EP3012463A1 - Agregat hydraulique - Google Patents

Agregat hydraulique Download PDF

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Publication number
EP3012463A1
EP3012463A1 EP15188200.8A EP15188200A EP3012463A1 EP 3012463 A1 EP3012463 A1 EP 3012463A1 EP 15188200 A EP15188200 A EP 15188200A EP 3012463 A1 EP3012463 A1 EP 3012463A1
Authority
EP
European Patent Office
Prior art keywords
hydraulic circuit
pressure
fluid
hydraulic
line
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP15188200.8A
Other languages
German (de)
English (en)
Other versions
EP3012463B1 (fr
Inventor
Johann Auer
Johann Schmollngruber
Hans-Wilhelm Weiss
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Weber Hydraulik GmbH
Original Assignee
Weber Hydraulik GmbH Austria
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Publication date
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Publication of EP3012463A1 publication Critical patent/EP3012463A1/fr
Application granted granted Critical
Publication of EP3012463B1 publication Critical patent/EP3012463B1/fr
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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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
    • 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
    • F15B11/022—Systems essentially incorporating special features for controlling the speed or actuating force of an output member in which a rapid approach stroke is followed by a slower, high-force working stroke
    • 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
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/042—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in"
    • F15B11/0426—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in" by controlling the number of pumps or parallel valves switched on
    • 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
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or 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
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/165—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for adjusting the pump output or bypass in response to demand
    • 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
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/166—Controlling a pilot pressure in response to the load, i.e. supply to at least one user is regulated by adjusting either the system pilot pressure or one or more of the individual pilot command pressures
    • 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
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2221—Control of flow rate; Load sensing arrangements
    • E02F9/2239—Control of flow rate; Load sensing arrangements using two or more pumps with cross-assistance
    • 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
    • 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
    • F15B2211/20576—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
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • F15B2211/20584—Combinations of pumps with high and low 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
    • F15B2211/20576—Systems with pumps with multiple pumps
    • F15B2211/20592—Combinations of pumps for supplying high and low 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
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/25—Pressure control functions
    • F15B2211/251—High pressure control
    • 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
    • F15B2211/25—Pressure control functions
    • F15B2211/252—Low pressure control
    • 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
    • F15B2211/255—Flow control functions
    • 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
    • F15B2211/2654—Control of multiple pressure sources one or more pressure sources having priority
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/3059—Assemblies of multiple valves having multiple valves for multiple output members
    • F15B2211/30595—Assemblies of multiple valves having multiple valves for multiple output members with additional valves between the groups of valves for multiple output members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
    • F15B2211/3157—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line
    • F15B2211/31582—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line having multiple pressure sources and a single 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
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional control characterised by the type of actuation actuated by fluid 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
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or 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
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40523—Flow control characterised by the type of flow control means or valve with flow dividers
    • F15B2211/4053—Flow control characterised by the type of flow control means or valve with flow dividers using valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/426—Flow control characterised by the type of actuation electrically or electronically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/428—Flow control characterised by the type of actuation actuated by fluid 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
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50536—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using unloading valves controlling the supply pressure by diverting fluid to the return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5157—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and a return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/528—Pressure control characterised by the type of actuation actuated by fluid 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
    • F15B2211/63—Electronic controllers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders

Definitions

  • the invention relates to a hydraulic unit with at least two pressure connections according to the preamble of claim 1 and a method for demand-based supply of one or more hydraulically drivable devices with hydraulic fluid by means of a hydraulic unit according to the preamble of claim 13.
  • Hydraulic power units are already known from the prior art, to which one or more hydraulic devices can be connected, which are operated independently of each other and are also claimed with varying working resistances.
  • such hydraulic units are often used to drive hydraulic recovery equipment, especially with internal combustion engine drive, as they allow a mobile and independent use of such devices. Since only the device with the lower working resistance is driven in a simultaneous operation of two devices on a hydraulic circuit, each hydraulic connection has its own hydraulic circuit with its own pump associated with such hydraulic units.
