WO2022039697A1 - Hydraulic system providing energy recovery by double spool directional valves during tilting/lowering in bucket cylinder on loader side and in arm / bucket cylinders on excavator side in backhoe loader, wheel loader and excavator machines - Google Patents

Hydraulic system providing energy recovery by double spool directional valves during tilting/lowering in bucket cylinder on loader side and in arm / bucket cylinders on excavator side in backhoe loader, wheel loader and excavator machines Download PDF

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Publication number
WO2022039697A1
WO2022039697A1 PCT/TR2021/050758 TR2021050758W WO2022039697A1 WO 2022039697 A1 WO2022039697 A1 WO 2022039697A1 TR 2021050758 W TR2021050758 W TR 2021050758W WO 2022039697 A1 WO2022039697 A1 WO 2022039697A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure
tilting
lowering
cylinder
valve
Prior art date
Application number
PCT/TR2021/050758
Other languages
French (fr)
Inventor
İskender Atilla ÖKMEN
Original Assignee
Hi̇dromek-Hi̇droli̇k Ve Mekani̇k Maki̇na İmalat Sanayi̇ Ve Ti̇caret Anoni̇m Şi̇rketi̇
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Hi̇dromek-Hi̇droli̇k Ve Mekani̇k Maki̇na İmalat Sanayi̇ Ve Ti̇caret Anoni̇m Şi̇rketi̇ filed Critical Hi̇dromek-Hi̇droli̇k Ve Mekani̇k Maki̇na İmalat Sanayi̇ Ve Ti̇caret Anoni̇m Şi̇rketi̇
Priority to EP21827172.4A priority Critical patent/EP4200481A1/en
Publication of WO2022039697A1 publication Critical patent/WO2022039697A1/en

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Classifications

    • 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
    • E02F9/2217—Hydraulic or pneumatic drives with energy recovery arrangements, e.g. using accumulators, flywheels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/024—Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/14—Energy-recuperation means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20507—Type of prime mover
    • F15B2211/20515—Electric motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20507—Type of prime mover
    • F15B2211/20523—Internal combustion engine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20538—Type of pump constant capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—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
    • F15B2211/25—Pressure control functions
    • F15B2211/253—Pressure margin control, e.g. pump pressure in relation to load pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/3054—In combination with a pressure compensating valve the pressure compensating valve is arranged between directional control valve and 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
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
    • F15B2211/3057—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve having two valves, one for each port of a double-acting 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
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
    • F15B2211/30575—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve in a Wheatstone Bridge arrangement (also half bridges)
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
    • F15B2211/3058—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve having additional valves for interconnecting the fluid chambers of a double-acting actuator, e.g. for regeneration mode or for floating mode
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3144—Directional control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional 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
    • F15B2211/30—Directional control
    • F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
    • F15B2211/31523—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source and an 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
    • F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
    • F15B2211/31523—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source and an output member
    • F15B2211/31541—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source and an output member having a single pressure source and 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
    • F15B2211/31552—Directional control characterised by the connections of the valve or valves in the circuit being connected to an output member and a return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/327—Directional control characterised by the type of actuation electrically or electronically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—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
    • F15B2211/50—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
    • F15B2211/50527—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 using cross-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
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5159—Pressure control characterised by the connections of the pressure control means in the circuit being connected to an output member and a return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6306—Electronic controllers using input signals representing a pressure
    • F15B2211/6309—Electronic controllers using input signals representing a pressure the pressure being a pressure source supply 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
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6306—Electronic controllers using input signals representing a pressure
    • F15B2211/6313—Electronic controllers using input signals representing a pressure the pressure being a load pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
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    • 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
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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
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    • F15B2211/6651—Control of the prime mover, e.g. control of the output torque or rotational speed
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    • 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
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    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6652—Control of the pressure source, e.g. control of the swash plate angle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
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    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
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    • F15B2211/6654—Flow rate control
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    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
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    • 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
    • F15B2211/7107—Multiple output members, e.g. multiple hydraulic motors or cylinders the output members being mechanically linked
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    • 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
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    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F15B2211/7114—Multiple output members, e.g. multiple hydraulic motors or cylinders with direct connection between the chambers of different actuators
    • F15B2211/7128—Multiple output members, e.g. multiple hydraulic motors or cylinders with direct connection between the chambers of different actuators the chambers being connected in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
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    • 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
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    • F15B2211/76—Control of force or torque of the output member
    • F15B2211/761—Control of a negative load, i.e. of a load generating hydraulic energy
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
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    • 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
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    • F15B2211/781—Control of multiple output members one or more output members 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
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/88—Control measures for saving energy

