG GmbH | Hydrostatische Radialkolbenmaschine mit drei hydraulischen Anschlüssen und Steuerfenstern zur Ansteuerung eines Differentialzylinders |
WO2020105560A1 (ja) * | 2018-11-19 | 2020-05-28 | 川崎重工業株式会社 | 液圧システム |
Also Published As
Publication number | Publication date |
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EP4348063A1 (de) | 2024-04-10 |
DE102021113665A1 (de) | 2022-12-01 |
CN117396679A (zh) | 2024-01-12 |
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