  • the directional control valves have a spring acting in the direction of a starting position and from the first hydraulic circuit or the second hydraulic circuit, a first control line to a first directional control valve acting on the first actuator and from the second hydraulic circuit or from the first hydraulic circuit, a second control line to one on the second Directional valve acting second actuator extends, the demand-based bypassing hydraulic fluid from a hydraulic circuit to another hydraulic circuit without intervention of an operator is possible and thereby greatly facilitates the handling of such a hydraulic unit.
  • first and / or the second control line is designed as a hydraulic control line and acts directly or by means of an actuating member in the form of a pilot valve on the second or first directional control valve.
  • the switching operations can be triggered in a reliable manner, since the pressure in the individual hydraulic circuits provides clues for the respective operating state of a device.
  • the first and / or second control line is designed as an electrical control line and by means of an electromagnetic actuator, in particular a magnetic coil, directly or via a pilot control element, e.g. Pilot valve acts on the second or first directional control valve.
  • an electromagnetic actuator in particular a magnetic coil
  • pilot valve acts on the second or first directional control valve.
  • the operating state of the connected devices may be e.g. be actively selected or determined by arranged at these switches or sensors and used as a basis for switching operations.
  • the switching signals can also be converted and processed using a logic circuit.
  • the first pumping elements comprise at least one high pressure element with smaller flow and at least one low pressure element with a larger flow rate and the second pumping elements comprise at least one high pressure element with smaller flow and at least one low pressure element with larger flow and the Directional valves are arranged in the outgoing of the low-pressure elements fluid lines.
  • the pressure level in the connected devices increases, the volume flow supplied to them can be reduced and thus the required power to the maximum power of the drive be adjusted.
  • the switching of the various pressure stages can, as known from the prior art by means of pressure-controlled directional control valves.
  • the delivery rate of the low pressure elements of a hydraulic circuit is at least twice the delivery rate of the high pressure elements of the same hydraulic circuit.
  • a possible embodiment of the hydraulic unit is that in the initial position of the directional control valves of these a flow path from the respective fluid line of a hydraulic circuit is open to the connection line to the other hydraulic circuit.
  • a volume flow of hydraulic fluid from one hydraulic circuit is diverted to another hydraulic circuit and this volume flow is brought back to a certain extent only when the pressure rises.
  • first connecting line extends from the first directional control valve to the second directional control valve and the second connecting line extends from the second directional control valve to the first directional control valve
  • the second directional control valve has a flow path from the first connecting line in a first switching position to a second fluid line leading to the second pressure connection or can produce in a further switching position to the fluid container and the first directional control valve can produce a flow path from the second connecting line in a first switching position to a first fluid line leading to the first pressure port or in a further switching position to the fluid container.
  • a hydraulic circuit comprises at least two high-pressure elements, of which at least one is connected via a fluid line directly to the pressure port and at least one via the directional control valve can be connected to another hydraulic circuit.
  • this design can both In the low-pressure range as well as in the high-pressure range, demand-oriented and performance-optimized allocation of the volume flows takes place.
  • a coordinated alternate operation of the equipment can also be done without its own operator for the hydraulic unit.
  • One possibility for a changeover of the operating mode could be that a signal for the resetting of the volume flow diversion is generated by the device not supplied with hydraulic fluid by means of a switch and an electrical control line, whereby a simultaneous supply of both devices is again provided.
  • One way to achieve an operation with multiple pressure levels is that in one of the fluid lines of a hydraulic circuit downstream of a pumping element, a pressure changeover valve is arranged, which is driven via an outgoing from another fluid line of the same hydraulic circuit pressure control line, thereby increasing pressure in the other Fluid line from the pressure changeover valve, a flow path from the pumping element to the fluid container is made.
  • the high pressure flow rate can be reduced as needed in a simple manner and the power of the drive can be optimally utilized.