Definitions

  • the present invention relates to a hydraulic system developed for reducing energy consumption during tilting/lowering with double spool valves in bucket cylinder in the backhoe loader, wheel loader machines and arm / bucket cylinders wheel excavator and crawler excavator.
  • the invention particularly relates to a hydraulic system that minimizes energy losses during operation, prevents oil leaks in long-term waiting in the cylinders, eliminates power losses during the bucket tilting period without using bucket tipping or steering with the steering wheel, provides lower fuel consumption and increased efficiency.
  • Backhoe loader is a construction machine used in channel digging and loading works.
  • Wheel loaders are the work machines used in loading works.
  • Wheel Excavator and Crawler Excavators are construction machines used digging and loading works.
  • These work machines are used for loading the material that is obtained as a result of the excavation or previously piled on the truck for transportation purposes, excavation on soft and hard grounds or transporting the work material from one location to another within a short distance. They can also be used for surface leveling or simple purpose shoveling based on the nature of the bucket. It can perform different purpose loading and unloading functions with different attachments mounted instead of the bucket.
  • variable flow gear pump or variable flow piston pump and direction control valves with single spool flow sharing are used in present excavator and loader machines.
  • variable and constant flow pump applications depending on the joystick variability in the pump flow rate is provided with the pilot oil taken from the user outlet of the single spool valve depending on joystick movement at user input.
  • regenerative function is included in the hydraulic system so as to prevent cavitation at low diesel revolutions in the applications in valve designs.
  • the present invention relates to a novel hydraulic system on loader-side bucket, excavator-side arm and bucket cylinders which fulfills the abovementioned requirements, eliminates all disadvantages and brings some additional advantages, is developed to be used the backhoeloader, wheel loader and excavator work machines.
  • the aim of the invention based on the state of the art is to is to reduce the pressure losses and excess energy absorbed in the system by performing proportional flow control at the cylinder inlet, external proportional flow, and pressure-dependent regeneration control during tilting/lowering at the cylinder outlet by using double spool directional valves instead of single spool directional valves in the developed hydraulic system.
  • Another aim of the invention is to provide operation without cavitation with low pump flow rates in the hydraulic system at different diesel speeds and tilting/lowering movements of the cylinders operating under different weight effect by means of the proportional regeneration made externally from the outside of the spool.
  • Another aim of the invention is to operate with lower pressure losses during tilting I lowering with regeneration flow in the cylinder by the proportional throttle valve, compensator and regeneration check valve, which are selected independently of the direction valve based on the cylinder descent rate at the user exit in the hydraulic system and to provide opportunity for switching to automatic excavation by cancelling the regeneration due to pressure during the excavation.
  • Another aim is to prevent power losses in the system by pumping only as much oil as the steering wheel needs when steering and bucket tilting movements are performed together with the joystick in the pulled position
  • Another aim of the invention is to eliminate pressure losses on the hydraulic installation by minimizing the length of pipes and hoses laid on the machine by carrying the designed control block on the cylinder.
  • Another aim of the invention is to provide continuous reading of the pressure sensors used in A, B user lines and P pump lines of the cylinder in hydraulic system design and to reach lower fuel consumption values and increase efficiency by means of smart software algorithms.
  • Figure 1 is the general view of the hydraulic circuit diagram of the tilting/ lowering-lifting cylinder hydraulic control block with double spool direction valves in the loader cylinders and the excavator arm and bucket cylinders.
  • Figure 2 is the general view of the hydraulic circuit diagram of the tilting/ lowering-lifting cylinder hydraulic control block with double spool directional valves in wheel loaders, wheel excavators, backhoe loaders in a preferred embodiment of the invention.
  • Figure-3 is a general view of the hydraulic circuit diagram of the arm and bucket cylinder tilting/lowering-lifting cylinder hydraulic control block in crawler excavators in a preferred embodiment of the invention.
  • Reference Numbers
  • inventive hydraulic system developed to provide energy recovery during tilting/ lowering in the tilting/ lowering-lifting cylinder hydraulic control block (2.0) for use in construction equipment such as backhoe loaders, wheel loaders and wheel and crawler excavators are described only for clarifying the subject matter illustratively and in a manner such that no limiting effect is created.
  • inventive hydraulic system of the tilting/lowering-lifting cylinder hydraulic control block (2.0) prevents the tilting/lowering-lifting cylinder hydraulic controls block (2.0) level losses in the cylinder (5.0) during idle standby.
  • Said hydraulic system comprises the following; the first pressure compensator tilting/lowering proportional directional valve (OR1 ) that provides flow control at the user input for minimum pump output flow (Q) and pressure, joystick movements when the joystick is not moving (2.1 ) and the second pressure lifting proportional directional valve (OR2) (2.2); third proportional throttle valve (OR3) (2.9) that controls the flow at the user outlet; compensator (2.10) that provides a transition period to automatic excavation by cancelling regeneration due to pressure during regeneration in idle movements through the fourth check valve (2.8) and excavation.
  • OR1 first pressure compensator tilting/lowering proportional directional valve
  • OR3 third proportional throttle valve
  • MA pressure sensor (2.12), MB pressure sensor (2.13) and MP pressure sensor (2.14) are continuously read and different types of hydraulic pumps (3,0) are selected according to different application types and the pump output flow rate (Q) that will provide advantage in fuel consumption and/or the first pressure compensator tilting / lowering proportional directional valve (OR1) (2.1 ) and the second pressure compensator lifting proportional directional valve (OR2) (2.2) are controlled by means of smart software algorithms.
  • first pressure compensator tilting/lowering proportional directional valve (OR1) (2.1 ), second pressure compensator lifting proportional directional valve (OR2) (2.2), controls the pump output flow rate (Q) according to the requirement of the system and can provide flow sharing when a plurality of users operate
  • the hydraulic pump (3.0) ensures that it operates only at the pump flow rate and pressure as required by the steering wheel.
  • first pressure compensator tilting/lowering proportional directional valve (OR1) (2.1), second pressure compensator lifting proportional directional valve (OR2) (2.2) ensures the operation is carried out with minimum energy consumption of the hydraulic pump (3.0) since it is de-energized.
