WO2022199609A1 - 液压系统的流量分配控制方法、设备和装置以及液压系统 - Google Patents

液压系统的流量分配控制方法、设备和装置以及液压系统 Download PDF

Info

Publication number
WO2022199609A1
WO2022199609A1 PCT/CN2022/082482 CN2022082482W WO2022199609A1 WO 2022199609 A1 WO2022199609 A1 WO 2022199609A1 CN 2022082482 W CN2022082482 W CN 2022082482W WO 2022199609 A1 WO2022199609 A1 WO 2022199609A1
Authority
WO
WIPO (PCT)
Prior art keywords
flow
valve
circuit
loop
actuator
Prior art date
Application number
PCT/CN2022/082482
Other languages
English (en)
French (fr)
Inventor
王维
付玲
袁野
张军花
饶德才
张劲
Original Assignee
中联重科股份有限公司
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 中联重科股份有限公司 filed Critical 中联重科股份有限公司
Priority to EP22774265.7A priority Critical patent/EP4317709A1/en
Publication of WO2022199609A1 publication Critical patent/WO2022199609A1/zh

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • 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
    • F15B13/08—Assemblies of units, each for the control of a single servomotor only
    • F15B13/0803—Modular units
    • F15B13/0807—Manifolds
    • 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
    • F15B13/08—Assemblies of units, each for the control of a single servomotor only
    • F15B13/0803—Modular units
    • F15B13/0846—Electrical details
    • 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
    • F15B21/02—Servomotor systems with programme control derived from a store or timing device; Control devices therefor
    • 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3138—Directional control characterised by the positions of the valve element the positions being discrete
    • 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
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • 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
    • F15B2211/41—Flow control characterised by the positions of the valve element
    • F15B2211/413—Flow 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
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41509—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and a directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41509—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and a directional control valve
    • F15B2211/41518—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and a directional control valve being connected to multiple pressure sources
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—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
    • F15B2211/455—Control of flow in the feed line, i.e. meter-in 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
    • F15B2211/60—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
    • F15B2211/665—Methods of control using electronic components
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6652—Control of the pressure source, e.g. control of the swash plate angle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6653—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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6654—Flow rate control