  • the object of the invention is also achieved by a method for supplying one or more hydraulically driven devices, in particular hydraulic rescue devices, with hydraulic fluid by means of a hydraulic unit with at least two pressure connections according to claim 13, wherein in a first hydraulic circuit with a first pump arrangement by means of first fluid lines Volume flows of at least two first pumping elements are combined and directed to a first pressure port and in a second hydraulic circuit with second pumping means by second fluid lines, the volume flows of at least two second pumping elements combined and passed to a second pressure port, wherein the first pumping elements and the second pumping elements be driven by a common drive at the same time and wherein, if necessary, the allocation of the volume flows to the pressure ports by means of a first directional valve at least one of first fluid lines via a first connecting line to a second fluid line in the second hydraulic circuit is connected and by means of a second directional valve at least one of the second fluid lines via a second connecting line to a first fluid line in the first hydraulic circuit is connected, characterized in that the directional control valves by means
  • each of the devices is automatically supplied with about half or a corresponding proportion of the total delivery volume, with only one activated device this is approximately supplied to the total delivery volume.
  • Fig. 1 shows a simplified and schematic diagram of a hydraulic unit 1 for demand-based supply of two or more hydraulically driven devices.
  • the hydraulic unit 1 has for this purpose at least two pressure ports 2 and 3 and can on the in Fig. 1 Left pressure port 2, a first device 4, for example in the form of a mountain scissors, a spreading cylinder or a spreading device to be connected.
  • a first device 4 for example in the form of a mountain scissors, a spreading cylinder or a spreading device to be connected.
  • Fig. 1 is shown with dashed lines and a second device 5, which can be connected to the right-hand pressure port 3.
  • the devices 4, 5 each have a fluid supply 6, through which the supplied from the pressure ports 2, 3 volume flow is supplied and further each have a fluid return 7, with which a volume flow is again supplied to the hydraulic unit 1.
  • the hydraulic unit 1 comprises two indicated by dotted lines hydraulic circuits 8 and 9, of which hydraulic fluid 10 removed from a fluid container 11 and the pressure ports 2, 3 is supplied.
  • the first hydraulic circuit 8 comprises a first pump arrangement 12, which consists of at least two pumping elements 13 and 14.
  • the second hydraulic circuit 9 comprises a second pump arrangement 15 which comprises at least two pumping elements 16 and 17.
  • the pumping elements 13, 14, 16, 17 are based on the displacement principle and can thereby build very high pressures, for example up to 1000 bar.
  • the pumping elements 13, 14, 16, 17 and possibly further pumping elements may be part of a hydraulic pump in the form of a radial piston pump, axial piston pump or similar pump types with a plurality of displacement elements.
  • the pumping elements 13, 14 of the first pump arrangement 12 and the pumping elements 16, 17 of the second pumping arrangement 15 are driven by a common drive 18, wherein the drive 18 may comprise, for example, an electric motor.
  • the drive 18 may comprise, for example, an electric motor.
  • the volume flows generated by the first pumping elements 13 and 14 are guided via first fluid lines 20 and 21 to the first pressure port 2, wherein the at least two first fluid lines 20 and 21 can be combined in a first manifold 22 before the first pressure port 2.
  • the volume flows generated by the second pumping elements 16 and 17 are led via second fluid lines 23 and 24 to the second pressure port 3, wherein here, the second fluid lines 23 and 24 may be performed before the second pressure port 3 to a second manifold 25 together.
  • the fluid lines 20, 21 and 23, 24 are shown in the form of arrows to illustrate the guided through them volume flows.
  • the volumetric flow of the first pump arrangement 12, ie the first pumping elements 13 and 14, is provided at the first pressure connection 2 for the first device 4 and, analogously, at the second pressure connection 3 for the second device 5 the volumetric flow of the second pump arrangement 15, So the second pumping elements 16 and 17 is provided.
  • no device 4, 5 is connected to one of the pressure ports 2, 3, it must be ensured by measures known from the prior art that the volume flows generated by the pumping elements 13, 14, 16, 17 return to the fluid reservoir without damaging the hydraulic unit 1 11 are supplied.
  • This can be, for example, a pressure relief valve arranged upstream of the pressure connections 2, 3, which is actuated manually and the volume flows are supplied to the pressure connections 2, 3 only after connection of a device 4 or 5.