  • the pump output flow rate (Q) required by the system is produced from the hydraulic pump (3.0) depending on the LS load pressure in proportion to the joystick movement.
  • Said first pressure compensator tilting/lowering proportional directional valve (OR1) (2.1 ), second pressure compensator lifting proportional directional valve (OR2) (2.2), third proportional throttle valve (OR3) (2.9) selections can be made as a hydraulic pilot actuated or electro-hydraulic actuated valve.
  • the minimum pump pressure in variable flow hydraulic pumps (3.0) is provided according to the minimum operating pressure provided by the pump manufacturer and the operating conditions in the machines.
  • Figure-2 shows a sample hydraulic system circuit diagram for wheel loader, backhoe-loader, wheel excavator applications, and figure-3 for crawler excavator applications.
  • the hydraulic pump (3.0) can be selected with constant or variable flow (load-sensing or electronic flow control), hydraulic pump (3.0) can be driven by diesel or electric motor (M).
  • the flow rate required by the system is generated from the pump by transmitting a signal to the pump over the LS line depending on the LS load pressure in proportion to the joystick movement in all hydraulic pump (3.0) applications.
  • MA pressure sensor (2.12), MB pressure sensor (2.13) and MP pressure sensor (2.14) are continuously read by the software and control the pump output flow (Q) by means of smart algorithms and smart algorithm software provides serious advantages in fuel consumption. Different AP values can be adjusted through the software in different operating periods.
  • the flow rate required by the user is controlled by sending the user's surplus hydraulic pump (3.0) flow to the tank at the value of user pressure + spring resistance over the hydraulic LS signal transmitted to the compensator with constant pressure adjustment in the safety block (1.0).
  • the first tilting/lowering proportional directional valve (OR1 ) (2.1), second pressure compensator lifting proportional directional valve (OR2) (2.2), third proportional throttle valve (OR3) (2.9) are in closed position.
  • the first pressure compensator lifting proportional direction valve (OR1) (2.1 ) and the second pressure compensator lowering proportional direction valve (OR2) (2.2) do not transmit flow from the hydraulic pump (3.0) to the cylinder (5.0) when the joystick is not used, at the same time LS lines are also kept open to the tank.
  • tilting/lowering cylinder (5.0) When the tilting/lowering cylinder (5.0) is in the tilting/lowering period (x), tilting/lowering can be performed by stimulating the third proportional throttle valve (OR3) (2.9). Regeneration is provided in the cylinder (5.0) by means of the constant pressure adjustable compensator (2.10) and the fourth check valve (2.8).
  • the hose bursting valve (4.0) mounted on the lowering cylinder (5.0) is opened by giving a pilot hydraulic warning to the first pressure compensator tilting /lowering proportional directional valve (OR1) (2.1 ) during lowering.
  • the tilting/lowering speed of the tilting/lowering cylinder (5.0) is calibrated over the third proportional throttle (2.9) in proportion to the movement course of the joystick.
  • the maximum breakout force lifting position of the vehicle from the ground
  • hydraulic pump (3.0) by obtaining the flow rate required for lifting the machine from the ground/excavation depending on user's tilting/lowering cylinder (5.0) diameter depending on joystick movement.
  • a minimum flow rate of the hydraulic pump (3.0) is required due to the potential energy in the cylinders (5.0) during tilting. For this reason, operation with low pressure losses is provided at variable diesel speeds.
  • the MA pressure sensor (2.12) used in the MA line remains at a pressure of 50 bar and above due to the weight effect on the piston side of the cylinder (5.0), when the tilting/lowering cylinder (5.0) presses to ground level, pressure in the MA line drops below 50 bar, the hydraulic pump (3.0) flow rate is transmitted to the system in proportion to the lowering speed with the joystick movement by stimulating the first pressure compensator tilting proportional directional control valve (OR1) (2.1).
  • the hydraulic pump (3.0) produces a minimum pressure and pump output flow (Q) during the lowering process of the cylinder (5.0), if the joystick is still pulled and the MA pressure sensor (2.12) is below 50 bar, the machine is forced to be lifted from the ground in proportion to the joystick movement by stimulating the first pressure compensator lowering proportional directional valve (OR1) (2.1 ). While it is in lifting the machine from the ground/in excavation position, the oil returning from the cylinder (5.0) returns to the tank at low pressure over the compensator (2.10) and the second counterbalance valve (2.6). Therefore, power drawing from the system is also minimized since the hydraulic pump (3.0) will remain at the minimum flow rate and pressure value until the machine moves to the lifting force from the ground in the tilting period.
  • the tilting position of the steering wheel and the tilting cylinder during loading is a period often used together by the operator. While the vehicle is loading, the machine is approaching and moving away from the vehicle together with the steering wheel, at the same time, the bucket tilting process is performed by the operator.
  • the hydraulic pump (3.0) flow is not required due to the potential energy of the attachment weight in tilting.
  • Warning of the third proportional throttle valve (2.9) and interruption of warning of the first pressure compensator lowering proportional directional valve (OR1 ) (2.1) is carried out with the information received from the MA pressure sensor (2.12) on the MA line. It is sufficient for the hydraulic pump (3.0) to pump oil as much as the steering wheel requires. While the joystick of the tilting cylinder (5.0) is pulled, The hydraulic pump (3.0) draws power from the system only in proportion to the steering flow rate and pressure, rather than the total flow of the user + steering requirement.
  • Lifting period (y) of the tilting/lowering cylinder (5.0) is performed by giving a warning to the second pressure compensator lifting proportional directional valve (OR2) (2.2).
  • Calibration of the minimum and maximum speed of the cylinder (5.0) in the lifting period (y) is made by the hydraulic pump (3.0) by pumping the required flow to the system after the second pressure compensator proportional lifting directional valve (OR2) (2.2) is stimulated in proportion to the joystick movement.
  • the flow of the cylinder (5.0) returned by the piston returns to the tank over the first counter balance valve (2.5).
  • the reduction in fuel consumption and increase in efficiency can be carried to higher levels by means of using smart algorithm software by reading the MA pressure sensor (2.12), MB pressure sensor (2.13) and MP pressure sensor (2.14) installed on the MA, MB, MP lines.
  • flow rate control in lowering cylinder (5.0) with first pressure compensator lowering proportional directional control valve (OR1) (2.1), Flow control and regeneration in idle movements at the cylinder outlet with the third proportional throttle (OR3) (2.9), the fourth check valve (2.8) and the compensator (2.10), transition movements to pressure can be provided during the excavation, by automatically cancelling the regeneration depending on the pressure.