Definitions

  • the present application relates to the field of flow control of hydraulic systems, in particular to a flow distribution control method, device and device for hydraulic systems, as well as hydraulic flow control systems, hydraulic systems and non-transitory computer-readable media.
  • the load-sensing system before or after the valve is mainly used, and the excess pressure is consumed by the constant pressure differential valve to ensure the constant pressure difference between the inlet and outlet of the main spool, so that the flow distribution is only proportional to the The flow area of the two main valve spools is proportional to the flow area. Due to the unreasonable design of the compensation valve, or the poor matching characteristics between the compensation valve and the load, etc., it will lead to poor synchronization and coordination of the operation of different mechanisms, and large impact during rapid movement, etc. Adverse effects, such as uncoordinated operation of excavators, incoherent movements, and large system impact.
  • the flow distribution method mainly relies on the constant pressure differential valve to consume excess pressure to ensure that the pressure difference between the inlet and outlet of the main spool is constant, so that the flow distribution is only proportional to the flow area of the two main valve spools.
  • the two-way main valve can refer to the valve that controls the flow or (and) direction of the aforementioned two-way load. It can be two separate valves, or it can be a two-way valve in a multi-way valve, or it can be an ordinary flow valve (such as a throttle valve). ) can also be an electro-proportional directional flow control valve. Theoretically, the flow rate of each channel does not change with the load pressure of this channel, nor is it affected by the flow rate of other channels. In fact, whether the design of the flow area of the spool of the constant pressure differential valve is reasonable has a great influence on the flow distribution characteristics.
  • the present application provides a flow distribution control method, equipment and device for a hydraulic system.
  • An electronically controlled pressure pump and a flow supplementary valve are used to replace the constant pressure differential valve, and the flow of each branch can be supplemented to solve the flow distribution characteristics of the pressure compensation system.
  • the uneven flow distribution is caused by the influence of the flow area of the constant pressure differential valve.
  • the solution provided in this application is a system that uses an open liquid resistance circuit for flow distribution.
  • the flow compensation scheme is adopted, and the structure is simple, insensitive to pollution and Low investment cost.
  • the present application provides a flow distribution control method for a hydraulic system, on the other hand a flow distribution control device for a hydraulic system, and a flow distribution control device for a hydraulic system on the other hand,
  • a flow distribution control device for a hydraulic system on the other hand
  • Another aspect provides a non-transitory computer readable medium, and another aspect provides a hydraulic system.
  • a first aspect of the present application provides a flow distribution control method for a hydraulic system, the hydraulic system includes N circuits L1 to LN, and the method includes: S1 : comparing the pressure at the inlet of the actuator in each circuit of the hydraulic system P1 ⁇ PN; S2: Determine the loop Lp1 that needs flow compensation according to the comparison result; S3: Perform flow compensation on the loop Lp1 according to the theoretical flow of the loop Lp1 and the actual flow of the actuator in the loop Lp1, wherein, in the loop Lp1 The number of loops is less than or equal to N.
  • a second aspect of the present application provides a flow distribution control device for a hydraulic system, the hydraulic system includes N circuits L1-LN, and the control device includes: a comparison module for comparing the actuators in each circuit of the hydraulic system The pressure at the inlet is P1 ⁇ PN; the determination module is used to determine the loop Lp1 that needs flow compensation according to the comparison result; the flow compensation module performs flow compensation for the loop Lp1 according to the theoretical flow of the loop Lp1 and the actual flow of the actuator in the loop Lp1 , wherein the number of loops in the loop Lp1 is less than or equal to N.
  • a third aspect of the present application provides a flow distribution control device for a hydraulic system, the hydraulic system includes N circuits L1-LN, the device includes one or more processors and a non-transitory computer storing program instructions A readable storage medium, when the one or more processors execute the program instructions, the one or more processors are used to implement the flow control method of the present application.
  • a fourth aspect of the present application provides a non-transitory computer-readable storage medium having stored thereon program instructions that, when executed by one or more processors, the one or more processors for The flow control method of the present application is implemented.
  • a fifth aspect of the present application provides a hydraulic system, comprising: a pump for providing flow to the system; N circuits L1 to LN, each circuit including an actuator and a flow adjustment element connected to the actuator, so The flow regulating element is used to provide flow for the actuator; the hydraulic system further includes a controller, the controller is connected with the pump and the flow regulating element, the controller is configured to: compare each circuit of the hydraulic system According to the comparison results, determine the circuit Lp1 that needs to perform flow compensation; according to the theoretical flow of the circuit Lp1 and the actual flow of the inflowing actuator in the circuit Lp1, the flow compensation is performed on the circuit Lp1, wherein the circuit The number of loops in Lp1 is less than or equal to N.
  • the flow distribution system of the present application does not have a pressure compensation valve, and the flow distribution characteristic is not affected by the pressure compensation valve, and the flow distribution characteristic is good.
  • the present application can realize flow compensation through the electronically controlled pump, the flow supplementary valve (or the auxiliary valve) and the control method thereof, which can break through the limitation of constant pressure compensation before the valve and after the valve required by the traditional load-sensing system;
  • the throttle valve and the flow supplementary valve are in a parallel structure, and two proportional throttle valves are used in parallel, which has high versatility and compact structure.
  • the flow supplement The valve can also be used as a backup valve;
  • the electronically controlled pressure pump of the solution of the present application can conveniently set the pump outlet pressure to be always higher than the load by a fixed value, which is more energy-saving than the traditional load-sensitive pump, has a faster response speed, and is easy to realize electrification control;
  • the scheme of the present application uses the electronic control system to improve the distribution characteristics of system flow through mathematical operations on the data of the electromagnetic proportional throttle valve test, and its flow distribution characteristics and automation degree are higher than those of the traditional load-sensing system.
  • FIG. 1 is a schematic diagram of a prior art valve pre-valve compensation system according to the present application.
  • FIG. 2 is a schematic diagram of a prior art post-valve compensation system according to the present application.
  • FIG. 3 is a block diagram of a flow distribution control system according to an exemplary embodiment of the present application.
  • FIG. 4 is a block diagram of an implementation of a flow distribution control system according to an exemplary embodiment of the present application.
  • FIG. 5 is a flow chart of hydraulic system flow control according to an exemplary embodiment of the present application.
  • FIG. 6 is a specific implementation flowchart of a hydraulic system flow control method according to an exemplary embodiment of the present application.
  • FIG. 7 is a wiring diagram of a controller in a hydraulic system according to an exemplary embodiment of the present application.
  • FIG. 8 is a block diagram of a flow distribution control system including a quad load according to an exemplary implementation of the present application.
  • FIG. 9 is a block diagram of another flow distribution control system according to an exemplary embodiment of the present application.
  • FIG. 10 is an implementation block diagram of another flow distribution control system according to an exemplary embodiment of the present application.
  • FIG. 11 is a simplified block diagram of another flow distribution control system according to an exemplary embodiment of the present application.
  • FIG. 12 is a specific implementation flowchart of another hydraulic system flow control method according to an exemplary embodiment of the present application.
  • FIG. 13 is a wiring diagram of a controller in another hydraulic system according to an exemplary embodiment of the present application.
  • FIG. 14 is an implementation block diagram of an alternative flow distribution control system according to an exemplary embodiment of the present application.
  • 15 is a block diagram of an alternative flow distribution control system implementation according to an exemplary embodiment of the present application.
  • 16 is a block diagram of an alternative flow distribution control system implementation according to an exemplary embodiment of the present application.
  • 17 is a block diagram of a flow control device of a hydraulic system according to an exemplary embodiment of the present application.
  • FIG. 18 is a block diagram of a hydraulic system according to an exemplary embodiment of the present application.
  • the terms "first,” “second,” etc. may be used to describe elements in the exemplary embodiments of the present application. These terms are only used to distinguish one element from another, and the inherent characteristics or order of the corresponding elements are not limited by the terms. Unless otherwise defined, all terms (including technical or scientific terms) used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this application belongs. Those terms as defined in common dictionaries are to be interpreted as having the same meaning as the contextual meaning in the relevant technical field, and are not to be interpreted as having an ideal or overly formal meaning, unless explicitly defined in this application as having such a meaning meaning.
  • control unit may refer to a hardware device including a memory and a processor
  • main control module may refer to a hardware device including a memory and a processor
  • hydroaulic system may refer to a device, equipment or system.
  • the memory or computer-readable storage medium is configured to store program instructions, and the processor is specifically configured to execute the program instructions to perform one or more processes that will be described further below.
  • the following methods may be performed by including a processor in combination with one or more other components, as will be appreciated by those of ordinary skill in the art.
  • connection should be understood in a broad sense, for example, it may be a fixed connection or a detachable connection Connection, or integral connection; may be a direct connection, or an indirect connection through an intermediate medium, and may be the internal communication between two elements or the interaction relationship between the two elements.
  • installation may be a fixed connection or a detachable connection Connection, or integral connection; may be a direct connection, or an indirect connection through an intermediate medium, and may be the internal communication between two elements or the interaction relationship between the two elements.
  • the flow distribution control system and control method of the present application can be applied to the field of construction machinery (eg, excavator leveling condition, loading condition), or crane's luffing and hoisting compound action condition. However, it is not limited to these conditions, as long as it involves compound action conditions between two or multiple loads, this application is applicable.
  • the multi-connected load in the invention can be the boom, stick, bucket and other mechanisms of the excavator, which can be understood as a mechanical structure; the actuator or the actuator in the hydraulic system can be hydraulic oil or hydraulic motor, The actuator converts hydraulic energy into mechanical energy; each circuit in the flow distribution control system refers to a hydraulic circuit that realizes the work (reversing, speed regulation, etc.) of an actuator (or actuator), and a hydraulic circuit Control 1 load.
  • FIG. 1 is a schematic diagram of a prior art valve pre-valve compensation system according to the present application.
  • the functions of each element in FIG. 1 are: the variable pump provides flow for the system; the pump variable displacement mechanism: the pressure at the load feedback port (ie the 7 shuttle valve) is fed back to the pump variable displacement
  • the pump variable displacement mechanism controls the swing angle of the pump swash plate, thereby controlling the change of the pump displacement; pressure compensation valve: the pressure compensation valve is a fixed differential pressure reducing valve to ensure that the pressure drop before and after the adjustable flow valve is a constant value;
  • Adjustable flow valve Control the single-piston hydraulic cylinder by adjusting the flow area of the adjustable flow valve;
  • Shuttle valve Feed back the highest pressure of the system (the one with the highest load pressure among the 8 and 9 single-piston hydraulic cylinders) to the pump variable displacement mechanism ;
  • the flow change of the single-piston hydraulic cylinder that is, the speed change
  • the control of the flow of the single-piston hydraulic cylinder is only related to the flow area of
  • FIG. 2 is a schematic diagram of a prior art post-valve compensation system according to the present application.
  • variable pump provide flow for the system
  • pump variable displacement mechanism the pressure of the load feedback port (ie, the 7 shuttle valve) is fed back to the pump variable displacement
  • the variable displacement mechanism of the pump controls the swing angle of the pump swash plate, thereby controlling the change of the pump displacement
  • adjustable flow valve by adjusting the flow area of the adjustable flow valve, control the single-piston hydraulic cylinder pressure compensation valve: pressure compensation All valves use the same pressure (that is, the pressure at the output port of the shuttle valve 7, whichever is higher in P1 or P2) as the control pressure to control the pressure at the outlet of the flow sensing port (that is, the pressure at the outlet of the flow port 3 and 5 can be adjusted), If the outlet pressure of the pump is the same (that is, the pressure at the inlet of the adjustable flow valve 3 and 5 is the same), the pressure drop on both sides of the adjustable flow valve 3 and 5 is always the same, and the flow rate of the single-piston hydraulic
  • Pre-valve compensation and post-valve compensation are commonly used flow distribution methods in hydraulic systems.
  • Pre-valve compensation means that the pressure compensation valve is arranged between the oil pump and the throttle valve (as shown in Figure 1)
  • post-valve compensation means that the pressure compensation valve is arranged between the throttle valve and the actuator (as shown in Figure 2) .
  • the essence of these two methods is to maintain a constant load pressure difference between the inlet and outlet ports of each throttle valve through the pressure compensation valve.
  • the pre-valve compensation does not have the function of anti-load flow saturation. When the pump oil supply is insufficient, the pre-valve compensation system The flow distribution of the valve is affected by the load difference, and the flow cannot be distributed in proportion to the flow area of the throttle valve.
  • the post-valve compensation has the function of resisting flow saturation.
  • the flow of each channel is not affected by the load pressure change of this channel, nor the flow of other channels.
  • oil flowing through the pipeline and the valve cavity will produce Due to the pressure loss, the flow distribution ratio of each channel is not completely equivalent to the flow area ratio of the throttle valve, and the design form of the flow area of the pressure compensation valve spool has a great influence on the flow distribution characteristics.
  • the pressure compensation valve is used to realize the constant pressure difference ⁇ p between the two ends of the flow area of the main spool, and the pressure compensation valve itself needs to consume a large amount of energy;
  • the pre-valve compensation load-sensing system in the prior art does not have the function of resisting load flow saturation; although the post-valve compensation load-sensing system has the function of resisting flow saturation, the pressure compensator needs to consume a large amount of energy when the load difference is large. energy, not suitable for occasions with large load differences;
  • the two load-sensitive control systems in the prior art, the valve front and the rear valve, are essentially a series structure of two damping holes, which have poor versatility, large energy consumption, and an incompact structure.
  • Figures 1 and 2 there are two orifices in Figure 1, one is the pressure compensation valve 3 (or the pressure compensation valve 5), and the other is the adjustable flow valve 4 (or the adjustable flow valve 6).
  • Figures 1 and 2 there are two orifices in Figure 1, one is the pressure compensation valve 3 (or the pressure compensation valve 5), and the other is the adjustable flow valve 4 (or the adjustable flow valve 6).
  • this application adopts a simple liquid resistance control loop without constant pressure differential valve, and its core idea is to perform active flow compensation for the system with high pressure in multiple load connections, so as to avoid the speed drop of the loop with high load pressure and reduce the excessive load.
  • the flow through the throttle valve is related to the pressure drop before and after the valve (the unit of pressure drop is MPa (or Bar)), the throttle area of the valve port related.
  • the traditional flow distribution method is to keep the pressure drop of each throttle valve constant, then the flow Q through each throttle valve is only related to the throttle area of its valve port, and the flow distribution ratio should theoretically be related to the throttle area ratio of each throttle valve. Consistent.
  • A the throttle area under a certain opening of the valve core (unit is mm2)
  • ⁇ P pressure drop before and after the valve (the unit of pressure drop is MPa (or Bar));
  • FIG. 3 is a block diagram of a flow distribution control system according to an exemplary embodiment of the present application.
  • the flow distribution control system is mainly composed of a pump (which can be an electronically controlled pressure pump), a load direction control valve, an actuator, a flow compensation reversing valve (including a main throttle valve and a flow supplementary valve) and a controller etc. composition.
  • the flow compensating reversing valve is a flow regulating element, which includes a main throttle valve and a flow supplementary valve.
  • the pump may be a pump system of multiple pumps, and the multiple pumps in the pump system may be electronically controlled pressure pumps, variable pumps or quantitative pumps, or various hydraulic pumps may be combined according to actual control needs.
  • the flow distribution control system shown in FIG. 3 includes: a pump for providing flow to the system, a main throttle valve and a flow supplement valve; wherein the main throttle valve and The flow supplementary valve is connected with the pump and the actuator to provide flow for the actuator; the system also includes a controller connected with the pump, the main throttle valve and the flow supplementary valve, and the controller adjusts the flow through the main flow according to a control algorithm Throttle valve and flow make-up valve flow.
  • FIG. 4 is a block diagram of an implementation of a flow distribution control system according to an exemplary embodiment of the present application.
  • the components and labels in Figure 4 are: 1a, 1b: electronically controlled pressure pump; 2a, 2b, 2c: main throttle valve; 3a, 3b, 3c: load direction control valve; 4a, 4b, 4c: Actuator; 5a, 5b, 5c: Flow replenishment valve; 6a, 6b: Pump outlet pressure sensor; 7a, 7b, 7c: Load pressure sensor; 8a, 8b, 8c: Check valve; 9a, 9b, 9c: Check valve; 10: fuel tank; Yp1, Yp2: regulator.
  • the functions of the main elements in FIG. 4 are:
  • the electronically controlled pressure pump 1a By giving the input command of the electronically controlled pressure pump 1a, the electronically controlled pressure pump 1a outputs the pressure oil PP1 which is higher by a fixed value ⁇ P1 than the maximum pressure PFmax of the load connection, that is, formula (2):
  • the electronically controlled pressure pump 1b outputs the pressure oil PP2 which is higher than the maximum pressure PFmax of the load connection by a fixed value ⁇ P2, namely formula (3):
  • ⁇ P1 and ⁇ P2 can be equal or unequal.
  • the flow distribution relationship between different load couplings is related to the main pump outlet pressure PP1, PP2, the main throttle valve 2a, 2b, 2c and the flow supplementary valve 5a, 5b, 5c.
  • the conventional throttling circuit can be greatly widened.
  • the load direction control valves 3a, 3b, and 3c only control the movement direction of the load, and do not participate in the flow distribution process between different couplings. In theory, the larger the flow area of the load directional control valve, the better. Considering the actual installation space and cost, the maximum pressure drop of the load directional control valve does not exceed 30bar.
  • 2a, 2b, 2c main throttle valve is electro-hydraulic proportional type, flow is stepless adjustment; 5a, 5b, 5c flow supplementary valve is also electric proportional type, flow is stepless adjustment.
  • the electro-hydraulic proportional formula is: according to the input electrical signal, the flow or direction of the oil is controlled continuously and proportionally; the flow stepless adjustment is: the flow can be continuously adjusted between the minimum value and the maximum value, and the flow value It is relatively smooth and has no steps (the speed of the actuator is affected by the flow change, and the result is the stepless adjustment of the speed).
  • the flow rate of the F1 circuit is the least, because the pressure difference between the two ends of the throttle port of the circuit with high load is small, so the flow through the ordinary throttle circuit is small.
  • the flow replenishment valves 5a and 5b are controlled to work (that is, the flow replenishment valve ports are opened), and the valve openings are adjusted by controlling the currents of 5a and 5b, the load 1 circuit and the load 2 circuit can be respectively supplemented due to the high load pressure. Reduced drop flow to equalize flow across circuits.
  • the flow distribution control algorithm and control strategy are implemented in the controller.
  • the pressure of the electronically controlled pressure pumps 1a and 1b can be set in the controller, the theoretical flow rate 1, the theoretical flow rate 2, and the theoretical (or imaginary) flow area Aa of the first circuit. , the second circuit theory (or hypothetical) flow area Ab and so on.
  • the theoretical flow is given by the hydraulic engineer when designing the system, and is given according to the requirements of the composite action characteristics of the host (such as cranes, excavators, etc.).