  • the power converted in a hydraulic circuit 8 or 9 is proportional to the product of the size of the volume flow and the height of the fluid pressure. Since the power of the drive 18, for example, an internal combustion engine used in the hydraulic unit 1 19 is limited, and the adjustable at the pressure ports 2 and 3 available flow at a certain pressure is limited upwards. At low back pressure by the connected device 4 or 5, the volume flow is additionally limited by the highest drive speed of the drive 18, for example by the maximum speed of the engine 19, upwards. In practice, however, a largely constant drive speed can be assumed, for which reason a largely constant total delivery quantity is supplied by the pump arrangements 12, 15 and, adapted to the available drive power, they have to be divided into volume flows with different pressure levels.
  • the first hydraulic circuit 8 has a first directional valve 26, with which the first fluid line 21 can be connected via a first connecting line 27 to a second fluid line 24 in the second hydraulic circuit 9.
  • a second directional control valve 28 is arranged in the second hydraulic circuit 9 in a second fluid line 24, and the second fluidic line 24 can be connected to the first fluid line 21 via a second connecting line 29.
  • a hydraulic unit 1 In a hydraulic unit 1 according to the invention no own operator is required for the demand-based allocation of the volume flows by the directional valves 26 and 28 perform automated switching operations.
  • the directional control valves 26, 28 have a spring 30, 31 acting in the direction of a starting position and further comprise an actuating member 32, 33 with which the volumetric flow either fed to the respective pressure port 2 or 3 or via the connecting line 27 and 29, respectively other hydraulic circuit 9 or 8 is redirected.
  • the acting on the first directional control valve 26 first actuator 32 is controlled by a control line 34 which extends in the illustrated embodiment of the second hydraulic circuit 9 to the actuator 32 and acting on the second directional control valve 28 second actuator 33 is controlled via a control line 35, which extends in this embodiment from the first hydraulic circuit 8 to the actuator 33.
  • the switching position of the directional control valve 30 is determined by the pressure prevailing in the second hydraulic circuit 9, since the control lines 34 and 35 are hydraulic control lines in which the pressure in a fluid line of the other hydraulic circuit to the actuator of the directional control valve the other hydraulic circuit is transmitted.
  • the volumetric flow provided at a pressure port 2 or 3 can be increased by the one pumping element 17 or 14 of the other hydraulic circuit 9 or 8, whereby the operating speed of a connected device 4 or 5 can be increased without that a manual adjustment of the directional valves 26, 28 would be required.
  • the control lines 34 and 35 may also be electrical control lines with which status information from the other hydraulic circuit 9 or 8, e.g. Pressure levels or switch positions on the devices 4, 5 are transmitted to the actuator 32 and 33 of the considered hydraulic circuit 8, 9 and the previously described switching operations can be effected.
  • the hydraulic fluid 10 can be performed at low pressure level to the switching valve of the rescue cylinder and from this back to the fluid tank 11.
  • This retraction or extension movement should be able to be performed with the highest possible speed for reasons of saving time and is therefore the provision of a large volume flow of advantage and can due to the relatively low pressure levels and the drive 18 to apply the necessary power.
  • the pressure level typically increases up to 700 (1000) bar and has to be reduced due to the limited power of the drive 18 of the high pressure volume flow.
  • Fig. 1 This can be done, for example, characterized in that at a pressure increase at the pressure port 2, only the volume flow of the first pumping element 13 is guided to the pressure port 2, while the flow rate of the pumping element 14 via a pressure-controlled valve, for example, at a switching pressure of 150 to 250 bar is returned to the fluid container 11.
  • the pumping element 14 thereby requires only a comparatively small proportion of the drive power and a correspondingly higher proportion of the drive power for the pumping element 13, which must generate the high working pressure, is available.
  • Fig. 1 is the initial position of the directional control valves 26 and 28, which is effected by the springs 30 and 31, such that the volume flow of the pumping elements 14 and 17 respectively in the respective hydraulic circuit 8, 9 remains and is thus fed to the pressure port 2 and 3 respectively.
  • the directional control valves 26 and 28 which is effected by the springs 30 and 31, such that the volume flow of the pumping elements 14 and 17 respectively in the respective hydraulic circuit 8, 9 remains and is thus fed to the pressure port 2 and 3 respectively.