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Abstract

The invention relates to a hydraulic system developed to provide energy recovery during tilting of the first pressure compensator tilting/lowering proportional directional valve (OR1) (2.1) in tilting/lowering-lifting cylinder hydraulic control block (2.0) in construction equipment such as backhoe-loaders, wheel loaders, wheel and crawler excavators. Said hydraulic system is positioned in the hydraulic control block (2.0) of the tilting / lowering-lifting cylinder in the bucket, arm and bucket cylinders (5.0) and prevents the tilting/lowering-lifting cylinder hydraulic control block (2.0) level losses in the cylinder during idle mode. Said hydraulic system comprises the following; the first pressure compensator tilting/lowering proportional directional valve (OR1) that provides flow control at the user input for minimum pump output flow (Q) and pressure, joystick movements when the joystick is not moving (2.1) and the second pressure lifting proportional directional valve (OR2) (2.2); third proportional throttle valve (OR3) (2.9) Provides automatic excavation transition period by canceling regeneration and pressure-dependent regeneration during excavation in idle tilting/lowering movements and controlling the flow rate depending on the pressure at the user exit; fourth check valve (2.8) and compensator (2.10); MP pressure sensor (2.14) in MP line, MA pressure sensor (2.12) in MA line and MB pressure sensor in MB line (2.13).