  • 2a, 2b, 2c main throttle valve; it is an electro-hydraulic proportional type, the flow is steplessly regulated, and together with the flow supplementary valves 5a, 5b, 5c are the actuators 4a, 4b, 4c provides flow, and the on-off states of 2a, 2b, 2c and 5a, 5b, and 5c are as described in the function description of the above throttle valve + flow supplementary valve; 4a, 4b, and 4c are actuators: the actuators are generally hydraulic motors or hydraulic cylinders.
  • Such as excavator boom cylinder, rotary motor, etc., is a device that converts hydraulic energy into mechanical energy; 5a, 5b, 5c: flow supplementary valve: it is electro-hydraulic proportional type, the flow is infinitely regulated, which is the same as the main throttle valve 2a, 2a, 5c.
  • 2b and 2c jointly provide flow for the actuators 4a, 4b, and 4c, and the on-off states of 2a, 2b, 2c and 5a, 5b, and 5c are as described in the function description of the above throttle valve + flow supplementary valve;
  • 6a, 6b pump outlet pressure sensor : Detect the pressure of the pump outlet, 7a, 7b, 7c: load pressure sensor; detect the pressure of the load port; 8a, 8b, 8c, 9a, 9b, 9c one-way valve: one-way valve; 10
  • Oil tank place hydraulic oil ;
  • Yp1, Yp2 are the regulators of the electronically controlled pressure pump 1a, 1b, according to the input electrical signal command of the regulator, to realize the regulation of pump pressure and flow.
  • FIG. 5 is a flowchart of a hydraulic system flow control method according to an exemplary embodiment of the present application.
  • the hydraulic system includes multiple circuits (eg, as shown in Figure 3, the hydraulic system includes 3 circuits).
  • step S1 compare the pressures P1-PN at the inlet of the actuator in each circuit of the hydraulic system
  • the circuit Lp1 that needs to be flow-compensated is determined according to the comparison result, and according to one or more embodiments of the present application, the minimum value Pmin of the pressures P1 to PN at the inlet of the actuator is determined, and the Pmin corresponds to The loop is Lp2, and the loop Lp1 that needs to perform flow compensation is: the loops L1 to LN do not include other loops of the loop Lp2, and the flow supplement valve connected to the actuator of the loop Lp2 is closed, wherein the sum of Lp1 and Lp2 is is the total number of circuits N, N is greater than or equal to 2; the flow distribution system shown in Figure 4, wherein, according to the comparison of the pressure value at the inlet of the actuator, Lp1 is the circuit where load 1 and load 2 are located, and Lp2 is where load 3 is located. circuit; that is, the flow supplementary valves 5a and 5b need to be opened, and the flow supplementary valve 5c should be closed;
  • step S3 flow compensation is performed on the loop Lp1 according to the theoretical flow of the loop Lp1 and the actual flow of the actuator in the loop Lp1, wherein the number of loops in the loop Lp1 is less than or equal to N, according to the loop
  • the flow compensation control is performed on the loop Lp1 by adjusting the flow of the flow supplementary valve in the loop Lp1; when the theoretical flow of the loop Lp1 and the flow of the loop Lp1 into the actuator
  • the difference of the actual flow is less than or equal to zero, the flow compensation of the loop Lp1 is terminated.
  • FIG. 6 is a specific implementation flowchart of a hydraulic system flow control method according to an exemplary embodiment of the present application.
  • the hydraulic system includes three circuits (that is, the three circuits include three actuators and actuators, that is, the hydraulic system includes three loads), in,
  • the flow replenishment valve corresponding to the minimum load is not open, and the flow replenishment valves corresponding to other connections must be opened. If PF1>PF2>PF3, both the flow supplementary valves 5a and 5b need to be opened, and the flow supplementary valve 5c does not need to be opened;
  • the theoretical flow rate 1 is related to the theoretical (or imaginary) flow area Aa of the first circuit, the difference ⁇ P1 between the pressure at the outlet of the pump 1a and the maximum pressure PFmax of the load connection, the oil density ⁇ , the flow coefficient Cd, etc.
  • the theoretical The flow area Aa needs to be given according to the requirements of the working conditions. For the convenience of analysis, once the other parameters are set ( ⁇ P1, ⁇ , Cd), they can default to constant values.
  • Theoretical flow 2 is related to the theoretical (or imaginary) flow area Ab of the second circuit, the difference ⁇ P1 between the pump 1b and the maximum pressure PFmax of the load connection, the oil density ⁇ , the flow coefficient Cd, etc.
  • the theoretical flow area Ab It needs to be given according to the requirements of the working conditions. For the convenience of analysis, several other parameters can be defaulted to constant values;
  • step 5 Determine whether the compensation flow is zero (that is, whether the theoretical flow minus the actual flow is zero). If it is greater than zero, it will restart to enter step 1 (load pressure comparison link). If it is less than or equal to zero, the corresponding flow supplementary valve will be closed, and the flow compensation process will end. , that is, the condition for the termination of flow compensation control or flow adjustment is to judge whether the theoretical flow minus the actual flow is less than or equal to 0;
  • FIG. 7 is a wiring diagram of a controller in a hydraulic system according to an exemplary embodiment of the present application.
  • set values can be stored in the controller, including the pressures of the electronically controlled pressure pumps 1a and 1b, and the theoretical flow rates (theoretical flow rates 1 and 2) of each circuit of the hydraulic system.
  • the controller is also capable of receiving pressure feedback signals from the pump port pressure sensors (6a and 6b) and the load pressure sensors (7a, 7b, 7c).
  • the controller can control the pressure at the pump outlet, the flow area of the main core valve, the load direction and the flow area of the flow supplementary valve.
  • the specific parameters are shown in Figure 7.
  • the connection of the controller Relationships are only specific examples in Figure 3-5. When there are multiple loops of the flow system, the connection relationship of the controller can be deduced by analogy, which will not be repeated here.
  • the flow distribution control system and control method of the present application are not only applicable to 2-connected loads and 3-connected loads, but also applicable to 4-connected loads (theoretically, the load can be infinitely Expansion), for the convenience of analysis, the following brief description is made: Assuming that it is extended to a 4-connected load, the relevant components of the hydraulic system can refer to Figure 8. The flow control method in Figure 8 is similar to that of a triple-connected load.
  • the adjustment range for the flow rate is:
  • the degree of freedom is 2; the degree of freedom that needs to be adjusted here in this application can be understood as the need to adjust the flow of the 2-connected load.
  • the degree of freedom is similar to that in the mechanical structure. A point in plane motion needs two coordinates of X and Y (ie, 2 degrees of freedom) to move anywhere, and three coordinates of X, Y, and Z are required for a point to move anywhere in space motion ( i.e. 3 degrees of freedom).
  • the degree of freedom to be adjusted is 3, and the adjustable degree of freedom for the actual pressure difference and overcurrent area is 5, which also meets the requirements for use; for a 5-connected load, the degree of freedom to be adjusted is 4.
  • the adjustable degree of freedom of the actual pressure difference and overcurrent area is 6, which meets the requirements of use.
  • the connection with the lowest load does not need to open the supplementary valve, that is, the degree of freedom N-1 that needs to be adjusted is other than the connection with the lowest load; among them, the actual pressure difference that can be adjusted by the flow area and the freedom that the flow area can be adjusted
  • the degree is (N+1).
  • the present application can also use electromagnetic proportional valves as the main valve and the auxiliary valve, the flow area of the main valve port can be infinitely changed, and the main valve controls the flow area of the valve core through the handle displacement, namely In the initial state, the main valve meets the load flow requirements.
  • the auxiliary valve starts to function, and the throttling area of the auxiliary valve spool is controlled by the electronic control unit.
  • the main valve and the auxiliary valve complete the flow supply together.
  • This embodiment of the present application essentially controls the flow of the sub-valve according to the load change to meet the load demand.
  • the flow distribution control system includes: a pump for providing flow to the system; a main valve and a sub-valve, wherein the main valve and the sub-valve are connected with the pump and the actuator, and are the actuator providing flow; the system further includes a controller connected with the pump, the main valve and the auxiliary valve, the controller controls the opening of the main valve and the auxiliary valve spool according to the control algorithm to adjust the output flow of the actuator.
  • the main valve controls the movement of the spool to adjust the flow through the input electrical signal
  • the auxiliary valve is controlled by the controller to make up for the insufficient flow of the actuator.
  • FIG. 10 is an implementation block diagram of another flow distribution control system according to an exemplary embodiment of the present application.
  • the flow distribution control system is mainly composed of main valve, auxiliary valve, shuttle valve, pressure sensor, safety valve and controller.
  • the marks in Figure 10 are: 1 fuel tank, 2 variable pump, 3, 9, 11 pressure sensors, 4 main valve 1, 5 auxiliary valve 1, 6 main valve 2, 7 auxiliary valve 2, 8, 10 shuttle valves, 12, 13 oil cylinders, 14 safety valves, A-first, B-second.
  • each element in Figure 10 the functions of each element in Figure 10 are: 1. Oil tank: place hydraulic oil; 2. Variable pump: The variable pump outputs a pressure oil PP that is a fixed value higher than the maximum pressure PFmax of the load connection; 3, 9, and 11 pressure Sensor: 3 detects the pump outlet pressure, 9, 11 pressure sensors detect the load-connected pressure, the pressure signal measured by the pressure sensor can be processed by the control unit, and the processed signal is amplified by the amplifier and sent to a1, a2, a3, a4, Then control the opening of the main and auxiliary valve spools, and adjust the input flow of each actuator; 4, 6 main valve: the main valve controls the movement of the spool through the input electrical signal in the system; 5, 7 auxiliary valves: as the main valve The auxiliary valve can make up for the insufficient flow of the actuator; 8, 10 Shuttle valve: obtain the highest load pressure, and feed this pressure to the 2 variable pump; 12, 13 Oil cylinder: Actuator, a device that converts hydraulic energy into mechanical energy, such as Boom cylinder,
  • the main valve 1 and the main valve 2 are of the electric proportional type, and the flow is steplessly adjusted; the flow supplementary valves of the auxiliary valve 1 and the auxiliary valve 2 are also of the electric proportional type, and the flow rate Stepless adjustment.
  • the main valve controls the movement of the spool through the input electrical signal in the system; the auxiliary valve, as the auxiliary valve of the main valve, can make up for the insufficient flow of the actuator; the shuttle valve can obtain the highest load pressure; the pressure sensor can detect the oil circuit pressure in real time, as shown in the figure
  • the pressure sensors 9 and 11 shown in 6 are used to monitor the high pressure load pressure, the pressure sensor 3 is used to monitor the pump outlet pressure, the pressure signal measured by the pressure sensor is fed back to the controller, and the flow distribution control algorithm and control strategy are implemented in the controller.
  • the pressure of the variable pump 2 can be set in the controller, the theoretical flow rate 1 and the theoretical flow rate 2 can be set, and the processed signal can be amplified by the amplifier and sent to a1, a2, a3, a4, and then control the main and auxiliary valve spools the opening degree, adjust the output flow of each actuator.
  • FIG. 11 is a simplified block diagram of another flow distribution control system according to an exemplary embodiment of the present application.
  • R1 main valve 1
  • R2 main valve 2
  • S1 auxiliary valve 1
  • S2 auxiliary valve 2
  • PF1 first actuator (actuator or actuator) Inlet pressure
  • PF2 inlet pressure of the second actuator (actuator or actuator)
  • Q1 flow of the first main valve
  • Q2 flow of the second main valve
  • QS1 flow of the first auxiliary valve
  • QS2 second The flow of the auxiliary valve
  • the R1 and R2 main valves, the S1 and S2 sub-valves, and the main valve and the sub-valve are connected in parallel to supply oil to a certain load. Therefore, the above-mentioned embodiments of the present application are equivalent to increasing the load circuit. It is especially suitable for occasions with high speed control requirements.
  • FIG. 12 is a specific implementation flowchart of another hydraulic system flow control method according to an exemplary embodiment of the present application.
  • the hydraulic system includes two circuits (that is, the two circuits include two actuators and actuators, that is, the hydraulic system includes two loads).
  • the difference between the theoretical flow and the actual flow is the compensation flow, and the flow compensation can be satisfied by adjusting the flow area of the auxiliary electromagnetic proportional reversing valve.
  • ⁇ P 1 (or ⁇ P 1 ′) is the actual pressure drop of the first load, which is obtained by detecting the pump outlet pressure P P (or P P1 ) and the first actuator inlet pressure P F1
  • ⁇ P 2 (or ⁇ P 2 ′) is the actual pressure drop of the second connection load, which is detected by detecting the pump outlet
  • the difference between the pressure P P (or P P2 ) and the inlet pressure P F2 of the second actuator, through ⁇ P 2 (or ⁇ P 2 ), formula (1), the second actual flow rate 2 can be calculated.
  • FIG. 13 is a wiring diagram of a controller in another hydraulic system according to an exemplary embodiment of the present application.
  • the set value can be stored in the controller, and the set value includes the pressure value of the pump and the theoretical flow rate of each circuit of the hydraulic system (theoretical flow rate 1 and 2).
  • the controller is also capable of receiving pressure feedback signals from load pressure sensors (3, 9, 11).
  • the controller can control the pressure at the pump outlet, the flow area of the main valve, and the flow area of the auxiliary valve.
  • the specific parameters are shown in Figure 13.
  • the connection relationship of the controller is only shown in Figure 13. Specific examples in 9-12. When there are multiple loops of the flow system, the connection relationship of the controller can be deduced by analogy, which will not be repeated here.
  • the first auxiliary valve (the auxiliary main valve R1 works) / 5 A1 Main spool 1 flow area mm2 6 AS1 Secondary spool 1 flow area mm2 7 Q1
  • the flow of the first main valve L/min 8 QS1 The flow of the first sub-valve L/min 9 QA First Union Theory Total Flow L/min 10 Q A ′
  • the second auxiliary valve (auxiliary main valve R2 works) / 13 A1 Main spool 2 flow area mm2 14 AS1 Secondary spool 2 flow area mm2 15 Q2
  • the flow of the second main valve L/min 16 QS2 The flow of the second sub-valve L/min 17 QB Second Union Theory Total Flow L/min 18 Q B ′
  • FIG. 14 is an implementation block diagram of an alternative flow distribution control system according to an exemplary embodiment of the present application.
  • FIG. 14 Elements in Fig. 14 are marked as follows: 1a, 1b: electronically controlled pressure pump; 2a, 2b, 2c: main throttle valve; 3a, 3b, 3c: load directional control valve; 4a, 4b, 4c: actuator; 5a , 5b, 5c: flow supplementary valve; 6a, 6b: pump outlet pressure sensor; 7a, 7b, 7c: shuttle valve; 8a, 8b, 8c, 8d, 8e, 8f: one-way valve; 9a, 9b, 9c: pressure sensor; 10: fuel tank.
  • 1a, 1b electronically controlled pressure pump
  • 2a, 2b, 2c main throttle valve
  • 3a, 3b, 3c load directional control valve
  • 4a, 4b, 4c actuator
  • 5a , 5b, 5c flow supplementary valve
  • 6a, 6b pump outlet pressure sensor
  • 7a, 7b, 7c shuttle valve
  • 8a, 8b, 8c, 8d, 8e, 8f one-way valve
  • an alternative flow distribution control system scheme can be used for a shuttle valve instead of a pressure sensor, as shown in Figure 14.
  • the shuttle valve is connected to both ends of the actuator, and the pressure of each connection can also be obtained.
  • the branch with high pressure can be obtained through the control unit, and then the opening of the flow replenishment valve can be controlled to replenish oil.
  • the shuttle valve can identify the pressure of each load working oil port, and the pressure sensor can obtain the values of two or more shuttle valves, so that the controller or flow distribution scheme of the present application can select The higher pressure circuits are flow compensated.
  • the flow distribution control system is not limited to using a variable pump, but can be replaced by a fixed pump, which also satisfies the original system characteristics. It is also possible to reduce 2 pumps to 1 to supply oil to the entire system.
  • the flow distribution control system or hydraulic system of the present application may integrate a directional valve and a proportional throttle valve into a proportional directional valve, and by controlling the primary proportional directional valve and the secondary proportional directional valve, the same can be achieved.
  • This control scheme is not limited to the application of the shuttle valve, in addition to the shuttle valve, it can also be used for the pressure sensor instead.
  • an alternative flow distribution control system according to an exemplary embodiment of the present application which replaces the shuttle valve with a plurality of pressure sensors, that is, a series of pressure sensors in each branch, can also achieve the invention described Function, the branch with high pressure is selected through the control unit, and the command signal corresponding to the auxiliary valve is given.
  • the flow distribution control system of the present application is not limited to the structure shown in FIG. 10 .
  • FIG. 10 it consists of two electromagnetic proportional valves, which can be replaced by two electromagnetic proportional valves and a shuttle valve.
  • the composed valve block is shown in Figure 16. The difference between Figure 10 and Figure 16 is whether the valve block contains a shuttle valve, see serial numbers 8 and 9 in the figure.
  • 17 is a block diagram of a flow control device of a hydraulic system according to an exemplary embodiment of the present application.
  • the flow distribution control device of the hydraulic system includes: a comparison module for comparing the pressures P1-PN at the inlet of the actuator in each circuit of the hydraulic system; a determination module for determining the need for flow compensation according to the comparison result
  • the flow compensation module is used to perform flow compensation on the loop Lp1 according to the theoretical flow of the loop Lp1 and the actual flow of the inflowing actuator in the loop Lp1, wherein the hydraulic system includes N parallel loops L1-LN, so The number of loops in the loop Lp1 is less than or equal to N.
  • the above-mentioned figure in the present application has a circuit with multiple loads, or a circuit with multiple actuators).
  • FIG. 18 is a block diagram of a hydraulic system according to an exemplary embodiment of the present application.
  • the hydraulic system includes: a pump for providing flow to the system; N circuits L1 to LN, each of which includes an actuator and a flow adjustment element connected to the actuator, the flow adjustment element
  • the hydraulic system further includes a controller, the controller is connected with the pump and the flow regulating element, and the controller is configured to: compare the inlet of the actuator in each circuit of the hydraulic system According to the comparison result, determine the circuit Lp1 that needs flow compensation; according to the theoretical flow of the circuit Lp1 and the actual flow of the actuator flowing into the circuit Lp1, the flow compensation is performed on the circuit Lp1, wherein the circuit The number of loops in Lp1 is less than or equal to N.
  • the present application also provides a non-transitory computer-readable storage medium having stored thereon program instructions that, when executed by one or more processors, are used to implement the above-described the methods or processes in the various embodiments of the present application.
  • the present application further provides a hydraulic system, including the flow distribution control system exemplified in the present application, a flow distribution control device, a flow distribution control device, a non-transitory computer control system having the above-mentioned non-transitory computer Read the storage medium, or adopt the flow distribution control method of this application.
  • the controller or control device of the present application may use data stored in a non-transitory computer and/or machine-readable medium (eg, hard drive, flash memory, read only memory, optical disk, digital multifunction encoded instructions (e.g., computer and/or machine readable instructions) on disk, cache, random access memory, and/or any other storage device or storage disk) to implement the processing of the control methods described above in this application, Information is stored for any period of time (eg, for extended periods of time, permanent, ephemeral instances, temporary caches, and/or information caches) in non-transitory computer and/or machine-readable media.
  • the term "non-transitory computer-readable medium" is expressly defined to include any type of computer-readable storage device and/or storage disk, and to exclude propagating signals and to exclude transmission media.
  • control device, control device, main control system or control module of the present application may include one or more processors or may include a non-transitory computer-readable medium internally.
  • the control device for flow distribution (main control system or control module) may include a microcontroller MCU, which is arranged in the hydraulic system and is used to implement various operations of flow distribution control and implement various functions.
  • the processors in the control device may be such as, but not limited to, one or more single-core or multi-core processors.
  • the processor(s) may include any combination of general-purpose processors and special-purpose processors (eg, graphics processors, application processors, etc.).
  • a processor may be coupled thereto and/or may include a memory/storage device, and may be configured to execute instructions stored in the memory/storage device to implement various applications and/or various applications running on the controller herein operating system.
  • the electronically controlled pressure pump 1a supplies oil to the main throttle valve, and the electronically controlled pressure pump 1b supplies oil to the flow supplementary valve.
  • the dynamic balance between the theoretical flow and the actual flow is realized through closed-loop control (that is, the compensation flow is zero), so as to achieve The flow distribution between different links meets the requirements.
  • the loop theoretical (or imaginary) flow area Aa, Ab, and Ac are input parameters, which are set according to the actual operating conditions (which can be given by the speed requirements). For the convenience of analysis, once the other parameters are set ( ⁇ P1, ⁇ , Cd) can default to constant values.
  • the system and control method of the present application are more energy-saving, have a faster response speed, and are easy to realize electrification control.