  • control lines 34 and 35 may also be electrical control lines with which electrical signals are transmitted from the respective other hydraulic circuit or from a device connected thereto to the actuator of the relevant hydraulic circuit. Electrical control signals can be generated by switching elements on the connected device or by pressure-voltage converter in the hydraulic circuit.
  • the actuators 32, 33 may, for. B. as a control piston for hydraulic control lines 34, 35 or as solenoid valves for electrical control lines 34, 35 may be realized in corresponding directional control valves.
  • Fig. 2 shows a diagram of a further embodiment of a hydraulic unit 1 according to the invention, wherein the components already described in the reference to Fig. 1 described Embodiment according to the same reference numerals. and is largely dispensed repetitions of component descriptions.
  • the connectable to the hydraulic unit 1 device 4 is formed in the illustrated embodiment by a hydraulic recovery device 36 and includes a double-acting hydraulic cylinder in which a piston separates two working spaces within the hydraulic cylinder from each other.
  • the direction of movement of the recovery device 36 depends on in which of the working spaces the hydraulic fluid 10 supplied through the fluid supply 6 is conducted by means of a switching valve 37.
  • the displaced from the respective other working space hydraulic fluid 10 is returned via the fluid return 7 back to the hydraulic unit 1.
  • a second device 5 is indicated, which can also be connected to the hydraulic unit 1.
  • the drive 18, the pump assemblies 12 and 15 and the fluid lines 20, 21, 23, 24 and manifolds 22, 25 correspond to the basis of Fig. 1 described embodiment, however, the lines are in Fig. 2 represented by dashes and not, as in Fig. 1 , by block arrows.
  • the embodiment according to Fig. 2 differs from that in Fig. 1 in that the directional control valves 26 and 28 are pressed by the springs 30 and 31 into a starting position in which a flow path from the first fluid line 21 of the first hydraulic circuit 8 to the connecting line 27 to the other hydraulic circuit 9 is opened.
  • the volume flow delivered by the pumping element 14 is diverted in the starting position of the directional control valve 26 to the other hydraulic circuit 9.
  • the starting position of the directional control valve 28 is such that the volume flow delivered by the pumping element 17 is diverted to the first hydraulic circuit 8.
  • the actuator 32 with which the first directional control valve 26 is switched against the action of the spring 30 from the starting position, in turn is addressed by a first control line 34, but in this embodiment, starting from the first hydraulic circuit 8 itself by the first fluid line 20, which leads from the pumping element 13 to the first pressure port 2.
  • the first hydraulic circuit 8 gets at a pressure increase in the fluid line 20, so to speak, the redirected from the pumping element 14 to the second hydraulic circuit 9 volume flow back for their own needs.
  • the second hydraulic circuit 9 can retrieve the in the initial position of the second directional valve 28 to the first hydraulic circuit 8 diverted volumetric flow of the pumping element 17, if necessary, to its own pressure port 3.
  • a device 4, 5 due to the predetermined power of the drive 18 at low pressure, a large volume flow and high pressure only a small volume flow can be provided.
  • it can be provided to redirect individual pumping elements, for example the pumping elements 14 and / or 17, directly to the fluid container 11 when the pressure level in the working device rises by means of a valve, not shown, and thus to reduce the proportion of the high-pressure delivery rate.
  • the pumping elements 13 and 14 of the pump arrangement 12 or the pumping elements 16 and 17 of the pump arrangement 15 have different sized delivery rates.
  • the pumping element 14 has a larger delivery capacity than the pumping element 13 and thus is well suited for the supply with a large volume flow at a comparatively low pressure level, while the smaller pumping element 13 with its smaller capacity for the provision of a relatively small volume flow at high pressure level is optimally suited.
  • Such multi-stage pumps are referred to the related art in this regard.
  • An inventive hydraulic unit 1 has, for example, the following flow rates, which are dependent on the respective operating situation.
  • a reference intensity of the drive 18, for example, a speed of 3000 / min is assumed.
  • the two pumping elements 13 and 16 of the hydraulic circuits 8, 9 have at this reference intensity a flow rate of, for example, in each case 0.7 l / min and have the pumping elements 14 and 17, for example, a flow rate of 2.0 l / min.