Description

HYDRAULIC SYSTEM PROVIDING ENERGY RECOVERY BY DOUBLE SPOOL DIRECTIONAL VALVES DURING TILTING/LOWERING IN BUCKET CYLINDER ON LOADER SIDE AND IN ARM I BUCKET CYLINDERS ON EXCAVATOR SIDE IN BACKHOE LOADER, WHEEL LOADER AND EXCAVATOR MACHINES
Field of the Invention
The present invention relates to a hydraulic system developed for reducing energy consumption during tilting/lowering with double spool valves in bucket cylinder in the backhoe loader, wheel loader machines and arm / bucket cylinders wheel excavator and crawler excavator.
The invention particularly relates to a hydraulic system that minimizes energy losses during operation, prevents oil leaks in long-term waiting in the cylinders, eliminates power losses during the bucket tilting period without using bucket tipping or steering with the steering wheel, provides lower fuel consumption and increased efficiency.
State of the Art
Backhoe loader is a construction machine used in channel digging and loading works. Wheel loaders are the work machines used in loading works. Wheel Excavator and Crawler Excavators are construction machines used digging and loading works.
These work machines are used for loading the material that is obtained as a result of the excavation or previously piled on the truck for transportation purposes, excavation on soft and hard grounds or transporting the work material from one location to another within a short distance. They can also be used for surface leveling or simple purpose shoveling based on the nature of the bucket. It can perform different purpose loading and unloading functions with different attachments mounted instead of the bucket.
Today, constant flow gear pump or variable flow piston pump and direction control valves with single spool flow sharing are used in present excavator and loader machines. In variable and constant flow pump applications, depending on the joystick variability in the pump flow rate is provided with the pilot oil taken from the user outlet of the single spool valve depending on joystick movement at user input. Furthermore, regenerative function is included in the hydraulic system so as to prevent cavitation at low diesel revolutions in the applications in valve designs. Since the flow rate at the cylinder outlet is designed according to the single spool parameter based on the bucket load and the idle speed of the diesel engine over the spool valve, pressure losses occur during the flow rate transitions from the pump to the cylinder and from the cylinder to the tank over the direction control valve in increasing diesel revolutions, there is energy loss in the bucket cylinder during the tilting arm and the bucket cylinder during the lowering movement during operation at high diesel speeds during measurements. Furthermore, during tilting on the loader side and lowering in the arm and bucket cylinders on the excavator side, it has been observed that while working at low diesel speeds, cavitation occurs in the cylinders, and level losses occur if there is no locking valve in the cylinders during long periods of waiting. Furthermore, the tilting process is frequently used on the steering wheel and the bucket cylinder on the loader side, it has been determined that while steering and tilting movements are carried out together, the pump consumes more power from the system than the desired value.
As a result, the requirement for a new hydraulic system developed for use in excavator and loader machines which eliminates the abovementioned problems and the insufficiency of the current solutions makes it necessary to make a development in the relevant technical field.
Brief Description of the Invention
The present invention relates to a novel hydraulic system on loader-side bucket, excavator-side arm and bucket cylinders which fulfills the abovementioned requirements, eliminates all disadvantages and brings some additional advantages, is developed to be used the backhoeloader, wheel loader and excavator work machines.
The aim of the invention based on the state of the art is to is to reduce the pressure losses and excess energy absorbed in the system by performing proportional flow control at the cylinder inlet, external proportional flow, and pressure-dependent regeneration control during tilting/lowering at the cylinder outlet by using double spool directional valves instead of single spool directional valves in the developed hydraulic system.
Another aim of the invention is to provide operation without cavitation with low pump flow rates in the hydraulic system at different diesel speeds and tilting/lowering movements of the cylinders operating under different weight effect by means of the proportional regeneration made externally from the outside of the spool.
Another aim of the invention is to operate with lower pressure losses during tilting I lowering with regeneration flow in the cylinder by the proportional throttle valve, compensator and regeneration check valve, which are selected independently of the direction valve based on the cylinder descent rate at the user exit in the hydraulic system and to provide opportunity for switching to automatic excavation by cancelling the regeneration due to pressure during the excavation.
Another aim is to prevent power losses in the system by pumping only as much oil as the steering wheel needs when steering and bucket tilting movements are performed together with the joystick in the pulled position
Another aim of the invention is to eliminate pressure losses on the hydraulic installation by minimizing the length of pipes and hoses laid on the machine by carrying the designed control block on the cylinder.
Another aim of the invention is to provide continuous reading of the pressure sensors used in A, B user lines and P pump lines of the cylinder in hydraulic system design and to reach lower fuel consumption values and increase efficiency by means of smart software algorithms.
The structural and characteristic features of the present invention will be understood clearly by the following drawings and the detailed description made with reference to these drawings. Therefore the evaluation shall be made by taking these figures and the detailed description into consideration.
Brief Description of Drawings
In order to understand the advantages of the present invention with its structure and additional elements, it shall be evaluated with the following defined figures.
Figure 1 is the general view of the hydraulic circuit diagram of the tilting/ lowering-lifting cylinder hydraulic control block with double spool direction valves in the loader cylinders and the excavator arm and bucket cylinders.
Figure 2 is the general view of the hydraulic circuit diagram of the tilting/ lowering-lifting cylinder hydraulic control block with double spool directional valves in wheel loaders, wheel excavators, backhoe loaders in a preferred embodiment of the invention.
Figure-3 is a general view of the hydraulic circuit diagram of the arm and bucket cylinder tilting/lowering-lifting cylinder hydraulic control block in crawler excavators in a preferred embodiment of the invention. Reference Numbers
Q. Pump outlet flow
1 .0. Multi-purpose safety block
2.0. Tilting/lowering-lifting cylinder hydraulic control block