  • the main valve obtains the initial flow demand through the handle displacement - the flow area of the spool, and the auxiliary valve plays a role when the load changes, realizing flow compensation, that is, the main valve and the auxiliary valve work at the same time.
  • the mathematical operation is carried out by using the pressure difference between the high-pressure branch and the pump outlet, and the transmission of electrical signals improves the control speed and control accuracy.
  • Example 1 A flow distribution control system, characterized by comprising: a pump for providing flow to the system; N circuits, each circuit including a main throttle valve, a flow supplementary valve, and a connection with the main throttle An actuator connected to a valve and a flow replenishment valve, wherein the pump provides flow for each circuit; a controller connected to the pump, to each circuit, the controller distributes the flow rate across each circuit according to a control algorithm The flow of the main throttle valve and the flow supplementary valve; wherein, the N is greater than or equal to 2.
  • Example 2 The system according to Example 1, wherein each circuit further includes a load direction control valve for controlling the direction of movement of the load, the input end of the load direction control valve being connected to the main throttle valve and the flow supplement The valve output end is connected, the output end of the load direction control valve is connected with the actuator, and the controller is connected with the load direction control valve.
  • load direction control valve for controlling the direction of movement of the load
  • Example 3 The system of Example 1, wherein the main throttle valve and the flow make-up valve in each circuit are connected in parallel.
  • Example 4 The system of Example 1, wherein the pumps include at least a first pump and a second pump, wherein the first pump provides flow to the main throttle valve and the second pump is The flow replenishment valve provides flow.
  • Example 5 The system of Example 1, further comprising: a pressure sensing element comprising: a pump outlet pressure sensor located at the pump outlet and a main throttle valve located in each circuit And the load pressure sensor at the output of the flow supplement valve, the pump outlet pressure sensor and the load pressure sensor send the detected pressure to the controller.
  • a pressure sensing element comprising: a pump outlet pressure sensor located at the pump outlet and a main throttle valve located in each circuit And the load pressure sensor at the output of the flow supplement valve, the pump outlet pressure sensor and the load pressure sensor send the detected pressure to the controller.
  • Example 6 The system of Example 1, wherein the pump is an electronically controlled pressure pump, a variable displacement pump, or a quantitative pump.
  • Example 7 The system of Example 1, wherein the number of main throttle valves is equal to the number of flow make-up valves in each circuit.
  • Example 8 The system of Example 1, wherein the main throttle valve and the flow supplement valve are electro-proportional flow steplessly regulated valves, or proportional directional valves.
  • Example 9 The system of Example 1, wherein each circuit further comprises a check valve between the pump and the main throttle valve, and a make-up valve between the pump and the flow one-way valve between.
  • Example 10 The system of Example 1, wherein the controller adjusts the valve opening of the flow supplement valve by controlling the current of the flow supplement valve.
  • Example 11 The system of Example 1, further comprising: a pressure sensing element comprising: a pump outlet pressure sensor located at the pump outlet and a shuttle located across the loop-connected load valve, the pump outlet pressure sensor and the shuttle valve send the acquired pressure to the controller.
  • a pressure sensing element comprising: a pump outlet pressure sensor located at the pump outlet and a shuttle located across the loop-connected load valve, the pump outlet pressure sensor and the shuttle valve send the acquired pressure to the controller.
  • Example 12 The system of Example 1, further comprising: a regulator connected to the pump to regulate the pressure and flow of the pump according to electrical signal instructions from the controller.
  • Example 1 A flow regulation and control system, characterized by comprising: a pump for providing flow to the system; N circuits, each circuit comprising: a main valve, a sub-valve, and a connection with the main valve and the sub-valve A connected actuator, wherein the pump supplies flow for each circuit; a controller connected with the pump and each circuit, the controller controls the opening of the main valve and the spool of the auxiliary valve in each circuit according to a control algorithm to adjust the output flow of the actuator, wherein the N is greater than or equal to 2.
  • Example 2 The system according to Example 1, wherein the main valve controls the movement of the spool to adjust the flow through an input electrical signal, and the auxiliary valve is controlled by the controller to compensate for the flow of the actuator insufficient.
  • Example 3 The system of example 1, wherein, in each circuit, the primary and secondary valves are connected in parallel.
  • Example 4 The system of Example 1, further comprising a pressure sensor at the input of the actuator and a pressure sensor at the outlet of the pump, the pressure sensor transmitting the detected pressure signal to the controller .
  • Example 5 The system of Example 1, wherein the system further comprises a pressure sensor located at an actuator for acquiring the pressure of the actuator connected to a load and selecting a circuit with a high pressure in the system .
  • Example 6 The system of Example 1, wherein the number of primary valves is equal to the number of secondary valves in each circuit.
  • Example 7 The system of Example 1, wherein the main valve and the auxiliary valve are electro-proportional flow steplessly regulated valves, or proportional directional valves.
  • Example 8 The system of Example 1, further comprising a safety valve connected to the pump, the safety valve being used for safety protection of the pump.
  • Example 9 The system of Example 1, wherein the controller controls the flow through the secondary valve according to a change in the load connected to the actuator to meet the demand of the load.
  • Example 10 The system of Example 1, wherein the main valve and the auxiliary valve are valve blocks consisting of a solenoid proportional valve and a shuttle valve.
  • Example 11 The system of Example 1, wherein the primary valve obtains an initial flow demand by displacing the spool flow area, and the controller adjusts the flow through the secondary valve when the load on the actuator changes To achieve the flow regulation control of the loop.
  • Example 1 A flow distribution control method for a hydraulic system, the hydraulic system includes N circuits L1-LN, and the method includes: S1: comparing the pressures P1-PN at the inlet of the actuator in each circuit of the hydraulic system; S2 : Determine the loop Lp1 that needs to be flow-compensated according to the comparison result; S3: Perform flow compensation on the loop Lp1 according to the theoretical flow of the loop Lp1 and the actual flow of the actuator flowing into the loop Lp1, wherein the flow of the loop Lp1 The number of loops is less than or equal to N.
  • Example 2 According to the method described in Example 1, determine the minimum value Pmin of the pressures P1 to PN at the inlet of the actuator, the circuit corresponding to the Pmin is Lp2, and the circuit Lp1 that needs to perform flow compensation is: the The other circuits of the circuit Lp2 are not included in the circuits L1 to LN.
  • Example 3 The method according to example 1 or 2, wherein the N circuits L1 to LN are connected in parallel, each circuit comprising an actuator and a main throttle valve and a flow supplement valve connected to the actuator, wherein the The main throttle valve and the flow supplementary valve are connected in parallel, wherein the N is greater than or equal to 2; wherein the step S2 includes: closing the flow supplementary valve connected to the actuator of the circuit Lp2.
  • Example 4 The method according to Example 1, wherein in the step S3, according to the difference between the theoretical flow rate of the loop Lp1 and the actual flow rate flowing into the actuator in the loop Lp1, the flow rate of the flow supplement valve in the loop Lp1 is adjusted to The loop Lp1 performs flow compensation control.
  • Example 5 The method according to Example 4, the step S3 comprising: performing flow compensation control by adjusting the flow rate of the flow supplement valve in the loop Lp1 that needs flow compensation.
  • Example 6 The method according to Example 1, wherein the step S3 includes: when the difference between the theoretical flow of the loop Lp1 and the actual flow of the actuator in the loop Lp1 is less than or equal to zero, ending the flow compensation of the loop Lp1.
  • Example 7 The method of Example 3, wherein the actual flow into the actuator in the loop Lp1 is the sum of the flow through the main throttle valve in the loop Lp1 and the flow through the supplemental flow valve in the loop Lp1.
  • Example 8 According to the method described in Example 1, the theoretical flow rate of the circuit Lp1 is set according to different working conditions, and the working conditions include at least pressure difference and flow area; the theoretical flow rate of the circuit Lp1 and the pressure at the pump outlet in the hydraulic system and the circuit The difference between the maximum pressures, the hydraulic fluid density, the flow coefficient and the flow area of the circuit Lp1 are related.
  • Example 9 The method of Example 8, wherein the theoretical flow of circuit Lp1 and the difference between the pressure at the pump outlet in the hydraulic system and the maximum pressure of the circuit, the hydraulic fluid density, the flow coefficient, and the flow area of the circuit Lp1 related.
  • Example 10 The method of Example 9, wherein the flow area of the circuit is related to operating conditions of the hydraulic system.
  • Example 11 The method according to Example 1, wherein the hydraulic system includes two parallel circuits, each circuit including an actuator and a main valve and a secondary valve connected to the actuator; wherein the step S2 includes: when the two When the pressures at the inlets of the actuators in the circuits are equal, the auxiliary valve in each circuit is closed; when the pressures at the inlets of the actuators in the two circuits are not equal, the circuit with the higher pressure is selected as the flow compensation circuit.
  • Example 12 The method according to Example 11, wherein the step S3 includes: if the difference between the theoretical flow rate of the circuit with higher pressure and the actual flow rate flowing into the actuator in the circuit is greater than zero, opening the circuit with higher pressure and close the auxiliary valve of the other circuit; if the difference between the theoretical flow of the circuit with higher pressure and the actual flow of the actuator flowing into the circuit is less than or equal to zero, the flow compensation of the circuit with higher pressure will be terminated.
  • Example 13 The method according to Example 11, the step S2 further comprising: selecting a circuit with a higher pressure as a flow compensation circuit according to a pressure sensor in the hydraulic system.
  • Example 14 The method of Example 11, wherein the primary and secondary valves in the circuit are connected in parallel.
  • Example 15 The method of example 3, the hydraulic system including a pump providing flow to the hydraulic system, the pump including at least a first pump and a second pump, wherein the first pump provides the main throttle valve flow, the second pump provides flow to the flow replenishment valve.
  • Example 16 The method of Example 15, wherein the degree of freedom over which the method can perform compensation control is at most N-1; the degree of freedom over which the method is capable of compensating for flow or differential pressure is at most N+1.
  • a flow distribution control device for a hydraulic system the hydraulic system includes N circuits L1 to LN, and the control device includes: a comparison module for comparing the pressure P1 at the inlet of the actuator in each circuit of the hydraulic system ⁇ PN; a determination module, used to determine the loop Lp1 that needs to be flow-compensated according to the comparison result; a flow compensation module, used to perform a flow measurement on the loop Lp1 according to the theoretical flow of the loop Lp1 and the actual flow of the actuator flowing into the loop Lp1 compensation, wherein the number of loops in the loop Lp1 is less than or equal to N.
  • Example 2 The device according to Example 1, wherein the determination module is used to determine the minimum value Pmin of the pressures P1 to PN at the inlet of the actuator, the circuit corresponding to the Pmin is Lp2, and the required The loop Lp1 that performs flow compensation is another loop that does not include the loop Lp2 among the N loops L1 to LN.
  • Example 3 The apparatus according to example 1 or 2, wherein the N circuits L1 to LN are connected in parallel, and each circuit includes an actuator and a main throttle valve and a flow supplement valve connected to the actuator, wherein the The main throttle valve and the flow supplementary valve are connected in parallel; wherein N is greater than or equal to 2; wherein the determination module is used to close the flow supplementary valve connected to the actuator of the loop Lp2.
  • Example 4 The device according to Example 1, wherein the flow compensation module is further configured to: supplement the flow rate of the valve by adjusting the flow rate in the loop Lp1 according to the difference between the theoretical flow rate of the loop Lp1 and the actual flow rate flowing into the actuator in the loop Lp1 The flow compensation control is performed on the loop Lp1.
  • Example 5 The apparatus of Example 1, wherein the flow compensation module is further configured to: perform flow compensation control by adjusting the flow rate of the flow supplement valve in the loop Lp1 that needs flow compensation.
  • Example 6 The device according to Example 1, wherein the flow compensation module is further configured to: when the difference between the theoretical flow of the loop Lp1 and the actual flow of the actuator in the loop Lp1 is less than or equal to zero, end the flow compensation of the loop Lp1.
  • Example 7 The apparatus of Example 3, wherein the actual flow into the actuator in the loop Lp1 is the sum of the flow through the main throttle valve in the loop Lp1 and the flow through the supplemental flow valve in the loop Lp1 .
  • Example 8 The device according to Example 1, wherein the theoretical flow rate of the loop Lp1 is set according to different operating conditions, and the operating conditions include at least pressure difference and flow area.
  • Example 9 The apparatus of Example 1, wherein the theoretical flow of circuit Lp1 is related to the difference between the pressure at the pump outlet in the hydraulic system and the maximum pressure of the circuit, the hydraulic fluid density, the flow coefficient, and the flow area of the circuit Lp1 .
  • Example 10 The apparatus of Example 9, wherein the flow area of the circuit Lp1 is related to the operating condition requirements of the hydraulic system.
  • Example 11 The apparatus of Example 1, wherein the hydraulic system includes two parallel circuits, each circuit including an actuator and a main valve and a secondary valve connected to the actuator; wherein the determining module is configured to: when the two When the pressures at the inlets of the actuators in the two circuits are equal, the auxiliary valve in each circuit is closed; when the pressures at the inlets of the actuators in the two circuits are not equal, the circuit with the higher pressure is selected as the flow compensation circuit.
  • Example 12 The device according to Example 11, wherein the flow compensation module is configured to: if the difference between the theoretical flow rate of the circuit with higher pressure and the actual flow rate flowing into the actuator in the circuit is greater than zero, turn on the pressure comparator. The auxiliary valve of the large circuit and the auxiliary valve of the other circuit are closed; if the difference between the theoretical flow of the circuit with higher pressure and the actual flow of the actuator flowing into the circuit is less than or equal to zero, the flow compensation of the circuit with higher pressure is terminated.
  • Example 13 The apparatus according to Example 11, wherein the determining module is configured to: select a circuit with a higher pressure as a flow compensation circuit according to a pressure sensor valve in the hydraulic system.
  • Example 14 The apparatus of Example 11, wherein the primary and secondary valves in the circuit are connected in parallel.
  • Example 15 The apparatus of example 3, the hydraulic system comprising a pump providing flow to the hydraulic system, the pump comprising at least a first pump and a second pump, wherein the first pump provides the main throttle valve flow, the second pump provides flow to the flow replenishment valve.
  • Example 16 The device according to Example 15, wherein the degree of freedom of the flow rate that the device can perform compensation control is at most N-1;
  • Example 1 A flow distribution control device for a hydraulic system, the hydraulic system comprising N circuits L1-LN, the device comprising one or more processors and a non-transitory computer-readable storage medium storing program instructions, When the one or more processors execute the program instructions, the one or more processors are configured to implement the method according to any one of the third set of examples 1-16 above.
  • Example 1 A non-transitory computer-readable storage medium having stored thereon program instructions that, when executed by one or more processors, are used to implement the third The method of any of Group Examples 1-16.
  • Example 1 A hydraulic system, comprising: a pump for providing flow to the system; N circuits L1 to LN, each of which includes an actuator and a flow regulating element connected to the actuator, the flow regulating element using for providing flow for the actuator; the hydraulic system further includes a controller, the controller is connected with the pump and the flow regulating element, the controller is configured to: compare the inlet of the actuator in each circuit of the hydraulic system According to the comparison result, determine the circuit Lp1 that needs to be compensated for the flow; according to the theoretical flow of the circuit Lp1 and the actual flow of the actuator flowing into the circuit Lp1, the flow compensation is performed on the circuit Lp1, wherein the circuit Lp1 The number of loops in is less than or equal to N.
  • Example 2 The hydraulic system of Example 1, wherein the flow regulating element includes a main throttle valve and a flow supplement valve.
  • Example 3 The hydraulic system of Example 2, wherein the main throttle valve and the flow make-up valve are connected in parallel.
  • Example 4 The hydraulic system of Example 1, wherein the flow regulating element includes a primary valve and a secondary valve.
  • Example 5 The hydraulic system of Example 4, wherein the primary and secondary valves are connected in parallel.
  • Example 6 The hydraulic system according to Example 1, wherein the controller is further configured to: determine the minimum value Pmin of the pressures P1 to PN at the inlet of the actuator, the circuit corresponding to the Pmin is Lp2, and the required The circuit Lp1 that performs flow compensation is another circuit that does not include the circuit Lp2 among the circuits L1 to LN.
  • Example 7 The hydraulic system according to example 1 or 6, wherein the N circuits L1 to LN are connected in parallel, and each circuit includes an actuator, and a main throttle valve and a flow supplement valve connected to the actuator, wherein The main throttle valve and the flow supplementary valve are connected in parallel, and the N is greater than or equal to 2; wherein the controller is further configured to: close the flow supplementary valve connected to the actuator of the circuit Lp2.
  • Example 8 The hydraulic system of Example 1, wherein the controller is further configured to: based on the difference between the theoretical flow of the circuit Lp1 and the actual flow into the actuator in the circuit Lp1, to adjust the required flow.
  • the compensated loop Lp1 performs flow compensation control.
  • Example 9 The hydraulic system of Example 7, wherein the controller is further configured to perform flow compensation by adjusting the flow of a flow make-up valve in the circuit Lp1 that requires flow compensation.
  • Example 10 The hydraulic system of Example 1, wherein the controller is further configured to: when the difference between the theoretical flow rate of the circuit Lp1 and the actual flow rate flowing into the actuator in the circuit Lp1 is less than or equal to zero, end the flow compensation of the circuit Lp1 .
  • Example 11 The hydraulic system of Example 3, wherein the actual flow into the actuator in the circuit is the sum of the flow through the main throttle valve in the circuit Lp1 and the flow through the supplemental flow valve in the circuit Lp1 .
  • Example 12 The hydraulic system according to Example 1, wherein the theoretical flow rate of the circuit Lp1 is set according to different operating conditions, and the operating conditions at least include differential pressure and flow area.
  • Example 13 The hydraulic system of Example 12, wherein the theoretical flow of circuit Lp1 and the difference between the pressure at the pump outlet in the hydraulic system and the maximum pressure of the circuit, the hydraulic fluid density, the flow coefficient, and the flow area of the circuit Lp1 related.
  • Example 14 The hydraulic system of Example 13, wherein the flow area of the circuit Lp1 is related to operating conditions of the hydraulic system.
  • Example 15 The hydraulic system of Example 1, comprising two parallel circuits, each circuit comprising an actuator and a main valve and a secondary valve connected to the actuator; wherein the controller is further configured to: when the two If the pressures at the inlets of the actuators in the circuits are equal, the auxiliary valve in each circuit is closed; when the pressures at the inlets of the actuators in the two circuits are not equal, the circuit with the higher pressure is selected as the flow compensation circuit.
  • Example 16 The hydraulic system of Example 15, wherein the controller is further configured to open the circuit if the difference between the theoretical flow of the higher pressure circuit and the actual flow into the actuator in the circuit is greater than zero.
  • Example 17 The hydraulic system of Example 15, wherein the controller is further configured to select a higher pressure circuit as the flow compensated circuit according to a pressure sensor in the hydraulic system.
  • Example 18 The hydraulic system of Example 3, the pumps comprising at least a first pump and a second pump, wherein the first pump provides flow to the main throttle valve and the second pump provides the flow The make-up valve provides flow.
  • Example 19 The apparatus of Example 18, wherein the system can compensate for flow with a degree of freedom of at most N-1; the system can compensate for a flow or differential pressure with a degree of freedom of at most N+1.
  • the present application also discloses a hydraulic system, including the flow distribution control system exemplified above in the present application, a flow distribution control device, a flow distribution control device, having the non-transitory computer-readable storage medium described above in the present application, or using the present application.
  • the applied flow control method including the flow distribution control system exemplified above in the present application, a flow distribution control device, a flow distribution control device, having the non-transitory computer-readable storage medium described above in the present application, or using the present application.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