  • the pumping elements 13 and 16 can thus be referred to as high-pressure elements 40 and 41, respectively, and the two larger pumping elements 14 and 17 can be referred to as low-pressure elements 42 and 43, respectively.
  • two devices 4, 5 are connected to the pressure ports 2, 3, they are flowed through at idle at a pressure level of up to about 20 bar. As flow rate stands at the pressure port 2 of the delivered from the pump assembly 12 volume flow of a total of 2.7 l available. Likewise, the second device 5 is supplied by the pressure port 3 with a flow rate of 2.7 l / min.
  • the volumetric flow delivered by the pumping element 14 is diverted to the second hydraulic circuit 9 and, in turn, in this operating state are available to the devices 4, 5, as in idling mode, in each case 2.7 l / min of flow rate.
  • the raised Operating speed of the devices 4 and 5 can therefore always be used automatically when only one of the devices 4, 5 is actuated.
  • the pressure level is approximately between the switching pressure of less than 250 bar, at the exceeding of which the volume flow of the pumping element 14 is switched off and the limited by a pressure relief valve system pressure of about 750 to 1000 bar.
  • the great advantage of the hydraulic unit 1 according to the invention is that these switching operations for the demand-oriented allocation of the volume flows to the pressure ports 2 and / or 3 need not be performed by an operator, but due to the directional valves 26, 28th
  • the device 4 is supplied from the pressure port 2 at idle with a flow rate of 2.7 l / min, which consists of a partial amount of 0.7 l / min from the high pressure element 40 of the first hydraulic circuit 8 and a subset of 2.0 l / min composed of the low pressure element 43 of the second hydraulic circuit.
  • the volume flow of the low-pressure element 42 is additionally conducted at a delivery rate of 2.0 l / min to the pressure port 2, which then in total 4.7 l / min are available, if no flow for a second device 5 is required.
  • Fig. 1 and 2 are known from the prior art measures that allow a two-stage printing operation, for example, pressure relief valves, throttle valves, check valves, etc. are not shown or described in detail.
  • Fig. 3 is a further and optionally independent embodiment of a hydraulic unit 1 shown schematically, again for like parts, the same reference numerals or component designations as in the preceding Fig. 1 and 2 be used. In order to avoid unnecessary repetition, the description in the previous Fig. 1 and 2 referred or referred.
  • check valves 44 may be provided in the connection lines 27, 29 to prevent undesired flow direction reversal or pressure propagation in an undesired direction.
  • check valves 44 may be provided in the outgoing of these fluid lines 21 and 24. Furthermore, in the fluid lines between the directional control valves 26, 28 and the pressure ports 2, 3 also each a check valve 44 may be provided to take place at an increase in the pressure level at the pressure ports 2, 3 no pressure propagation in the low pressure region.
  • the pumping elements 13, 14, 16, 17 in Fig. 3 are, as already based on Fig. 1 and 2 described, provided with a drive, not shown, with which the pumping elements are driven simultaneously.
  • a pressure changeover valve 45 is provided in the first hydraulic circuit 8, a pressure changeover valve 45, with which the volume flow delivered by the pumping element 14, that is a low pressure element 42, when a switching pressure is exceeded is no longer passed to the pressure port 2, but into the fluid container 11.
  • the switching of the pressure changeover valve 45 is effected via an outgoing from the first fluid line 20 control line 46, with which the pressure prevailing at the pressure port 2 fluid pressure is passed to the pressure changeover valve 45 and this triggers a switching operation by means of an actuator, not shown, when due to an increasing pressure in the Control line 46, a spring 47 causing the starting position of the pressure switching valve 45 is overcome.
  • a pressure changeover valve 48 is analogously provided, with which the volume flow delivered by the second pumping element 17 is no longer passed to the second pressure port 3, but into the fluid container 11 when a limiting pressure is exceeded.
  • a control line 49 effecting the switchover acts on the pressure level existing between the second pumping element 16, that is to say the high pressure element 41 and the second pressure connection 3, and causes the volume flow of the pumping element 17 to be conveyed to the fluid reservoir 11 when a restoring force caused by a spring 50 is exceeded.