2.1 . First pressure compensator tilting/lowering proportional directional valve (OR1)
2.2. Second pressure compensator lifting proportional directional valve (OR2)
2.3. First check valve
2.4. Second check valve
2.5. First counter balance valve
2.6. Second counter balance valve
2.7. Third check valve
2.8. Fourth check valve
2.9. Third proportional throttle valve (OR3)
2.10. Compensator
2.11. Balance compensator orifice
2.12. MA Pressure sensor
2.13. MB Pressure sensor
2.14. MP Pressure sensor
3.0 Hydraulic pumps
4.0 Hose bursting valves
5.0 Tilting/lowering lifting cylinders x. Tilting/lowering period y. lifting period
M. Motor
Detailed Description of the Invention
In this detailed description, the inventive hydraulic system developed to provide energy recovery during tilting/ lowering in the tilting/ lowering-lifting cylinder hydraulic control block (2.0) for use in construction equipment such as backhoe loaders, wheel loaders and wheel and crawler excavators are described only for clarifying the subject matter illustratively and in a manner such that no limiting effect is created. As indicated in Figure-1 , the inventive hydraulic system of the tilting/lowering-lifting cylinder hydraulic control block (2.0) prevents the tilting/lowering-lifting cylinder hydraulic controls block (2.0) level losses in the cylinder (5.0) during idle standby. Said hydraulic system comprises the following; the first pressure compensator tilting/lowering proportional directional valve (OR1 ) that provides flow control at the user input for minimum pump output flow (Q) and pressure, joystick movements when the joystick is not moving (2.1 ) and the second pressure lifting proportional directional valve (OR2) (2.2); third proportional throttle valve (OR3) (2.9) that controls the flow at the user outlet; compensator (2.10) that provides a transition period to automatic excavation by cancelling regeneration due to pressure during regeneration in idle movements through the fourth check valve (2.8) and excavation.
In said hydraulic system, MA pressure sensor (2.12), MB pressure sensor (2.13) and MP pressure sensor (2.14) are continuously read and different types of hydraulic pumps (3,0) are selected according to different application types and the pump output flow rate (Q) that will provide advantage in fuel consumption and/or the first pressure compensator tilting / lowering proportional directional valve (OR1) (2.1 ) and the second pressure compensator lifting proportional directional valve (OR2) (2.2) are controlled by means of smart software algorithms. Said first pressure compensator tilting/lowering proportional directional valve (OR1) (2.1 ), second pressure compensator lifting proportional directional valve (OR2) (2.2), controls the pump output flow rate (Q) according to the requirement of the system and can provide flow sharing when a plurality of users operate When the steering wheel is used at the same time in said hydraulic system, in tilting period, the hydraulic pump (3.0) ensures that it operates only at the pump flow rate and pressure as required by the steering wheel. In said hydraulic system, first pressure compensator tilting/lowering proportional directional valve (OR1) (2.1), second pressure compensator lifting proportional directional valve (OR2) (2.2) ensures the operation is carried out with minimum energy consumption of the hydraulic pump (3.0) since it is de-energized. In all hydraulic pump (3.0) applications, the pump output flow rate (Q) required by the system is produced from the hydraulic pump (3.0) depending on the LS load pressure in proportion to the joystick movement. Said first pressure compensator tilting/lowering proportional directional valve (OR1) (2.1 ), second pressure compensator lifting proportional directional valve (OR2) (2.2), third proportional throttle valve (OR3) (2.9) selections can be made as a hydraulic pilot actuated or electro-hydraulic actuated valve. The minimum pump pressure in variable flow hydraulic pumps (3.0) is provided according to the minimum operating pressure provided by the pump manufacturer and the operating conditions in the machines. Figure-2 shows a sample hydraulic system circuit diagram for wheel loader, backhoe-loader, wheel excavator applications, and figure-3 for crawler excavator applications. The hydraulic pump (3.0) can be selected with constant or variable flow (load-sensing or electronic flow control), hydraulic pump (3.0) can be driven by diesel or electric motor (M).
The flow rate required by the system is generated from the pump by transmitting a signal to the pump over the LS line depending on the LS load pressure in proportion to the joystick movement in all hydraulic pump (3.0) applications. MA pressure sensor (2.12), MB pressure sensor (2.13) and MP pressure sensor (2.14) are continuously read by the software and control the pump output flow (Q) by means of smart algorithms and smart algorithm software provides serious advantages in fuel consumption. Different AP values can be adjusted through the software in different operating periods. In constant flow hydraulic pump (3.0) application with variable speed electric motor (M), as the hydraulic pump (3.0) delivers a constant flow rate, the amount of the pump output flow rate (Q) is provided by adjusting the speed of the electric motor (M) through the software to be MP-MA = AP or MP-MB = AP depending on the movement speed of the cylinders (5.0). In electronic flow control pump application with diesel driven engine (M), the electronic pump output flow rate (Q) of the pump is adjusted over software, depending on the movement speed of the cylinder in a manner such that the pressure difference is MP-MA = AP, MP-MB = AP. In diesel driven motor (M) and variable flow load sensitive hydraulic pump (3.0) (with load sensing) application, the pump output flow rate (Q) is provided over the hydraulic LS signal transmitted to the hydraulic pump (3.0) in a manner such that P-LS = AP is constant depending on the movement speed of the cylinders (5.0). In Diesel driven engine (M) constant flow hydraulic pump (3.0) (with load sensing) application, the flow rate required by the user is controlled by sending the user's surplus hydraulic pump (3.0) flow to the tank at the value of user pressure + spring resistance over the hydraulic LS signal transmitted to the compensator with constant pressure adjustment in the safety block (1.0). While the hydraulic tilting/ lowering-lifting cylinder hydraulic block (2.0) is operating without power, the first tilting/lowering proportional directional valve (OR1 ) (2.1), second pressure compensator lifting proportional directional valve (OR2) (2.2), third proportional throttle valve (OR3) (2.9) are in closed position. In Figure-1 , the first pressure compensator lifting proportional direction valve (OR1) (2.1 ) and the second pressure compensator lowering proportional direction valve (OR2) (2.2) do not transmit flow from the hydraulic pump (3.0) to the cylinder (5.0) when the joystick is not used, at the same time LS lines are also kept open to the tank. If the P line is closed and the LS signal pressure is sent to tank at zero pressure the hydraulic pump (3.0) produces a minimum pump output flow rate (Q). Therefore, the hydraulic pump (3.0) remains at minimum pressure and the energy drawn from the system is kept at minimum. While the hydraulic control block (2.0) of the hydraulic tilting/lowering-lifting cylinder operates without energy; the first pressure compensator tilting/lowering proportional directional valve (OR1) (2.1), second pressure compensator lifting proportional directional valve (OR2) (2.2), third proportional throttle valve (OR3) (2.9) have closed zero leakage structure in non-stimulated position, again the other first check valve (2.3), second check valve (2.4), third check valve (2.7), fourth check valve (2.8), first counter balance valve (2.5) and second counter balance valve (2.6) have a zero leakage structure. There is no level loss in the cylinders (5.0) when the joystick is not used in the tilting/lowering cylinder (5.0) (during standby)