一种液压系统的流量分配控制方法，其中液压系统包括N个回路L1～LN，该流量分配控制方法包括以下步骤：S1：比较液压系统每个回路中执行元件入口处的压力P1～PN；S2：根据比较结果确定需要进行流量补偿的回路Lp1；S3：根据回路Lp1的理论流量和回路Lp1中流入执行元件实际流量，对回路Lp1进行流量补偿，其中，回路Lp1中的回路的数量小于或等于N。还公开了一种液压系统的流量分配控制设备、流量分配控制装置、液压系统和非暂时性计算机可读介质。采用电控压力泵加流量补充阀代替定压差阀，可对各支路流量进行补充，以解决压力补偿系统流量分配特性受定压差阀过流面积影响产生的流量分配不均现象，采用流量补偿的方案，构造简单，对污染不敏感且投资成本低。

Description

液压系统的流量分配控制方法、设备和装置以及液压系统
相关申请的交叉引用
本申请要求2021年3月23日提交的中国专利申请202110309855.2的权益，该申请的内容通过引用被合并于本文。
技术领域
本申请涉及液压系统的流量控制领域，具体涉及一种液压系统的流量分配控制方法、设备和装置，以及液压流量控制系统、液压系统和非暂时性计算机可读介质。
背景技术
在现有的液压系统流量控制中，主要采用阀前或阀后负载敏感系统，依靠定压差阀消耗掉多余的压力，保证主阀芯进出口之间的压差恒定，使流量分配只与两联主阀阀芯的过流面积成正比，因补偿阀设计不合理、或补偿阀与负载之间的匹配特性不好等因素，会导致不同机构运行同步协调性差、快速运动时冲击大等不良影响，如挖掘机作业不协调、动作不连贯、系统冲击大等。
当两联负载(两联负载可以是不同执行机构之间的负载,如挖掘机的动臂与斗杆负载，也可以是起重机变幅与起升负载，等)不一致时，目前现有技术中的流量分配方式，主要依靠定压差阀消耗掉多余的压力，保证主阀芯进出口之间的压差恒定，使流量分配只与两联主阀阀芯的过流面积成正比。
两联主阀可以指控制前述两联负载流量或(和)方向的阀，可以是两个单独的阀，也可以是多路阀中的两联，既可以是普通流量阀(如节流阀)也可以是电比例方向流量控制阀。理论上各通道的流量既不随本通道负载压力的变化而变化，也不受其他通道流量的影响。实际上，定压差阀阀芯过流面积设计是否合理，对流量分配特性影响较大。
上述在背景部分公开的信息仅用于对本申请的背景做进一步的理解，因此它可以包含对于本领域普通技术人员已知的不构成现有技术的信息。
发明内容
本申请提供了一种液压系统的流量分配控制方法、设备和装置，采用电控压力泵加流量补充阀代替定压差阀，可对各支路流量进行补充，以解决压力补偿系统流量分配特性受定压差阀过流面积影响产生的流量分配不均现象，本申请提供的方案为一种采用开式液阻回路进行流量分配的系统，采用流量补偿方案,构造简单，对污染不敏感且投资成本低。
为此，本申请的一方面提供了一种液压系统的流量分配控制方法，另一方面提供了一种液压系统的流量分配控制设备，另一方面提供了一种液压系统的流量分配控制装置，另一方面提供了一种非暂时性计算机可读介质，另一方面提供了一种液压系统。
本申请的第一方面提供了一种液压系统的流量分配控制方法，所述液压系统包括N个回路L1～LN，所述方法包括：S1：比较液压系统每个回路中执行元件入口处的压力P1～PN；S2：根据比较结果确定需要进行流量补偿的回路Lp1；S3：根据回路Lp1的理论流量和回路Lp1中流入执行元件实际流量，对回路Lp1进行流量补偿，其中，所述回路Lp1中的回路的数量小于或等于N。
本申请的第二方面提供了一种液压系统的流量分配控制设备，所述液压系统包括N个回路L1～LN，所述控制设备包括：比较模块，用于比较液压系统每个回路中执行元件入口处的压力P1～PN；确定模块，用于根据比较结果确定需要进行流量补偿的回路Lp1；流量补偿模块根据回路Lp1的理论流量和回路Lp1中流入执行元件实际流量，对回路Lp1进行流量补偿，其中，所述回路Lp1中的回路的数量小于或等于N。
本申请的第三方面提供了一种液压系统的流量分配控制装置，所述液压系统包括N个回路L1～LN，所 述装置包括一个或多个处理器以及存储有程序指令的非暂时性计算机可读存储介质，当所述一个或多个处理器执行所述程序指令时，所述一个或多个处理器用于实现本申请的流量控制方法。
本申请的第四方面提供了一种非暂时性计算机可读存储介质，其上存储有程序指令，当所述程序指令被一个或多个处理器执行时，所述一个或多个处理器用于实现本申请的流量控制方法。
本申请的第五方面提供了一种液压系统，包括：用于为所述系统提供流量的泵；N个回路L1～LN，每个回路包括执行元件和与执行元件连接的流量调节元件，所述流量调节元件用于为执行元件提供流量；所述液压系统还包括控制器，所述控制器与所述泵和流量调节元件相连接，所述控制器被配置为：比较液压系统每个回路中执行元件入口处的压力P1～PN；根据比较结果确定需要进行流量补偿的回路Lp1；根据回路Lp1的理论流量和回路Lp1中流入执行元件实际流量，对回路Lp1进行流量补偿,其中所述回路Lp1中的回路的数量小于或等于N。
本申请相对于现有技术具有的有益效果为：
(1)本申请的方案与负载敏感流量分配系统相比，本申请的流量分配系统不带压力补偿阀，流量分配特性不受压力补偿阀的影响，流量分配特性好。此外，本申请通过电控泵、流量补充阀(或副阀)及其控制方法能够实现流量补偿，可突破传统负载敏感系统所要求的阀前阀后压力补偿恒定的局限性；
(2)在本申请的方案中，节流阀和流量补充阀为并联式的结构，采用两个比例节流阀并联，其通用性比较高且结构紧凑，当主节流阀出现问题，流量补充阀也可以做备用阀；
(3)本申请方案的电控压力泵可方便的通过程序设置使泵出口压力始终高于负载一个固定值，相对传统负载敏感泵更节能，响应速度也更快，易于实现电气化控制；
(4)本申请的方案通过对电磁比例节流阀测试的数据进行数学运算，利用电控系统改善系统流量的分配特性，其流量分配特性与自动化程度均高于传统负载敏感系统。
(5)本申请方案中的主阀和副阀并联式的结构，两个电液比例阀并联，通用性比较高且结构紧凑，当主阀出现问题，副阀也可以做备用阀。
附图说明
为了更清楚地说明本申请的技术方案，下面将对实施例描述中所需要使用的附图进行简单介绍，显而易见地，下面描述中的附图仅仅是本申请的一些实施例，对于本领域普通技术人员而言，在不付出创造性劳动的前提下，还可以根据这些附图获得其他的附图。
图1是根据本申请的现有技术阀前补偿系统原理图。
图2是根据本申请的现有技术阀后补偿系统原理图。
图3是根据本申请的一个示例性的实施例流量分配控制系统的框图。
图4根据本申请的一个示例性的实施例流量分配控制系统的实现框图。
图5是根据本申请的一个示例性的实施例的液压系统流量控制流程图。
图6是根据本申请的一个示例性的实施例的液压系统流量控制方法具体的实施流程图。
图7是根据本申请的一个示例性的实施例的液压系统中控制器连线图。
图8是根据本申请的一个示例性的实施包括四联负载的流量分配控制系统的框图。
图9是根据本申请的一个示例性的实施例的另一流量分配控制系统的框图。
图10根据本申请的一个示例性的实施例的另一流量分配控制系统的实现框图。
图11根据本申请的一个示例性的实施例的另一流量分配控制系统的简化框图。
图12是根据本申请的一个示例性的实施例的另一液压系统流量控制方法具体的实施流程图。
图13是根据本申请的一个示例性的实施例的另一液压系统中控制器连线图。
图14是根据本申请的一个示例性的实施例的替代的流量分配控制系统的实现框图。
图15是根据本申请的一个示例性的实施例的替代的流量分配控制系统实现框图。
图16是根据本申请的一个示例性的实施例的替代的流量分配控制系统实现框图。
图17是根据本申请的一个示例性的实施例的液压系统的流量控制设备的框图。
图18是是根据本申请的一个示例性实施例的液压系统的框图。
具体实施方式
如在本文中所使用的，词语“第一”、“第二”等可以用于描述本申请的示例性实施例中的元件。这些词语只用于区分一个元件与另一元件，并且对应元件的固有特征或顺序等不受该词语的限制。除非另有定义，本文中使用的所有术语(包括技术或科学术语)具有与本申请所属技术领域的普通技术人员通常理解的含意相同的含意。如在常用词典中定义的那些术语被解释为具有与相关技术领域中的上下文含意相同的含意，而不被解释为具有理想或过于正式的含意，除非在本申请中被明确定义为具有这样的含意。
本领域的技术人员将理解的是，本文中描述的且在附图中说明的本申请的装置和方法是非限制性的示例性实施例，并且本申请的范围仅由权利要求书限定。结合一个示例性实施例所说明或描述的特征可与其他实施例的特征组合。这种修改和变化包括在本申请的范围内。
下文中，将参考附图详细描述本申请的示例性实施例。在附图中，省略相关已知功能或配置的详细描述，以避免不必要地遮蔽本申请的技术要点。另外，通篇描述中，相同的附图标记始终指代相同的电路、模块或单元，并且为了简洁，省略对相同电路、模块或单元的重复描述。
此外，应当理解一个或多个以下方法或其方面可以通过至少一个控制系统、控制单元或控制器执行。术语“控制单元”，“控制器”,“控制模块”或者“主控模块”可以指代包括存储器和处理器的硬件设备，术语“液压系统”可以指代类似于包含液压控制功能、液压设备的装置、设备或系统。存储器或者计算机可读存储介质配置成存储程序指令，而处理器具体配置成执行程序指令以执行将在以下进一步描述的一个或更多进程。而且，应当理解，正如本领域普通技术人员将意识到的，以下方法可以通过包括处理器并结合一个或多个其他部件来执行。
在本申请的描述中，需要说明的是，除非另有明确的规定和限定，术语“安装”、“设置”、“连接”应做广义理解，例如，可以是固定连接，也可以是可拆卸连接，或者是一体连接；可以是直接连接，也可以是通过中间媒介间接连接，可以是两个元件内部的连通或两个元件的相互作用关系。对于本领域的普通技术人员而言，可以根据具体情况理解上述术语在本申请中的具体含义。
首先需要说明，本申请涉及的方案属于液压领域，对于该领域的技术人员而言，其实质性技术构思在于液压连接关系，本领域技术人员在知悉本申请的技术构思之后，也可以将油路或阀门等进行简单的置换，从而实现本申请的功能，这同样属于本申请的保护范围。相关液压元件，例如换向阀、节流阀、传感器、变量泵、梭阀、比例阀等均属于本领域技术人员熟知的，同时也是现有液压系统中的常用部件，因此下文对这些液压元件仅简略描述，而将描述重点集中于本申请方案的独创性地连接关系。
本申请的流量分配控制系统及控制方法，可以应用于工程机械领域(如挖掘机平地工况、装车工况)，或者起重机的变幅和起升复合动作工况。但不限于这些工况，只要涉及两联或多联负载之间的复合动作工况，本申请均适用。在发明中的多联负载，可以是挖掘机的动臂、斗杆、铲斗等机构，可以理解为一种机械结构；执行元件或执行机构在液压系统中可以为液压油液或液压马达，执行元件将液压能转换为机械能；在流量分配控制系统中的每一个回路指的是实现1个执行元件(或执行器)工作(换向、调速等功能)的液压回路，1个液压回路控制1个负载。
图1是根据本申请的现有技术阀前补偿系统原理图。
如图1所示，图1中各元件的标号和含义为：1变量泵，2泵变排量机构，3、5压力补偿阀，4、6可调节流阀，7梭阀，8、9单活塞液压缸，10油箱。
根据本申请的一个或多个实施例，图1中各元件的功能为：变量泵为系统提供流量；泵变排量机构：负载反馈口(即7梭阀)的压力反馈至泵变排量机构，泵变排量机构控制泵斜盘摆角，从而控制泵排量的变化；压力补偿阀：压力补偿阀为定差减压阀，以保证可调节流阀阀前后压降为恒定值；可调节流阀：通过调节可调节流阀的过流面积，控制单活塞液压缸；梭阀：将系统最高压力(8、9单活塞液压缸中负载压力最高者)反馈给泵变排量机构；单活塞液压缸的流量变化(即速度变化)，因可调节流阀前后压降为恒定值，控制单活塞液压缸的流量只与可调节流阀过流面积相关；10油箱：放置液压油。
图2是根据本申请的现有技术阀后补偿系统原理图。
如图2所示，图2中各元件的标号和含义为：1变量泵，2泵变排量机构，3、5可调节流阀，4、6压力补偿阀，7梭阀，8、9单活塞液压缸，10油箱。
根据本申请的一个或多个实施例，图2中各元件的功能为：变量泵：为系统提供流量；泵变排量机构：负载反馈口(即7梭阀)的压力反馈至泵变排量机构，泵变排量机构控制泵斜盘摆角，从而控制泵排量的变化；可调节流阀：通过调节可调节流阀的过流面积，控制单活塞液压缸压力补偿阀：压力补偿阀都使用同一个压力(即梭阀7输出口的压力，P1或P2压力高者)作为控制压力，用来控制流量感应口出口的压力(即3、5可调节流口出口的压力)，泵出口压力相同(即可调节流阀3、5入口的压力相同)，则可调节流口可调节流阀3、5进出口两侧压降始终相同，单活塞液压缸回路流量只与可调节流阀过流面积相关；梭阀：将系统最高压力(8、9单活塞液压缸中负载压力最高者)反馈给泵变排量机构；单活塞液压缸的流量变化(即速度变化)，因可调节流阀前后压降为恒定值，控制单活塞液压缸的流量只与可调节流阀过流面积相关；油箱：放置液压油。
阀前补偿与阀后补偿为液压系统中常用的流量分配方法。阀前补偿是指压力补偿阀布置在油泵与节流阀之间(如图1所示)，阀后补偿是指压力补偿阀布置在节流阀与执行机构之间(如图2所示)。这两种方式实质是通过压力补偿阀使各节流阀进出油口两端负载压差保持一个定值，阀前补偿不具备抗负载流量饱和功能，当泵供油不足时，阀前补偿系统的流量分配受负载差异的影响，不能按照节流阀过流面积的比例分配流量。阀后补偿具有抗流量饱和功能，理论上各通道的流量既不受本通道负载压力变化的影响，也不受其他通道流量的影响，实际上油液流过管道以及阀的腔体均会产生压力损失，使各通道的流量分配比并不完全等效于节流阀的过流面积比，且压力补偿阀阀芯通流面积的设计形式对流量分配特性的影响较大。
因此采用现有技术传统负载敏感控制系统进行流量分配时，具有如下缺点：
(1)采用压力补偿阀实现主阀芯过流面积两端压力差Δp恒定，压力补偿阀本身需要消耗较大的能量；
(2)现有技术的阀前补偿负载敏感系统，不具备抗负载流量饱和功能；阀后补偿负载敏感系统虽有抗流量饱和功能，但因负载差异较大时压力补偿器需要消耗较大的能量，不适用于负载差异较大的场合；
(3)现有技术的阀前、阀后两种负载敏感控制系统，压力补偿阀阀芯通流面积设计是否合理，对流量分配特性的影响较大；
(4)现有技术的阀前、阀后两种负载敏感控制系统，其实质为两个个阻尼孔的串联结构，通用性差，能耗大，结构不紧凑。如图1和图2所示，图1中2个阻尼孔，1个是压力补偿阀3(或压力补偿阀5)，另1个是可调节流阀4(或可调节流阀6)。图2中2个阻尼孔，1个是压力补偿阀4(或压力补偿阀6)，另1个是可调节流阀3(或可调节流阀5)。
为此，本申请采用不含定压差阀的简单液阻控制回路，其核心思想是对多个负载联中压力高的系统进行主动流量补偿，以避免负载压力高的回路速度下降，减少多个执行元件(或执行器)之间的互相干扰，从而达到多执行元件系统复合动作时的协调性。
根据本申请的一个或多个实施例，根据节流出口公式(1)可知，通过节流阀的流量与阀前后的压降(压降单位用MPa(或Bar))、阀口节流面积有关。传统流量分配方式是令各节流阀的压降保持恒定，则通过各节流阀的流量Q仅与其阀口节流面积有关，流量分配比理论上应与各节流阀的节流面积比一致。
Figure PCTCN2022082482-appb-000001
其中在公式(1)式中：Cd—小孔节流常数；
A—阀芯某一开口下的节流面积(单位为mm2)；
ΔP—阀前后压降(压降单位用MPa(或Bar))；
ρ—油液密度，为常数(单位为kg/m3)。
图3是根据本申请的一个示例性的实施例流量分配控制系统的框图。如图3所示,流量分配控制系统主要由泵(可为电控压力泵)、负载方向控制阀、执行元件、流量补偿式换向阀(包括主节流阀和流量补充阀)及控制器等组成。
根据本申请的一个或多个实施例，流量补偿式换向阀为流量调节元件，其包括主节流阀和流量补充阀。其中泵可以为多个泵的泵系统，泵系统中的多个泵为电控压力泵、变量泵或定量泵，或者根据实际控制需要来将各种液压泵进行组合。
根据本申请的一个或多个实施例，图3所示的流量分配控制系统包括：用于为所述系统提供流量的泵、主节流阀和流量补充阀；其中所述主节流阀和流量补充阀与泵和执行元件相连接，为执行器提供流量；所述系统还包括与泵、主节流阀、流量补充阀连接的控制器，所述控制器根据控制算法来调整流过主节流阀和流量补充阀的流量。
图4根据本申请的一个示例性的实施例流量分配控制系统的实现框图。
如图4所示，图4中的元件和标号为：1a、1b：电控压力泵；2a、2b、2c：主节流阀；3a、3b、3c：负载方向控制阀；4a、4b、4c：执行器；5a、5b、5c：流量补充阀；6a、6b：泵出口压力传感器；7a、7b、7c：负载压力传感器；8a、8b、8c：单向阀；9a、9b、9c：单向阀；10：油箱；Yp1、Yp2：调节器。
根据本申请的一个或多个实施例，图4中主要元件的功能为：
电控压力泵
1a、1b为电控压力泵，通过给定电控压力泵1a输入指令，电控压力泵1a输出比负载联最高压力PFmax高一固定值ΔP1的压力油PP1，即公式(2)：
P P1-P Fmax＝ΔP 1   (2)
电控压力泵1b输出比负载联最高压力PFmax高一固定值ΔP2的压力油PP2，即公式(3)：
P P2-P Fmax＝ΔP 2   (3)
根据液压系统使用工况需要，ΔP1与ΔP2可以相等，也可以不相等。不同负载联之间的流量分配关系与主泵出口压力PP1、PP2，主节流阀2a、2b、2c以及流量补充阀5a、5b、5c这三个因素之间相关，适用场合及适用范围较常规节流回路可大大拓宽。
负载方向控制阀
负载方向控制阀3a、3b、3c只控制负载的运动方向，不参与不同联之间的流量分配过程。理论而言，负载方向控制阀的过流面积越大越好，考虑实际安装空间及成本，负载方向控制阀的最大压降不超过30bar。
主节流阀+流量补充阀
2a、2b、2c主节流阀为电液比例式，流量无极调节；5a、5b、5c流量补充阀也为电比例式，流量无极调节。其中，电液比例式为：按输入的电气信号连续地、按比例地对油液的流量或方向进行控制；流量无极调节为：流量可以在最小值到最大值之间连续调节，且流量值比较平滑没有台阶(因流量变化影响的是执行机构的速度，其结果是速度的无极调节)。
当流量补充阀5a、5b、5c不工作(即阀口全关，流量补充阀过流面积为零)，若负载1压力PF1高于负载2压力PF2，负载2压力PF2高于负载3压力PF3(即PF1＞PF2＞PF3)，假设主节流阀2a、2b、2c完全一致(即过流面积完全相等)，则流入负载F3回路的流量最大，流入负载F2回路的流量次之，流入负载F1回路的流量最少，这是因为普通节流回路，负载高的回路节流口两端压差小，故通过的流量小。此时，若控制流量补充阀5a、5b工作(即流量补充阀口打开)，通过控制5a、5b的电流调整阀口开度，则可以分别补充负载1回路、负载2回路因负载压力高所减少的下降流量，使各回路流量相等。
控制器
流量分配控制算法及控制策略在控制器中实现，可在控制器中设置电控压力泵1a、1b压力，设置理论流量1、理论流量2，第一联回路理论(或假想)过流面积Aa、第二联回路理论(或假想)过流面积Ab等。理论流量由液压工程师设计系统时给出，根据主机(如起重机、挖掘机等)复合动作特性要求来给出。