  • the power of the drive is thus in these cases for the greater part for the drive of the high pressure elements 40 and 41 available and can be overcome with the connected devices 4, 5 and high Häderfound.
  • each hydraulic circuit 8, 9 is provided with a pressure relief valve 51 which limits the maximum pressure provided at the pressure ports 2 and 3 and the maximum pressure is set such that bursting of components of the hydraulic unit. 1 is avoided.
  • maximum pressure for example, an upper limit of 750 to 1000 bar is set.
  • the operation of the directional control valves 26, 28 corresponds to Fig. 3 essentially those of Fig. 2 illustrated embodiment, since here in the initial position of the pumping element 14, 15 supplied flow to the other hydraulic circuit is passed and at a switching operation of the directional control valve 26 and 28 due to an increasing pressure in the control line 34 and 35 of the flow again in each considered Hydraulic circuit 8 and 9 is retrieved and directed to the respective pressure port 2 and 3 respectively.
  • both directional control valves 26 and 28 are shown in the initial position and is returned directly from the valve of the other hydraulic circuit 9 and 8 diverted volume flow via a return line 39 substantially without pressure in the fluid container 11. If, for example, a device 4 is actuated at the pressure port 2 and the fluid pressure rises as a result, a switching process of the directional valve 26 is effected via the control line 34 and the volume flows of the pumping elements 13, 14 and 17 are supplied to the pressure port 2 in this case. This means an increased operating speed of a device 4 compared to a supply by only one hydraulic circuit 8 alone.
  • Fig. 4 is a further and possibly independent embodiment of a hydraulic unit 1 is shown, again for like parts, the same reference numerals or component names as in the preceding Fig. 1 to 3 be used. In order to avoid unnecessary repetition, the detailed description in the previous ones will be used Fig. 1 to 3 referred or referred.
  • the hydraulic unit 1 according to Fig. 4 differs from the embodiment in Fig. 3 in the integration of the directional control valves 26 and 28, in which in the initial position caused by the springs 30 and 31, the volume flows supplied by the pumping elements 14 and 17 are provided within the own hydraulic circuit 8 and 9 at the respective pressure port 2 and 3 respectively and only at pressure increase in the other hydraulic circuit 9 and 8, a diversion of a flow occurs.
  • the actuators that are activated by the control lines 34 and 35 are in Fig. 4 not shown for reasons of space.
  • Fig. 4 further shows that optionally in the hydraulic circuits 8 and 9 in each case before the pressure ports 2 and 3, pressure relief valves 52 may be provided with which a largely unpressurized return of hydraulic fluid to the fluid container 11 are produced can, in the event that no device is connected to the respective pressure port 2 or 3.
  • pressure relief valves 52 may be manually operated or else part of a clutch system, in which in a coupling operation both the fluid supply 6 and the fluid return 7 of the device (see Fig. 1 ) get connected.
  • the pressure relief valve 52 may be formed in this case as a by-pass valve in the pressure port 2 and 3, respectively.
  • Fig. 4 is further shown that the pump elements 14, 17, which may be formed as low pressure elements 42 and 43, respectively, a pressure relief valve (DBV) 53 may be downstream, which then becomes effective in the illustrated embodiment, when the hydraulic fluid from the directional control valves 26 and 28 respectively is redirected to the other hydraulic circuit 9 and 8 respectively and in this due to a high resistance to high pressure fluid is present.
  • the volume flow of the pumping elements 42 and 43 can be derived in this case via the pressure relief valve 53 into the fluid container 11.
  • a pressure limiting valve 53 can structurally correspond to the pressure changeover valves 45, 48.
  • Fig. 5 is a further and possibly independent embodiment of a hydraulic unit 1 is shown, again for like parts, the same reference numerals or component names as in the preceding Fig. 1 to 4 be used. In order to avoid unnecessary repetition, the detailed description in the preceding is preceded Fig. 1 to 4 referred or referred.
  • the leading to the directional control valve 26 first fluid line 21 leads in this embodiment, not only the volume flow of the pumping element 14, but also the flow of a further pumping element 54 and can be redirected via the directional control valve 26 to the other hydraulic circuit 9 become.