When the tilting/lowering cylinder (5.0) is in the tilting/lowering period (x), tilting/lowering can be performed by stimulating the third proportional throttle valve (OR3) (2.9). Regeneration is provided in the cylinder (5.0) by means of the constant pressure adjustable compensator (2.10) and the fourth check valve (2.8). The hose bursting valve (4.0) mounted on the lowering cylinder (5.0) is opened by giving a pilot hydraulic warning to the first pressure compensator tilting /lowering proportional directional valve (OR1) (2.1 ) during lowering. The tilting/lowering speed of the tilting/lowering cylinder (5.0) is calibrated over the third proportional throttle (2.9) in proportion to the movement course of the joystick. It is be provided to operate with minimum hydraulic pump (3.0) flow rate over the tilting/lowering proportional direction valve (OR1) (2.1 ) with first pressure compensator at variable diesel speeds in the tilting position, less hydraulic pump (3.0) flow rate in proportion to the piston rod area in the lowering cylinder, to operate without cavitation in the cylinder by means of the third check valve (2.7) and to operate with low pressure losses. Also at variable diesel speeds, when other users are activated due to its compensator structure, the first pressure compensator tilting/lowering proportional directional control valve (OR1) (2.1) allows for flow sharing.
When the maximum breakout force (lifting position of the vehicle from the ground) is created during the excavation, it is provided from hydraulic pump (3.0) by obtaining the flow rate required for lifting the machine from the ground/excavation depending on user's tilting/lowering cylinder (5.0) diameter depending on joystick movement. Normally, a minimum flow rate of the hydraulic pump (3.0) is required due to the potential energy in the cylinders (5.0) during tilting. For this reason, operation with low pressure losses is provided at variable diesel speeds. The MA pressure sensor (2.12) used in the MA line remains at a pressure of 50 bar and above due to the weight effect on the piston side of the cylinder (5.0), when the tilting/lowering cylinder (5.0) presses to ground level, pressure in the MA line drops below 50 bar, the hydraulic pump (3.0) flow rate is transmitted to the system in proportion to the lowering speed with the joystick movement by stimulating the first pressure compensator tilting proportional directional control valve (OR1) (2.1). The hydraulic pump (3.0) produces a minimum pressure and pump output flow (Q) during the lowering process of the cylinder (5.0), if the joystick is still pulled and the MA pressure sensor (2.12) is below 50 bar, the machine is forced to be lifted from the ground in proportion to the joystick movement by stimulating the first pressure compensator lowering proportional directional valve (OR1) (2.1 ). While it is in lifting the machine from the ground/in excavation position, the oil returning from the cylinder (5.0) returns to the tank at low pressure over the compensator (2.10) and the second counterbalance valve (2.6). Therefore, power drawing from the system is also minimized since the hydraulic pump (3.0) will remain at the minimum flow rate and pressure value until the machine moves to the lifting force from the ground in the tilting period.
The tilting position of the steering wheel and the tilting cylinder during loading is a period often used together by the operator. While the vehicle is loading, the machine is approaching and moving away from the vehicle together with the steering wheel, at the same time, the bucket tilting process is performed by the operator. The hydraulic pump (3.0) flow is not required due to the potential energy of the attachment weight in tilting. Warning of the third proportional throttle valve (2.9) and interruption of warning of the first pressure compensator lowering proportional directional valve (OR1 ) (2.1) is carried out with the information received from the MA pressure sensor (2.12) on the MA line. It is sufficient for the hydraulic pump (3.0) to pump oil as much as the steering wheel requires. While the joystick of the tilting cylinder (5.0) is pulled, The hydraulic pump (3.0) draws power from the system only in proportion to the steering flow rate and pressure, rather than the total flow of the user + steering requirement.
Lifting period (y) of the tilting/lowering cylinder (5.0) is performed by giving a warning to the second pressure compensator lifting proportional directional valve (OR2) (2.2). Calibration of the minimum and maximum speed of the cylinder (5.0) in the lifting period (y) is made by the hydraulic pump (3.0) by pumping the required flow to the system after the second pressure compensator proportional lifting directional valve (OR2) (2.2) is stimulated in proportion to the joystick movement. The flow of the cylinder (5.0) returned by the piston returns to the tank over the first counter balance valve (2.5).
While the first pressure compensator proportional tilting/lowering proportional directional valve (OR1 ) (2.1) and the second pressure compensator lifting proportional directional valve (OR2) (2.2), which are positioned in the hydraulic system, are non-stimulated under normal conditions, the hydraulic pump (3.0) gives minimum flow and pressure, leaks that may occur in the cylinders (5.0) during idle standby in the hydraulic system are prevented, when the third pressure compensator proportional throttle valve (OR3) (2.9) is stimulated, the cylinders (5.0) are operated without cavitation although the hydraulic pump (3.0) is not active in the tilting / lowering period (x) of the cylinders (5.0). In said hydraulic system, in the hydraulic pump (3.0) and the tilting / lowering-lifting cylinder hydraulic control block (2.0), the reduction in fuel consumption and increase in efficiency can be carried to higher levels by means of using smart algorithm software by reading the MA pressure sensor (2.12), MB pressure sensor (2.13) and MP pressure sensor (2.14) installed on the MA, MB, MP lines. In said hydraulic system, flow rate control in lowering cylinder (5.0) with first pressure compensator lowering proportional directional control valve (OR1) (2.1), Flow control and regeneration in idle movements at the cylinder outlet with the third proportional throttle (OR3) (2.9), the fourth check valve (2.8) and the compensator (2.10), transition movements to pressure can be provided during the excavation, by automatically cancelling the regeneration depending on the pressure.