根据本申请的一个或多个实施例，2a、2b、2c：主节流阀；为电液比例式，流量无极调节，其与流量补充阀5a、5b、5c共同为执行器4a、4b、4c提供流量，2a、2b、2c与5a、5b、5c通断状态如上述节流阀+流量补充阀的功能描述；4a、4b、4c为执行器：执行器一般是液压马达或液压油缸，如挖掘机的动臂油缸、回转马达等，是将液压能转变为机械能的装置；5a、5b、5c：流量补充阀：为电液比例式，流量无极调节，其与主节流阀2a、2b、2c共同为执 行器4a、4b、4c提供流量，2a、2b、2c与5a、5b、5c通断状态如上述节流阀+流量补充阀的功能描述；6a、6b：泵出口压力传感器：检测泵出口的压力，7a、7b、7c：负载压力传感器；检测负载口的压力；8a、8b、8c、9a、9b、9c单向阀：单向导通的阀；10油箱：放置液压油；Yp1、Yp2是电控压力泵1a、1b的调节器，根据调节器的输入电信号指令，实现泵压力和流量的调节。
图5是根据本申请的一个示例性的实施例的液压系统流量控制方法流程图。液压系统包括多个回路(例如，如图3所示，液压系统包括3个回路)。
如图5所示，在步骤S1处，比较液压系统每个回路中执行元件入口处的压力P1～PN；
在步骤S2处，根据比较结果确定需要进行流量补偿的回路Lp1，根据本申请的一个或多个实施例，确定所述执行元件入口处的压力P1～PN的最小值Pmin，所述Pmin对应的回路为Lp2，所述需要进行流量补偿的回路Lp1为：所述回路L1～LN中不包含回路Lp2的其他回路，并关闭回路Lp2的执行元件所连接的流量补充阀，其中Lp1和Lp2的和为回路总数量N，N大于或等于2；如图4所示的流量分配系统，其中，根据比较执行元件入口处的压力值，Lp1为负载1和负载2所在的回路，Lp2为负载3所在的回路；即流量补充阀5a、5b均需打开，流量补充阀5c关闭；
在步骤S3处，根据所述回路Lp1的理论流量和所述回路Lp1中流入执行元件实际流量，对回路Lp1进行流量补偿，其中，所述回路Lp1中的回路的数量小于或等于N，根据回路Lp1的理论流量和回路Lp1中流入执行元件的实际流量的差值，通过调节回路Lp1中流量补充阀的流量对回路Lp1进行流量补偿控制；当回路Lp1的理论流量和回路Lp1中流入执行元件的实际流量的差值小于等于零时，结束回路Lp1的流量补偿。
图6是根据本申请的一个示例性的实施例的液压系统流量控制方法具体的实施流程图。
如图6所示，根据本申请的一个或多个实施例，液压系统包括3个回路(也即3个回路中包括了3个执行元件获执行器，也即液压系统包括3联负载)，其中，
第1联流入负载PF1的实际总流量：Q A′＝Q1+Q1S；
第2联流入负载PF2的实际总流量：Q B′＝Q2+Q2S；
第3联流入负载PF3的实际总流量：Q C′＝Q3+Q3S；
假设PF1＞PF2＞PF3，图6所示液压系统流量控制方法具体的实施流程具体工作流程如下：
1、通过压力传感器采集压力信号，比较执行元件入口压力PF1、PF2与PF3之间的大小；
2、最小联负载对应的流量补充阀不开，其他联对应的流量补充阀均需打开。如PF1＞PF2＞PF3，则流量补充阀5a、5b均需打开，流量补充阀5c不需打开；
3、设置理论流量1(即第1联回路的理论流量)、理论流量2(即第2联回路的理论流量)的值。理论流量1与第一联回路理论(或假想)过流面积Aa、泵1a出口处的压力与负载联最高压力PFmax之间的差值ΔP1、油液密度ρ、过流系数Cd等相关，理论过流面积Aa需根据工况要求给定，为了分析方便，其他几个参量一旦调定好后(ΔP1、ρ、Cd)即可默认为恒定值。理论流量2与第二联回路理论(或假想)过流面积Ab、泵1b与负载联最高压力PFmax之间的差值ΔP1、油液密度ρ、过流系数Cd等相关，理论过流面积Ab需根据工况要求给定，为了分析方便，其他几个参量可默认为恒定值；
4、计算流入负载F1的流量(实际流量1)，理论流量1与实际流量1的差值即补偿流量1，可通过调节流量补偿阀5a的电流大小(即控制流量补偿阀5a的过流面积)，使流量补偿阀5a的流量来补偿回路1因负载压力高而减少的流量。同理，计算流入负载F2的流量(实际流量2)，调节流量补偿阀5b的电流大小，使流量补偿阀5b的流量来补偿回路2因负载压力高而减少的流量；
5、判断补偿流量是否为零(即理论流量减去实际流量是否为零)，大于零则重新开始进入步骤1(负载压力比较环节)，小于等于零则对应的流量补充阀关闭，流量补偿过程结束，即流量补偿控制或流量调整执行终止的条件为判断理论流量减去实际流量是否小于或等于0；
6、最终实现回路1、回路2与回路3流量分配满足实际工况流量分配需求。
假设PF1、PF2与PF3不满足PF1＞PF2＞PF3，也可参考上述控制方法。
根据本申请的一个或多个实施例，判断PF1、PF2与PF3的大小是决定开启哪个流量补充阀的条件；如果PF1、 PF2、PF3三者的值相同，则三个流量补偿阀均关闭；如果两个一样，假设PF1＝PF2，且PF1＞PF3，则需打开流量补充阀5a、5b；如果两个一样，假设PF1＝PF2，且PF1＜PF3，则只需打开流量补充阀5c。
图7是根据本申请的一个示例性的实施例的液压系统中控制器连线图。
如图7所示，控制器中可存储设定值，该设定值包括电控压力泵1a和1b的压力，以及液压系统各个回路的理论流量(理论流量1和2)。控制器还能够接收泵口压力传感器(6a和6b)和负载压力传感器(7a，7b,7c)传送的压力反馈信号。此外，控制器可以对泵出口的压力，主芯阀流过的面积、负载方向和流量补充阀流过面积进行控制，具体的参数如图7所示，在图7中，控制器的连线关系仅仅为图3-5中具体的实例。当流量系统的回路包括多个时，控制器的连线关系可以此类推，在这里不一一赘述。
根据本申请的一个或多个实施例，本申请的流量分配控制系统及控制方法，除适用于2联负载、3联负载外，同样也适用于4联负载(理论上，可对负载进行无限扩展)，为了分析方便，做以下简要说明：假设扩展到4联负载，液压系统相关的部件可参照图8，图8中流量控制方法与三联负载类似。
根据本申请的一个或多个实施例，根据本申请图4的控制方法，对流量的调整范围为：
(1)对于3联负载，因负载压力导致流量分配不均，只需要调节最多2联负载的流量(负载最小联流量理论而言最大，不需要补充流量)即3联负载系统需调节的自由度为2；在本申请此处中需要调节的自由度可以理解为需要调节2联负载的流量。自由度类似于机械结构中，平面运动一个点运动到任何地方需要X、Y两个坐标(即2个自由度)，空间运动中一个点运动到任何地方需要X、Y、Z三个坐标(即3个自由度)。
(2)本申请图3中有2个电控压力泵，压差方面有ΔP 1、ΔP 2两个自由度可以调节，可根据实际使用工况及能耗要求调节ΔP 1与ΔP 2的值；
(3)本申请图3中有5a、5b、5c共3个流量补充阀，考虑最多2路需要补偿，过流面积方面至少有2个自由度可以调节；如果有4个补充阀，需要开启的补充阀最多为3，即所需调节的自由度为3，则可调节的自由度为3+2＝5；如果液压系统有N个补充阀，所需调节的自由度为N-1，则压差与过流面积可调节的自由度为(N-1)+2＝N+1。
(4)在本申请的上述实施例中，对于3联负载，需调节的自由度为2，压差与过流面积可调节的自由度为4，远远满足液压系统使用要求。
(5)同理，对于4联负载，需调节的自由度为3，实际压差与过流面积可调节的自由度为5，也满足使用要求；对于5联负载，需调节的自由度为4，实际压差与过流面积可调节的自由度为6，满足使用要求。其中，负载最低联不需要开启补充阀，即需要调节的自由度N-1是除了负载最低联之外的其他联；其中，过流面积可调节的实际压差与过流面积可调节的自由度为(N+1)。
图3-7中，本申请实施例用到的符号如以下表1所示：
表1
序号 符号 含义 单位
1 Pp1 电控压力泵1a出口压力 MPa
2 Pp2 电控压力泵1b出口压力 MPa
3 PF 负载压力 MPa
4 PF1 第1联负载压力 MPa
5 PF2 第2联负载压力 MPa
6 PF3 第3联负载压力 MPa
7 PFmax 负载最高联压力 MPa
8 QA 第一联理论总流量 L/min
9 Q A′ 第一联实际总流量 L/min
10 Q1 第一联主节流阀2a过流量 L/min
11 Q1S 第一联流量补充阀5a过流量 L/min
12 QB 第二联理论总流量 L/min
13 Q B′ 第二联实际总流量 L/min
14 Q2 第二联主节流阀2b过流量 L/min
15 Q2S 第二联流量补充阀5b过流量 L/min
16 QC 第三联理论总流量 L/min
17 Q C′ 第三联实际总流量 L/min
18 Q3 第三联主节流阀2b过流量 L/min
19 Q3S 第三联流量补充阀5b过流量 L/min
20 A1 第一联主节流阀阀芯过流面积 mm2
21 A1S 第一联流量补充阀阀芯过流面积 mm2
22 Aa 第一联回路理论(或假想)过流面积 mm2
23 A2 第二联主节流阀阀芯过流面积 mm2
24 A2S 第二联流量补充阀阀芯过流面积 mm2
25 Ab 第二联回路理论(或假想)过流面积 mm2
26 A3 第三联主节流阀阀芯的过流面积 mm2
27 A3S 第三联流量补充阀阀芯的过流面积 mm2
28 Ac 第三联回路理论(或假想)的过流面积 mm2
29 ΔP 1 (PP1-PFmax)的值 MPa
30 ΔP 2 (PP2-PFmax)的值 MPa
31 Cd 节流孔过流系数 Null
根据本申请的一个或多个实施例，本申请还可采用电磁比例阀做为主阀和副阀，主阀阀口过流面积可无极变化，主阀通过手柄位移控制阀芯过流面积即初始状态主阀满足负载流量需求，当负载发生变化时，副阀开始发挥作用，通过电控单元控制副阀阀芯的节流面积，这时主阀和副阀共同完成流量供给。本申请的该实施例实质依据负载变化来控制副阀流量，满足负载需求，与现有阀前或阀后负载敏感系统不同在于，其不需保持主阀芯前后压差恒定。通过副阀及其控制方法，实现流量补偿，进而打破传统负载敏感系统所要求的阀前阀后压力补偿恒定的局限性。
图9是根据本申请的一个示例性的实施例的另一流量分配控制系统的框图。如图9所示，该流量分配控制系统包括：用于为所述系统提供流量的泵；主阀和副阀，其中，所述主阀和副阀与泵和执行器相连接，为执行器提供流量；所述系统还包括与泵、主阀、和副阀连接的控制器，所述控制器根据控制算法控制主阀和副阀阀芯的开度来调节执行器的输出流量。所述主阀通过输入的电信号控制阀芯移动来调整流量，所述副阀由所述控制器控制来弥补所述执行器的流量不足。
图10根据本申请的一个示例性的实施例的另一流量分配控制系统的实现框图。
如图10所示，流量分配控制系统主要由主阀、副阀、梭阀、压力传感器、安全阀及控制器等组成。
如图10所示，图10中的标记为：1油箱，2变量泵，3、9、11压力传感器，4主阀1，5副阀1，6主阀2，7副阀2，8、10梭阀，12、13油缸，14安全阀，A-第一联，B-第二联。
如图10所示，图10中各元件的功能为：1油箱：放置液压油；2变量泵：变量泵输出比负载联最高压力PFmax高一固定值的压力油PP；3、9、11压力传感器：3检测泵出口压力，9、11压力传感器检测负载联压力，压力传感器测得的压力信号可通过控制单元处理，将处理后的信号经放大器放大后输送到a1、a2、a3、a4，进而控制主、副阀阀芯的开度，调节各执行器的输入流量；4、6主阀：主阀在系统中通过输入的电信号控制阀芯移动；5、7副阀：作为主阀的辅助阀可以弥补执行机构流量的不足；8、10梭阀：获取最高负载压力，并将该压力反馈给2变量泵；12、13油缸：执行器，将液压能转变为机械能的装置，如挖掘机的动臂油缸、回转马达等；14安全阀：其实质是溢流阀，系统最大压力达到安全阀设置压力时开启，作为安全用。
根据本申请的一个或多个实施例，如图10所示，主阀1与主阀2为电比例式，流量无极调节；副阀1与副阀2 流量补充阀也为电比例式，流量无极调节。主阀在系统中通过输入的电信号控制阀芯移动；副阀作为主阀的辅助阀可以弥补执行机构流量的不足；梭阀可以获取最高负载压力；压力传感器可以实时检测油路压力，如图6所示压力传感器9、11用来监测高压负载压力，压力传感器3用于监测泵出口压力，压力传感器测得的压力信号反馈至控制器中，流量分配控制算法及控制策略在控制器中实现，可在控制器中设置变量泵2的压力，设置理论流量1、理论流量2，并将处理后的信号经放大器放大后输送到a1、a2、a3、a4，进而控制主、副阀阀芯的开度，调节各执行器的输出流量。
图11根据本申请的一个示例性的实施例的另一流量分配控制系统的简化框图。
如图11所示，图11中的标记为：R1：主阀1；R2：主阀2；S1：副阀1；S2：副阀2；PF1：第一执行机构(执行元件或执行器)入口压力；PF2：第二执行机构(执行元件或执行器)入口压力；Q1：第一联主阀流量；Q2：第二联主阀流量；QS1：第一联副阀流量；QS2：第二联副阀流量；
如图11所示，R1、R2主阀，S1、S2副阀，主阀与副阀采用并联形式，共同为某一负载供油，因此，本申请上述的实施例相当于增大了负载回路的过流面积，特别适用于速度控制要求高的场合。
图12是根据本申请的一个示例性的实施例的另一液压系统流量控制方法具体的实施流程图。
如图12所示：液压系统包括2个回路(也即2个回路中包括了2个执行元件获执行器，也即液压系统包括2联负载)。
图12所示液压系统流量控制方法具体的实施流程具体工作流程如下：
1、比较执行元件入口压力PF1与PF2的大小，由压力传感器选择高压回路，进而对流量进行补偿。
2、由于每个比例阀在完成设计时都有对应的面积-位移关系，通过数学运算即可得出高压回路主阀理论流量。
3、根据PF1(或PF2)与泵出油口压力Pp的差值，利用出口流量公式计算实际流量，出口流量的计算公式为上述公式(1)。
4、理论流量与实际流量差值即补偿流量，可通过调节副电磁比例换向阀的通流面积满足流量补偿。
5、最终使实际流量约等于理论流量，满足流量分配需求，也即当理论流量和实际流量的差值小于等于零时，结束流量的分配控制。
在图12的流程中，需要计算的参数值为：ΔP 1—第一联阀芯理论压降，单位为bar；ΔP 2—第二联阀芯理论压降，单位为bar；Q A—第一联总流量，等于Q 1+Q S1，单位为L/min；Q B—第二联总流量，等于Q 2+Q S2，单位为L/min；Cd1—主阀芯1小孔节流常数；Cd2—主阀芯2小孔节流常数；其中ΔP 1′＝P P-P F1；ΔP 2′＝P P-P F2。
其中，根据图12所示的流程，ΔP 1(或ΔP 1′)为第1联负载的实际压降，是通过检测泵出口压力P P(或P P1)和第一执行机构入口压力P F1做差,通过ΔP 1(或ΔP 1′)、公式(1)，可以计算第一联实际流量1；ΔP 2(或ΔP 2′)为第2联负载的实际压降，是通过检测泵出口压力P P(或P P2)和第二执行机构入口压力P F2做差，通过ΔP 2(或ΔP 2)、公式(1)，可以计算第二联实际流量2。
图13是根据本申请的一个示例性的实施例的另一液压系统中控制器连线图。如图13所示，控制器中可存储设定值，该设定值包括泵的压力值，以及液压系统各个回路的理论流量(理论流量1和2)。控制器还能够接收负载压力传感器(3,9,11)传送的压力反馈信号。此外，控制器可以对泵出口的压力，主阀流过的面积、和副阀流过面积进行控制，具体的参数如图13所示，在图13中，控制器的连线关系仅仅为图9-12中具体的实例。当流量系统的回路包括多个时，控制器的连线关系可以此类推，在这里不一一赘述。
在图9-12中所描述的实施例中，本申请实施例用到的符号如以下表2所示：
表2
序号 符号 含义 单位
1 Pp 泵出口压力 MPa
2 Q 泵出口流量 L/min
3 R1 第一联主阀 /
4 S1 第一联副阀(辅助主阀R1工作) /
5 A1 主阀芯1过流面积 mm2
6 AS1 副阀芯1过流面积 mm2
7 Q1 第一联主阀流量 L/min
8 QS1 第一联副阀流量 L/min
9 QA 第一联理论总流量 L/min
10 Q A′ 第一联实际总流量 L/min
11 R2 第二联主阀 /
12 S2 第二联副阀(辅助主阀R2工作) /
13 A1 主阀芯2过流面积 mm2
14 AS1 副阀芯2过流面积 mm2
15 Q2 第二联主阀流量 L/min
16 QS2 第二联副阀流量 L/min
17 QB 第二联理论总流量 L/min
18 Q B′ 第二联实际总流量 L/min
19 PF1 第一执行机构入口压力 MPa
20 PF2 第二执行机构入口压力 MPa
图14是根据本申请的一个示例性的实施例的替代的流量分配控制系统的实现框图。
图14中各元件的标记为：1a、1b：电控压力泵；2a、2b、2c：主节流阀；3a、3b、3c：负载方向控制阀；4a、4b、4c：执行器；5a、5b、5c：流量补充阀；6a、6b：泵出口压力传感器；7a、7b、7c：梭阀；8a、8b、8c、8d、8e、8f：单向阀；9a、9b、9c：压力传感器；10：油箱。
如图14所述，替代的流量分配控制系统方案可以用于梭阀代替压力传感器，如图14所示。用梭阀连接到执行器两端，同样可以获取各联的压力，通过控制单元可获取压力高的支路，进而控制流量补充阀开度进行补油。
根据本申请的一个或多个实施例，其中梭阀能够识别每个负载工作油口的压力，压力传感器能够获取两联及以上梭阀的值，从而本申请的控制器或流量分配方案能够选取压力较大的回路进行流量补偿。
根据本申请的一个或多个实施例，流量分配控制系统不限于使用变量泵，可以将其替换为定量泵，同样满足原有系统特性。也可以将2个泵减少为1个，给整个系统供油。
根据本申请的一个或多个实施例，本申请的流量分配控制系统或液压系统可将方向阀与比例节流阀集合成比例方向阀，通过控制主比例方向阀以及副比例方向阀，同样可以实现流量分配。
本控制方案不限于梭阀的应用，除可用梭阀以外，也可以用于压力传感器代替。如图15所示的根据本申请的一个示例性的实施例的替代的流量分配控制系统，其用多个压力传感器代替梭阀，即在每个支路串联压力传感器，同样可以实现发明所述功能，通过控制单元选取压力高的支路，并给定对应副阀的指令信号。
图15中各元件的标记为：1油箱，2定量泵，3、8、9、11压力传感器，4、6主电磁比例阀，5、7副电磁比例阀，8、10梭阀，12、13油缸。
根据本申请的一个或多个实施例，本申请的流量分配控制系统不限于图10所示的结构，图10中由两个电磁比例阀组成，可将替代为两个电磁比例阀和梭阀组成的阀块如图16所示，其中图10和图16的区别在于阀块是否包含梭阀，见图中序号8、9。
图16中各元件的标记为：1油箱，2变量泵，3、8、9、11压力传感器，4、6主电磁比例阀，5、7副电磁比例阀，8、10梭阀，12、13油缸。
图17是根据本申请的一个示例性的实施例的液压系统的流量控制设备的框图。
如图17所示，液压系统的流量分配控制设备包括：比较模块，用于比较液压系统每个回路中执行元件入口处的 压力P1～PN；确定模块，用于根据比较结果确定需要进行流量补偿的回路Lp1；流量补偿模块，用于根据所述回路Lp1的理论流量和所述回路Lp1中流入执行元件实际流量对回路Lp1进行流量补偿，其中，液压系统包括N个并联回路L1～LN，所述回路Lp1中的回路的数量小于或等于N。(例如本申请上述的图中具有多联负载的回路，或者具有多个执行元件的回路)。
图18是根据本申请的一个示例性实施例的液压系统的框图。
如图18所示，该液压系统包括：用于为所述系统提供流量的泵；N个回路L1～LN，每个回路包括执行元件和与执行元件连接的流量调节元件，所述流量调节元件用于为执行元件提供流量；所述液压系统还包括控制器，所述控制器与所述泵和流量调节元件相连接，所述控制器被配置为：比较液压系统每个回路中执行元件入口处的压力P1～PN；根据比较结果确定需要进行流量补偿的回路Lp1；根据所述回路Lp1的理论流量和所述回路Lp1中流入执行元件实际流量，对回路Lp1进行流量补偿,其中所述回路Lp1中的回路的数量小于或等于N。