  • the pumping element 14 is designed as a low-pressure element 42 having a comparatively high delivery rate
  • the pumping element 54 is designed as a high-pressure element 55, which has a comparatively small delivery rate.
  • both volume flows of the pumping elements 14 and 54 are thus diverted via the first connecting line 27 to the second hydraulic circuit 9. If no increased volume flow is required in this, since the connected device is idling, this redirected flow is discharged via the return line 39 to the fluid tank 11. At a pressure increase in the second hydraulic circuit 9, this volume flow is conducted to the second pressure port 3, since the second directional control valve 28 is switched via the control line 35 of the second hydraulic circuit. At the pressure port 3, the delivery rate of the second hydraulic circuit 9 is thus increased by the delivery rate of the pumping elements 14 and 54.
  • an additional pumping element 56 is arranged, which is designed as a high pressure element 57 and the provided at the pressure port 2 of the first hydraulic circuit 8 volume flow to the delivery of this high pressure element 57 and optionally also to the flow of the low pressure element 43 in the second hydraulic circuit 9 are increased.
  • control of the pressure changeover valves 45 and 48 takes place via control lines 46 and 49 with the fluid pressure acting on the high-pressure elements 55 and 57, respectively.
  • Fig. 6 is a further and possibly independent embodiment of a hydraulic unit 1 is shown, again for like parts, the same reference numerals or component names as in the preceding Fig. 1 to 5 be used. In order to avoid unnecessary repetition, the detailed description in the preceding is preceded Fig. 1 to 5 referred or referred.
  • the volume flow provided at a pressure connection can, if required, be increased by the delivery rate of all pumping elements of another hydraulic circuit.
  • the volume flow of the pumping elements 13 and 14 can be diverted via the path element 26 to the second hydraulic circuit 9, wherein the control of the volume flow of the pumping element 14, which may be designed as a low pressure element 42, as is done with reference to the preceding embodiments.
  • the control of the volume flow of the pumping element 14, which may be designed as a low pressure element 42 is done with reference to the preceding embodiments.
  • the shut-off valve 58 is in his open position caused by a spring 60 and the volume flow of the pumping element 13 can reach the pressure port 2 of the first hydraulic circuit 8.
  • the first fluid line 20 is shut off from the pumping element 13 to the pressure port 2 and the volume flow of the pumping element 13 via the transition line 59 to the directional control valve 26, from which it passes through the first connecting line 27 to the second hydraulic circuit 9 in a row .
  • the volume flow of the pumping element 16 can be redirected to the first hydraulic circuit 8 in analogy.
  • both hydraulic circuits 8 and 9 have such a transition function or diversion function in the exemplary embodiment shown, only the hydraulic circuit that requests the volume flows of the other pump elements in time before the other hydraulic circuit can provide the increased flow rate at the pressure port.
  • the activation of the shut-off valves 58, 62 takes place at a pressure below about 25 bar, which is at non-actuated devices, ie in idle mode, the required base pressure available at both pressure connections and the previously activated device gets the volume flow of all pumping elements available.
  • transition lines 59 and 60 are further advantageously throttle elements 65 and 66 respectively arranged, with which in the first fluid line 20 and the second fluid line 23, a back pressure is built up for the optionally required control of the directional valves 26, 28 and the shut-off valves 58th , 62 serves.
  • the hydraulic fluid 10 advantageously passes via suction lines from the fluid container 11 to the pumping elements.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT524855B1 (de) * 2021-06-18 2022-10-15 Weber Hydraulik Gmbh Hydraulikaggregat zur Versorgung hydraulisch antreibbarer Rettungsgeräte
AT524855A4 (de) * 2021-06-18 2022-10-15 Weber Hydraulik Gmbh Hydraulikaggregat zur Versorgung hydraulisch antreibbarer Rettungsgeräte

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US10041508B2 (en) 2018-08-07
AT516181A4 (de) 2016-03-15
EP3012463B1 (fr) 2020-09-02
AT516181B1 (de) 2016-03-15
US20160102687A1 (en) 2016-04-14

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