Claims

CLAIMS . A tilting/lowering-lifting cylinder hydraulic control block (2.0) developed for providing energy recovery during tilting on the loader side, during tilting/lowering on the excavator side in arm and bucket cylinders (5.0) in backhoe - loaders, wheel loaders, construction equipment such as wheel and crawler excavators, characterized by comprising;
- First pressure compensator lowering proportional directional valve (OR1 ) (2.1 ) that provides the minimum pump output flow (Q) and standby at minimum pressure when the joystick is not moving, provides flow control in joystick movements according to the needs of the system at user input and provides flow sharing in case of plurality of users, is normally closed and has a zero leakage structure when in the non-stimulated position; ensures that the hydraulic pump (3.0) only operates at the steering pump flow rate and steering pressure value although the joystick is activated when it enters the tilting period with the steering wheel or ensures minimum flow and pressure control in the hydraulic pump (3.0) only during tilting in the bucket cylinder (5.0) without steering;
- Second pressure compensator lifting proportional directional valve (OR2) (2.2) that provides the minimum pump output flow (Q) and standby at minimum pressure when the joystick is not moving, provides flow, pressure control in joystick movements according to the needs of the system at user input and provides flow sharing in case of plurality of users, is normally closed and has zero leakage structure when it operates without power and stimulation;
- Third proportional throttle valve (OR3) (2.9) that is normally closed and has zero leakage structure when in the non-stimulated position, provides flow control at the outlet of the cylinder (5.0) while tilting/lowering-lifting cylinder hydraulic control block (2.0) operates without power;
- Fourth check valve (2.8) and compensator (2.10) that controls the flow rate and pressure at the cylinder (5.0) outlet, provides regeneration in idle movements in the lowering period (x), provides automatic transition period to excavation by cancelling pressure-dependent regeneration during excavation;
- MA pressure sensor (2.12) and MB pressure sensor (2.13) installed on MA and MB ports and pressure MP pressure sensor installed on the P line (2.14) to gain advantage in fuel consumption with smart software algorithms. The tilting/lowering-lifting cylinder hydraulic control block (2.0) according to Claim 1 , characterized in that; the first pressure compensator tilting / lowering proportional directional valve (OR1 ) (2.1), the second pressure compensator lift proportional directional valve (OR2) (2.2), the third proportional throttle valve (OR3) (2.9) is a hydraulic actuated or electro- hydraulic actuated valve. The tilting/lowering-lifting cylinder hydraulic control block (2.0) according to Claim 1 , characterized in that; it is mounted close to the cylinder (5.0) inlet.
PCT/TR2021/050758 2020-08-21 2021-07-30 Hydraulic system providing energy recovery by double spool directional valves during tilting/lowering in bucket cylinder on loader side and in arm / bucket cylinders on excavator side in backhoe loader, wheel loader and excavator machines WO2022039697A1 (en)

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EP21827172.4A EP4200481A1 (en) 2020-08-21 2021-07-30 Hydraulic system providing energy recovery by double spool directional valves during tilting/lowering in bucket cylinder on loader side and in arm / bucket cylinders on excavator side in backhoe loader, wheel loader and excavator machines

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
TR2020/13253A TR202013253A2 (en) 2020-08-21 2020-08-21 STIPPING/DOWNLOADING SYSTEMS WITH DUAL SLOT VALVES IN LOADER SIDE BUCKET ROLLERS, BACKHOE SIDE ARM AND BUCKET CYLINDERS WITH STIPPING/DOWNLOADING SYSTEMS
TR2020/13253 2020-08-21

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WO2022039697A1 true WO2022039697A1 (en) 2022-02-24

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PCT/TR2021/050758 WO2022039697A1 (en) 2020-08-21 2021-07-30 Hydraulic system providing energy recovery by double spool directional valves during tilting/lowering in bucket cylinder on loader side and in arm / bucket cylinders on excavator side in backhoe loader, wheel loader and excavator machines

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4350088A1 (en) * 2022-10-07 2024-04-10 Kramer-Werke GmbH Hydraulic machine with a boom pivotable about a pivot axis

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008014467A (en) * 2006-07-10 2008-01-24 Shin Caterpillar Mitsubishi Ltd Hydraulic control system of working machine
JP2010053969A (en) * 2008-08-28 2010-03-11 Sumitomo (Shi) Construction Machinery Co Ltd Construction machine

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008014467A (en) * 2006-07-10 2008-01-24 Shin Caterpillar Mitsubishi Ltd Hydraulic control system of working machine
JP2010053969A (en) * 2008-08-28 2010-03-11 Sumitomo (Shi) Construction Machinery Co Ltd Construction machine

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4350088A1 (en) * 2022-10-07 2024-04-10 Kramer-Werke GmbH Hydraulic machine with a boom pivotable about a pivot axis

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TR202013253A2 (en) 2021-03-22

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