本申请还提供一种非暂时性计算机可读存储介质，其上存储有程序指令，当所述程序指令被一个或多个处理器执行时，所述一个或多个处理器用于实现如上所示的本申请各个实施例中的方法或流程。
根据本申请的一个或多个实施例，本申请还提供一种液压系统，包括本申请示例的流量分配控制系统，流量分配控制设备、流量分配控制装置、具有本申请上述的非暂时性计算机可读存储介质，或采用本申请的流量分配控制方法。
根据本申请的一个或多个实施例，本申请的控制器或控制装置可以使用存储在非暂时性计算机和/或机器可读介质(例如硬盘驱动器、闪存、只读存储器、光盘、数字多功能磁盘、高速缓存、随机存取存储器和/或任何其他存储设备或存储磁盘)上的编码的指令(例如，计算机和/或机器可读指令)来实现如本申请以上所述控制方法的处理，在非暂时性计算机和/或机器可读介质中存储任何时间期间(例如，延长的时间段、永久的、短暂的实例、临时缓存和/或信息高速缓存)的信息。如本文所使用的，术语“非暂时性计算机可读介质”被明确定义为包括任何类型的计算机可读存储设备和/或存储盘，并且排除传播信号并排除传输介质。
根据本申请的一个或多个实施例，本申请的控制设备、控制装置、主控系统或控制模块可以包含一个或多个处理器也可以在内部包含有非暂时性计算机可读介质。具体地，在流量分配的控制设备中(主控系统或控制模块)可以包括微控制器MCU，其布置在液压系统中，用于实现流量分配控制的各种操作和实施多种功能。控制设备中的处理器可以诸如但不限于一个或多个单核或多核处理器。(一个或多个)处理器可包括通用处理器和专用处理器(例如，图形处理器、应用处理器等)的任何组合。处理器可与其耦接和/或可包括计存储器/存储装置，并且可被配置为执行存储在存储器/存储装置中的指令，以实现在本申请中控制器上运行的各种应用和/或操作系统。
本申请提供的在液压系统中通过流量补偿实现流量分配的控制的方案具有的优点为：
(1)电控压力泵1a为主节流阀供油，电控压力泵1b为流量补充阀供油，通过闭环控制实现理论流量与实际流量的动态平衡(即补偿流量为零)，从而实现不同联之间流量分配满足要求。
(2)PF1＞PF2＞PF3工况下，流量分配控制方法、工作流程及流程图。PF1、PF2与PF3不满足PF1＞PF2＞PF3工况，也可参考前述控制方法。
(3)该流量分配系统采用电控压力泵，P P1-P Fmax＝ΔP 1，P P2-P Fmax＝ΔP 2，ΔP 1与ΔP 2可分别独立调节，可根据应用工况设置不同的值。
(4)回路理论(或假想)过流面积Aa、Ab、Ac是输入参量，根据实际使用工况要求设置(可通过速度要求给出)，为了分析方便，其他几个参量一旦调定好后(ΔP1、ρ、Cd)即可默认为恒定值。
(5)本申请的系统及控制方法，相对传统负载敏感泵更节能，响应速度也更快，易于实现电气化控制。
(6)利用主阀和副阀配合工作，主阀通过手柄位移-阀芯通流面积获得初始流量需求，副阀在负载变化时发挥作用，实现了流量补偿，即主阀和副阀同时工作满足流量需求；在电控单元中，利用高压支路与泵出口压力差进行数学运算，以电信号进行传递提高了控制速度和控制精度。
以下是本申请的示例：
第一组示例：
示例1.一种流量分配控制系统，其特征在于，包括：用于为所述系统提供流量的泵；N个回路，每个回路包括主节流阀、流量补充阀以及与所述主节流阀和流量补充阀连接的执行器，其中所述泵为每个回路提供流量；与所 述泵、所述每个回路连接的控制器，所述控制器根据控制算法来分配过每个回路的主节流阀和流量补充阀的流量；其中，所述N大于或等于2。
示例2.根据示例1所述的系统，其特征在于，每个回路中还包括用于控制负载运动方向的负载方向控制阀，所述负载方向控制阀的输入端与主节流阀和流量补充阀输出端相连接，所述负载方向控制阀的输出端与执行器相连接，其中所述控制器与所述负载方向控制阀相连接。
示例3.根据示例1所述的系统，其特征在于，其特征在于，每个回路中的主节流阀和流量补充阀并联连接。
示例4.根据示例1所述的系统，其特征在于，所述泵至少包括第一泵和第二泵，其中所述第一泵为所述主节流阀提供流量，所述第二泵为所述流量补充阀提供流量。
示例5.根据示例1所述的系统，其特征在于，还包括：压力检测元件，所述压力检测元件包括：位于所述泵出口的泵出口压力传感器和位于每个回路中的主节流阀和流量补充阀输出端的负载压力传感器，所述泵出口压力传感器和所述负载压力传感器将检测到的压力发送至所述控制器。
示例6.根据示例1所述的系统，其特征在于，所述泵为电控压力泵、变量泵或定量泵。
示例7.根据示例1所述的系统，其特征在于，其特征在于，在每个回路中，所述主节流阀的数量等于所述流量补充阀的数量。
示例8.根据示例1所述的系统，其特征在于，其中所述主节流阀和流量补充阀为电比例式流量无极调节的阀、或为比例方向阀。
示例9.根据示例1所述的系统，其特征在于，每个回路还包括：位于所述泵和所述主节流阀之间的单向阀，以及位于所述泵和所述流量补充阀之间的单向阀。
示例10.根据示例1所述的系统，其特征在于，所述控制器通过控制流量补充阀的电流来调整流量补充阀的阀口开度。
示例11.根据示例1所述的系统，其特征在于，还包括：压力检测元件，所述压力检测元件包括：位于所述泵出口的泵出口压力传感器和位于所述回路连接的负载两端的梭阀，所述泵出口压力传感器和所述梭阀将获取到的压力发送至所述控制器。
示例12.根据示例1所述的系统，其特征在于，还包括：：与泵相连接的调节器，根据来自控制器的电信号指令来对泵的压力和流量进行调节。
第二组示例：
示例1.一种流量调节控制系统，其特征在于，包括：用于为所述系统提供流量的泵；N个回路，每个回路包括：主阀、副阀以及与所述主阀和副阀连接的执行器，其中，所述泵为每个回路供流量；与泵、每个回路连接的控制器，所述控制器根据控制算法控制每个回路中主阀和副阀阀芯的开度来调节所述执行器的输出流量，其中，所述N大于或等于2。
示例2.根据示例1所述的系统，其特征在于，所述主阀通过输入的电信号控制阀芯移动来调整流量，所述副阀由所述控制器控制来弥补所述执行器的流量不足。
示例3.根据示例1所述的系统，其特征在于，，在每个回路中，所述主阀和副阀并联连接。
示例4.根据示例1所述的系统，其特征在于，所述系统还包括位于在执行器输入端的压力传感器和位于泵出口的压力传感器，所述压力传感器将检测到的压力信号传送至控制器。
示例5.根据示例1所述的系统，其特征在于，所述系统还包括位于执行器处的压力传感器，用于获取所述执行器连接负载的压力，并选择所述系统中压力高的回路。
示例6.根据示例1所述的系统，其特征在于，在每个回路中，所述主阀的数量等于所述副阀的数量。
示例7.根据示例1所述的系统，其特征在于，其中所述主阀和副阀为电比例式流量无极调节的阀、或为比例方向阀。
示例8.根据示例1所述的系统，其特征在于，还包括与所述泵连接的安全阀，所述安全阀用于对所述泵进行安全保护。
示例9.根据示例1所述的系统，其特征在于，所述控制器根据执行器连接的负载的变化来控制通过副阀的流量，以满足负载的需求。
示例10.根据示例1所述的系统，其特征在于，所述主阀和副阀为由电磁比例阀和梭阀组成的阀块。
示例11.根据示例1所述的系统，其特征在于，所述主阀通过位移阀芯通流面积来获得初始流量需求，当执行器的负载变化时，所述控制器调节通过副阀的流量来实现所述回路的流量调节控制。
第三组示例：
示例1.一种液压系统的流量分配控制方法，所述液压系统包括N个回路L1～LN，所述方法包括：S1：比较液压系统每个回路中执行元件入口处的压力P1～PN；S2：根据比较结果确定需要进行流量补偿的回路Lp1；S3：根据所述回路Lp1的理论流量和所述回路Lp1中流入执行元件实际流量，对回路Lp1进行流量补偿，其中，所述回路Lp1中的回路的数量小于或等于N。
示例2.根据示例1所述的方法，确定所述执行元件入口处的压力P1～PN的最小值Pmin，所述Pmin对应的 回路为Lp2，所述需要进行流量补偿的回路Lp1为：所述回路L1～LN中不包含回路Lp2的其他回路。
示例3.根据示例1或2所述的方法，其中所述N个回路L1～LN并联连接，每个回路包括执行元件和与执行元件相连接的主节流阀和流量补充阀，其中所述主节流阀和流量补充阀并联连接，其中所述N大于或等于2；其中所述步骤S2包括：关闭回路Lp2的执行元件所连接的流量补充阀。
示例4.根据示例1所述的方法，其中在所述步骤S3中，根据回路Lp1的理论流量和回路Lp1中流入执行元件的实际流量的差值，通过调节回路Lp1中流量补充阀的流量对回路Lp1进行流量补偿控制。
示例5.根据示例4所述的方法，所述步骤S3包括：通过调节需要进行流量补偿的回路Lp1中流量补充阀的流量来进行流量补偿控制。
示例6.根据示例1所述的方法，所述步骤S3包括：当回路Lp1的理论流量和回路Lp1中流入执行元件的实际流量的差值小于等于零时，结束回路Lp1的流量补偿。
示例7.根据示例3所述的方法，其中，回路Lp1中流入执行元件的实际流量为：回路Lp1中主节流阀流过的流量与回路Lp1中补充流量阀流过的流量的总和。
示例8.根据示例1所述的方法，回路Lp1理论流量根据不同工况设定，所述工况至少包括压差和过流面积；路Lp1的理论流量与液压系统中泵出口处压力与回路最高压力之间的差、液压油液密度、过流系数和回路Lp1的过流面积相关。
示例9.根据示例8所述的方法，其中，回路Lp1的理论流量与液压系统中泵出口处压力与回路最高压力之间的差、液压油液密度、过流系数和回路Lp1的过流面积相关。
示例10.根据示例9所述的方法，其中，该回路的过流面积和所述液压系统的工况要求相关。
示例11.根据示例1所述的方法,其中所述液压系统包括两个并联回路，每个回路包括执行元件和与执行元件连接的主阀和副阀；其中所述步骤S2包括：当两个回路中的执行元件入口处的压力相等，则关闭每个回路中的副阀；当两个回路中的执行元件入口处的压力不相等，则选择压力较大的回路作为流量补偿的回路。
示例12.根据示例11所述的方法，其中所述步骤S3包括：如果压力较大的回路的理论流量与该回路中流入执行元件的实际流量差值大于零时，则开启该压力较大回路的副阀并关闭另一回路的副阀；如果压力较大的回路的理论流量与该回路中流入执行元件的实际流量差值小于等于零时，则结束该压力较大的回路流量补偿。
示例13.根据示例11所述的方法，所述步骤S2还包括：根据液压系统中的压力传感器来选择压力较大的回路作为流量补偿的回路。
示例14.根据示例11所述的方法，其中所述回路中的主阀和副阀并联连接。
示例15.根据示例3所述的方法，所液压系统包括为液压系统提供流量的泵，所述泵至少包括第一泵和第二泵，其中所述第一泵为所述主节流阀提供流量，所述第二泵为所述流量补充阀提供流量。
示例16.根据示例15所述的方法，所述方法能够进行补偿控制的流量的自由度最多为N-1；所述方法能够进行补偿的流量或压差的自由度最多为N+1。
第四组示例：
示例1.一种液压系统的流量分配控制设备，所述液压系统包括N个回路L1～LN，所述控制设备包括：比较模块，用于比较液压系统每个回路中执行元件入口处的压力P1～PN；确定模块，用于根据比较结果确定需要进行流量补偿的回路Lp1；流量补偿模块，用于根据所述回路Lp1的理论流量和所述回路Lp1中流入执行元件实际流量对回路Lp1进行流量补偿，其中，所述回路Lp1中的回路的数量小于或等于N。
示例2.根据示例1所述的设备，所述确定模块用于确定模块用于确定所述执行元件入口处的压力P1～PN的最小值Pmin，所述Pmin对应的回路为Lp2，所述需要进行流量补偿的回路Lp1为：所述N个回路L1～LN中不包含回路Lp2的其他回路。
示例3.根据示例1或2所述的设备，其中，所述N个回路L1～LN并联连接，每个回路包括执行元件和与执行元件相连接的主节流阀和流量补充阀，其中所述主节流阀和流量补充阀并联连接；其中N大于或等于2；其中所述确定模块用于关闭回路Lp2的执行元件所连接的流量补充阀。
示例4.根据示例1所述的设备，所述流量补偿模块还用于：根据回路Lp1的理论流量和回路Lp1中流入执行元件的实际流量的差值，通过调节回路Lp1中流量补充阀的流量对回路Lp1进行流量补偿控制。
示例5.根据示例1所述的设备，所述流量补偿模块还用于：通过调节需要进行流量补偿的回路Lp1中流量补充阀的流量来进行流量补偿控制。
示例6.根据示例1所述的设备，所述流量补偿模块还用于：当回路Lp1的理论流量和回路Lp1中流入执行元件的实际流量的差值小于等于零时，结束回路Lp1的流量补偿。
示例7.根据示例3所述的设备，其中该回路Lp1中流入执行器的实际流量为：该回路Lp1中主节流阀流过的流量与该回路Lp1中补充流量阀流过的流量的总和。
示例8.根据示例1所述的设备，其中，回路Lp1理论流量根据不同工况设定，所述工况至少包括压差和过流面积。
示例9.根据示例1所述的设备，其中回路Lp1的理论流量与液压系统中泵出口处压力与回路最高压力之间的 差、液压油液密度、过流系数和回路Lp1的过流面积相关。
示例10.根据示例9所述的设备，其中，该回路Lp1的过流面积和所述液压系统的工况要求相关。
示例11.根据示例1所述的设备,其中所述液压系统包括两个并联回路，每个回路包括执行元件和与执行元件连接的主阀和副阀；其中所述确定模块用于：当两个回路中的执行元件入口处的压力相等，则关闭每个回路中的副阀；当两个回路中的执行元件入口处的压力不相等，则选择压力较大的回路作为流量补偿的回路。
示例12.根据示例11所述的设备，其中所述流量补偿模块用于：如果压力较大的回路的理论流量与该回路中流入执行元件的实际流量差值大于零时，则开启该压力较大回路的副阀并关闭另一回路的副阀；如果压力较大的回路的理论流量与该回路中流入执行元件的实际流量差值小于等于零时，则结束该压力较大的回路流量补偿。
示例13.根据示例11所述的设备，所述确定模块用于：根据液压系统中的压力传感器阀来选择压力较大的回路作为流量补偿的回路。
示例14.根据示例11所述的设备，其中所述回路中的主阀和副阀并联连接。
示例15.根据示例3所述的设备，所液压系统包括为液压系统提供流量的泵，所述泵至少包括第一泵和第二泵，其中所述第一泵为所述主节流阀提供流量，所述第二泵为所述流量补充阀提供流量。
示例16.根据示例15所述的设备，所述设备能够进行补偿控制的流量的自由度最多为N-1；所述设备能够进行补偿的流量或压差的自由度最多为N+1。
第五组示例：
示例1.一种液压系统的流量分配控制装置，所述液压系统包括N个回路L1～LN，所述装置包括一个或多个处理器以及存储有程序指令的非暂时性计算机可读存储介质，当所述一个或多个处理器执行所述程序指令时，所述一个或多个处理器用于实现根据上述第三组示例1-16任意一项所述的方法。
第六组示例：
示例1.一种非暂时性计算机可读存储介质，其上存储有程序指令，当所述程序指令被一个或多个处理器执行时，所述一个或多个处理器用于实现根据上述第三组示例1-16任意一项所述的方法。
第七组示例：
示例1.一种液压系统，包括：用于为所述系统提供流量的泵；N个回路L1～LN，每个回路包括执行元件以及与执行元件连接的流量调节元件，所述流量调节元件用于为执行元件提供流量；所述液压系统还包括控制器，所述控制器与所述泵和流量调节元件相连接，所述控制器被配置为：比较液压系统每个回路中执行元件入口处的压力P1～PN；根据比较结果确定需要进行流量补偿的回路Lp1；根据所述回路Lp1的理论流量和所述回路Lp1中流入执行元件实际流量，对回路Lp1进行流量补偿,其中所述回路Lp1中的回路的数量小于或等于N。
示例2.根据示例1所述的液压系统，其中所述流量调节元件包括主节流阀和流量补充阀。
示例3.根据示例2所述的液压系统，其中所述主节流阀和流量补充阀并联连接。
示例4.根据示例1所述的液压系统，其中所述流量调节元件包括主阀和副阀。
示例5.根据示例4所述的液压系统，其中所述主阀和副阀并联连接。
示例6.根据示例1所述的液压系统，所述控制器还被配置为：确定所述执行元件入口处的压力P1～PN的最小值Pmin，所述Pmin对应的回路为Lp2，所述需要进行流量补偿的回路Lp1为：所述回路L1～LN中不包含回路Lp2的其他回路。
示例7.根据示例1或6所述的液压系统，其中所述N个回路L1～LN并联连接，每个回路包括执行元件，以及与执行元件相连接的主节流阀和流量补充阀，其中所述主节流阀和流量补充阀并联连接，所述N大于或等于2；其中所述控制器还被配置为：关闭回路Lp2的执行元件所连接的流量补充阀。
示例8.根据示例1所述的液压系统，其中所述控制器还被配置为：根据所述回路Lp1的理论流量和该回路Lp1中流入执行器的实际流量的差值，来对需要进行流量补偿的回路Lp1进行流量补偿控制。
示例9.根据示例7所述的液压系统，所述控制器还被配置为：通过调节需要进行流量补偿的回路Lp1中流量补充阀的流量来进行流量补偿。
示例10.根据示例1所述的液压系统，所述控制器还被配置为：当回路Lp1的理论流量和回路Lp1中流入执行元件的实际流量的差值小于等于零时，结束回路Lp1的流量补偿。
示例11.根据示例3所述的液压系统，其中该回路中流入执行器的实际流量为：该回路Lp1中主节流阀流过的流量与该回路Lp1中补充流量阀流过的流量的总和。
示例12.根据示例1所述的液压系统，其中，回路Lp1理论流量根据不同工况设定，所述工况至少包括压差和过流面积。
示例13.根据示例12所述的液压系统，其中回路Lp1的理论流量与液压系统中泵出口处压力与回路最高压力之间的差、液压油液密度、过流系数和回路Lp1的过流面积相关。
示例14.根据示例13所述的液压系统，其中，该回路Lp1的过流面积和所述液压系统的工况要求相关。
示例15.根据示例1所述的液压系统,其中包括两个并联回路，每个回路包括执行元件和与执行元件连接的主阀和副阀；其中所述控制器还被配置为：当两个回路中的执行元件入口处的压力相等，则关闭每个回路中的副阀； 当两个回路中的执行元件入口处的压力不相等，则选择压力较大的回路作为流量补偿的回路。
示例16.根据示例15所述的液压系统，其中所述控制器还被配置为：如果压力较大的回路的理论流量与该回路中流入执行元件的实际流量差值大于零时，则开启该压力较大回路的副阀并关闭另一回路的副阀；如果压力较大的回路的理论流量与该回路中流入执行元件的实际流量差值小于等于零时，则结束该压力较大的回路流量补偿。
示例17.根据示例15所述的液压系统，所述所述控制器还被配置为：根据液压系统中的压力传感器来选择压力较大的回路作为流量补偿的回路。
示例18.根据示例3所述的液压系统，所述泵至少包括第一泵和第二泵，其中所述第一泵为所述主节流阀提供流量，所述第二泵为所述流量补充阀提供流量。
示例19.根据示例18所述的设备，所述系统能够进行补偿控制的流量的自由度最多为N-1；所述系统能够进行补偿的流量或压差的自由度最多为N+1。
另外，本申请还公开了一种液压系统，包括本申请以上示例的流量分配控制系统，流量分配控制设备、流量分配控制装置、具有本申请上述的非暂时性计算机可读存储介质，或采用本申请的流量控制方法。
作为本申请示例的上文涉及的附图和本申请的详细描述，用于解释本申请，但不限制权利要求中描述的本申请的含义或范围。因此，本领域技术人员可以很容易地从上面的描述中实现修改。此外，本领域技术人员可以删除一些本文描述的组成元件而不使性能劣化，或者可以添加其它的组成元件以提高性能。此外，本领域技术人员可以根据工艺或设备的环境来改变本文描述的方法的步骤的顺序。因此，本申请的范围不应该由上文描述的实施例来确定，而是由权利要求及其等同形式来确定。
尽管本申请结合目前被认为是可实现的实施例已经进行了描述，但是应当理解本申请并不限于所公开的实施例，而相反的，意在覆盖包括在所附权利要求的精神和范围内的各种修改和等同配置。

Claims (15)

  1. 一种液压系统的流量分配控制方法，所述液压系统包括N个回路L1～LN，所述方法包括：
    S1：比较液压系统每个回路中的执行元件入口处的压力P1～PN；
    S2：根据比较结果确定需要进行流量补偿的回路Lp1；
    S3：根据回路Lp1的理论流量和回路Lp1中流入执行元件实际流量，对回路Lp1进行流量补偿，
    其中，所述回路Lp1中的回路的数量小于或等于N，
    其中所述N个回路L1～LN并联连接，每个回路包括执行元件和与执行元件相连接的主节流阀和流量补充阀，其中所述主节流阀和流量补充阀并联连接，所述N大于或等于2。
  2. 根据权利要求1所述的方法，确定所述每个回路中的执行元件入口处的压力P1～PN的最小值Pmin，所述Pmin对应的回路为Lp2，其中，所述需要进行流量补偿的回路Lp1为：所述回路L1～LN中不包含回路Lp2的其他回路。
  3. 根据权利要求1所述的方法，其中所述步骤S2包括：关闭回路Lp2的执行元件所连接的流量补充阀。
  4. 根据权利要求1所述的方法，其中在所述步骤S3中，根据回路Lp1的理论流量和回路Lp1中流入执行元件的实际流量的差值，通过调节回路Lp1中流量补充阀的流量对回路Lp1进行流量补偿控制。
  5. 根据权利要求1所述的方法，其中，回路Lp1中流入执行元件的实际流量为：回路Lp1中主节流阀流过的流量与回路Lp1中补充流量阀流过的流量的总和。
  6. 根据权利要求1所述的方法,其中所述液压系统包括两个并联回路，每个回路包括执行元件和与执行元件连接的主阀和副阀；其中所述步骤S2包括：
    当两个回路中的执行元件入口处的压力相等，则关闭每个回路中的副阀；
    当两个回路中的执行元件入口处的压力不相等，则选择压力较大的回路作为流量补偿的回路。
  7. 根据权利要求6所述的方法，其中所述步骤S3包括：
    如果压力较大的回路的理论流量与该回路中流入执行元件的实际流量差值大于零时，则开启该压力较大回路的副阀并关闭另一回路的副阀；
    如果压力较大的回路的理论流量与该回路中流入执行元件的实际流量差值小于等于零时，则结束该压力较大的回路流量补偿。
  8. 根据权利要求7所述的方法，所述步骤S2还包括：根据液压系统中的压力传感器来选择压力较大的回路作为流量补偿的回路。
  9. 根据权利要求8所述的方法，其中所述回路中的主阀和副阀并联连接。
  10. 根据权利要求1所述的方法，所液压系统包括为液压系统提供流量的泵，所述泵至少包括第一泵和第二泵，其中所述第一泵为所述主节流阀提供流量，所述第二泵为所述流量补充阀提供流量。
  11. 一种液压系统的流量分配控制设备，所述液压系统包括N个回路L1～LN，所述控制设备包括：
    比较模块，用于比较液压系统每个回路中执行元件入口处的压力P1～PN；
    确定模块，用于根据比较结果确定需要进行流量补偿的回路Lp1；
    流量补偿模块，用于根据回路Lp1的理论流量和回路Lp1中流入执行元件实际流量对 回路Lp1进行流量补偿，
    其中，所述回路Lp1中的回路的数量小于或等于N，
    其中所述N个回路L1～LN并联连接，每个回路包括执行元件和与执行元件相连接的主节流阀和流量补充阀，其中所述主节流阀和流量补充阀并联连接，其中所述N大于等于2。
  12. 一种液压系统的流量分配控制装置，所述液压系统包括N个回路L1～LN，所述装置包括一个或多个处理器以及存储有程序指令的非暂时性计算机可读存储介质，当所述一个或多个处理器执行所述程序指令时，所述一个或多个处理器用于实现根据权利要求1-10任意一项所述的方法。
  13. 一种非暂时性计算机可读存储介质，其上存储有程序指令，当所述程序指令被一个或多个处理器执行时，所述一个或多个处理器用于实现根据权利要求1-10中任一项所述的方法。
  14. 一种液压系统，包括：
    用于为所述系统提供流量的泵；
    N个回路L1～LN，每个回路包括执行元件和与执行元件连接的流量调节元件，所述流量调节元件用于为执行元件提供流量；
    所述液压系统还包括控制器，所述控制器与所述泵和流量调节元件相连接，所述控制器被配置为执行根据权利要求1-10中任一项所述的方法。
  15. 根据权利要求14所述的液压系统，其中所述流量调节元件包括主节流阀和流量补充阀。
PCT/CN2022/082482 2021-03-23 2022-03-23 液压系统的流量分配控制方法、设备和装置以及液压系统 WO2022199609A1 (zh)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP22774265.7A EP4317709A1 (en) 2021-03-23 2022-03-23 Flow distribution control method, device, and apparatus for hydraulic system and hydraulic system

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN202110309855.2A CN113027847B (zh) 2021-03-23 2021-03-23 液压系统的流量分配控制方法、设备和装置以及液压系统
CN202110309855.2 2021-03-23

Publications (1)

Publication Number Publication Date
WO2022199609A1 true WO2022199609A1 (zh) 2022-09-29

Family

ID=76473039

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2022/082482 WO2022199609A1 (zh) 2021-03-23 2022-03-23 液压系统的流量分配控制方法、设备和装置以及液压系统

Country Status (3)

Country Link
EP (1) EP4317709A1 (zh)
CN (1) CN113027847B (zh)
WO (1) WO2022199609A1 (zh)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113027847B (zh) * 2021-03-23 2022-04-26 中联重科股份有限公司 液压系统的流量分配控制方法、设备和装置以及液压系统
CN115899020B (zh) * 2022-12-19 2023-07-21 东北林业大学 一种比例阀控缸动态特性测试可编程试验台

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101858368A (zh) * 2010-05-13 2010-10-13 山东泰丰液压设备有限公司 负载敏感压力补偿回油节流控制多路换向阀系统
CN102734246A (zh) * 2012-07-13 2012-10-17 三一重工股份有限公司 液压阀及压力补偿方法、液压阀组、液压系统和工程机械
CN103573731A (zh) * 2012-07-24 2014-02-12 徐工集团工程机械股份有限公司 流量控制阀、流量控制装置以及液压油散热系统
CN105443471A (zh) * 2015-12-04 2016-03-30 湖南三一快而居住宅工业有限公司 一种多路阀和多路阀的流量补偿控制系统及方法
US20210048118A1 (en) * 2019-08-12 2021-02-18 Sun Hydraulics, Llc Proporational Flow Control Valve with an Integrated Pressure Compensator and Features for Flow Force Reduction
CN113027847A (zh) * 2021-03-23 2021-06-25 中联重科股份有限公司 液压系统的流量分配控制方法、设备和装置以及液压系统
CN215257058U (zh) * 2021-03-23 2021-12-21 中联重科股份有限公司 流量分配控制系统
CN215257059U (zh) * 2021-03-23 2021-12-21 中联重科股份有限公司 流量调节控制系统

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5134853A (en) * 1988-05-10 1992-08-04 Hitachi Construction Machinery Co., Ltd. Hydraulic drive system for construction machines
JP2005147257A (ja) * 2003-11-14 2005-06-09 Kayaba Ind Co Ltd 油圧制御装置
FR2948078B1 (fr) * 2009-07-17 2011-07-15 Lohr Ind Bloc hydraulique d'alimentation et de recalage pour un ensemble de levage a deux supports motorises independants actionnes simultanement
US8336232B2 (en) * 2010-09-08 2012-12-25 Caterpillar Inc. Multi-function wheel loader linkage control with optimized power management
JP2013079552A (ja) * 2011-10-05 2013-05-02 Komatsu Ltd 作業車両
CN202659605U (zh) * 2012-06-26 2013-01-09 南车二七车辆有限公司 一种重力平衡流量补偿式液压缸位移同步控制系统
CN207598616U (zh) * 2017-11-30 2018-07-10 圣邦集团有限公司 一种可变补偿压差的多路阀控制系统
CN111577687B (zh) * 2020-05-06 2021-10-08 太原理工大学 一种负载敏感双液压缸同步系统及其控制方法
CN111577680B (zh) * 2020-05-22 2021-08-27 中国矿业大学 一种负载敏感分流阀、变速同步驱动系统及工作方法
CN112064714B (zh) * 2020-08-26 2022-06-03 合肥工业大学 一种新型液压挖掘机流量控制系统

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101858368A (zh) * 2010-05-13 2010-10-13 山东泰丰液压设备有限公司 负载敏感压力补偿回油节流控制多路换向阀系统
CN102734246A (zh) * 2012-07-13 2012-10-17 三一重工股份有限公司 液压阀及压力补偿方法、液压阀组、液压系统和工程机械
CN103573731A (zh) * 2012-07-24 2014-02-12 徐工集团工程机械股份有限公司 流量控制阀、流量控制装置以及液压油散热系统
CN105443471A (zh) * 2015-12-04 2016-03-30 湖南三一快而居住宅工业有限公司 一种多路阀和多路阀的流量补偿控制系统及方法
US20210048118A1 (en) * 2019-08-12 2021-02-18 Sun Hydraulics, Llc Proporational Flow Control Valve with an Integrated Pressure Compensator and Features for Flow Force Reduction
CN113027847A (zh) * 2021-03-23 2021-06-25 中联重科股份有限公司 液压系统的流量分配控制方法、设备和装置以及液压系统
CN215257058U (zh) * 2021-03-23 2021-12-21 中联重科股份有限公司 流量分配控制系统
CN215257059U (zh) * 2021-03-23 2021-12-21 中联重科股份有限公司 流量调节控制系统

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
DU JIA, GANG XIAO, JING YANG, LONG QUAN: "Energy efficiency characteristics analysis for crane hydraulic system of pump-valve coordinated composite control", JOURNAL OF CENTRAL SOUTH UNIVERSITY(SCIENCE AND TECHNOLOGY), ZHONGNAN DAXUE, CHANGSHA, CN, vol. 52, no. 2, 28 February 2021 (2021-02-28), CN , pages 389 - 399, XP055970354, ISSN: 1672-7207, DOI: 10.11817/j.issn.1672-7207.2021.02.007 *

Also Published As

Publication number Publication date
EP4317709A1 (en) 2024-02-07
CN113027847A (zh) 2021-06-25
CN113027847B (zh) 2022-04-26

Similar Documents

Publication Publication Date Title
WO2022199609A1 (zh) 液压系统的流量分配控制方法、设备和装置以及液压系统
KR101597174B1 (ko) 건설기계의 유압회로
WO2012174937A1 (zh) 一种搭载负载敏感主阀与正流量泵的挖掘机液压系统
KR20140093657A (ko) 유압제어 시스템
WO2023036000A1 (zh) 一种闭式液压控制系统及工程机械
CN109139598A (zh) 一种基于机液压差补偿的双阀控式负载口独立控制阀
WO2023274210A1 (zh) 一种多级压力控制和压力调速液压系统及作业机械
CN215257058U (zh) 流量分配控制系统
CN215257059U (zh) 流量调节控制系统
CN207761575U (zh) 旋挖钻机主泵辅泵合流控制系统
WO2020188920A1 (ja) 油圧ショベル
CN208185091U (zh) 正控制负载敏感系统
CN210565427U (zh) 无人化农机的液压阀组
CN109306976B (zh) 一种负载敏感控制系统
CN108533556B (zh) 一种用于闭式与开式系统切换的补油切换阀及控制系统
CN116146555A (zh) 多路阀、首联、工作联、液压系统、方法和可读存储介质
CN216199342U (zh) 一种闭式液压控制系统及工程机械
CN109519428A (zh) 一种多液压泵复合控制系统、工作联及工程机械
CN109210024A (zh) 负流量液压控制油路及液压系统和挖掘机
CN112268032A (zh) 一种直臂随车起重机合流多路阀装置及其工作方法
CN212744559U (zh) 一种起重机扩展阀组及液压系统
CN210344387U (zh) 一种基于阻尼桥路的可变压差分流阀及液压控制系统
CN208442095U (zh) Lep电比例负载敏感泵及液压系统
Hießl et al. Energy Consumption and Efficiency Measurements of Different Excavators: Does Hybridization Pay?
CN114658708A (zh) 一种负载转速双敏感抗流量饱和系统及其工程机械装置

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 22774265

Country of ref document: EP

Kind code of ref document: A1

WWE Wipo information: entry into national phase

Ref document number: 2022774265

Country of ref document: EP

NENP Non-entry into the national phase

Ref country code: DE

ENP Entry into the national phase

Ref document number: 2022774265

Country of ref document: EP

Effective date: 20231023

WWE Wipo information: entry into national phase

Ref document number: 18552080

Country of ref document: US