CN116771744A - Flow-combining type throttle speed regulation multi-way valve and throttle linkage control system - Google Patents

Flow-combining type throttle speed regulation multi-way valve and throttle linkage control system Download PDF

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Publication number
CN116771744A
CN116771744A CN202310695722.2A CN202310695722A CN116771744A CN 116771744 A CN116771744 A CN 116771744A CN 202310695722 A CN202310695722 A CN 202310695722A CN 116771744 A CN116771744 A CN 116771744A
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CN
China
Prior art keywords
valve
oil
pressure reducing
control
reducing valve
Prior art date
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Pending
Application number
CN202310695722.2A
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Chinese (zh)
Inventor
商晓恒
余旋
任路遥
陈磊
刘振中
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Xuzhou XCMG Truck Mounted Crane Co Ltd
Original Assignee
Xuzhou XCMG Truck Mounted Crane Co Ltd
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Publication date
Application filed by Xuzhou XCMG Truck Mounted Crane Co Ltd filed Critical Xuzhou XCMG Truck Mounted Crane Co Ltd
Priority to CN202310695722.2A priority Critical patent/CN116771744A/en
Publication of CN116771744A publication Critical patent/CN116771744A/en
Pending legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • B66C13/00—Other constructional features or details
    • B66C13/18—Control systems or devices
    • B66C13/20—Control systems or devices for non-electric drives
    • 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
    • F15B13/025—Pressure reducing 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
    • 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
    • F15B13/027—Check valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/04—Special measures taken in connection with the properties of the fluid
    • F15B21/041—Removal or measurement of solid or liquid contamination, e.g. filtering
    • 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
    • F15B21/08—Servomotor systems incorporating electrically operated control means

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

Abstract

The invention discloses a combined flow type throttle speed regulation multi-way valve and throttle linkage control system, which comprises a big pump oil inlet linkage, a telescopic control linkage, a luffing control linkage, a winch control linkage, an oil return linkage, a rotary control linkage and a small pump oil inlet linkage which are connected in parallel; the telescopic control unit, the amplitude variation control unit, the hoisting control unit and the rotation control unit comprise one-way valves, reversing valves, a first electric proportional reversing valve and a second electric proportional reversing valve; in the scheme, all control units in the multi-way valve are integrated with the power-on proportional pressure reducing valve to realize the proportional relation between the axial opening of the main valve and the input electric signal, thereby realizing the electric control throttling speed regulation control; the throttle linkage control system can realize stable low-speed operation of the multi-way valve with a small opening and continuous acceleration operation of the multi-way valve with a large opening, and enlarges a speed regulation interval.

Description

Flow-combining type throttle speed regulation multi-way valve and throttle linkage control system
Technical Field
The invention relates to a straight arm lorry-mounted crane, in particular to a combined flow type throttling speed regulation multi-way valve and an accelerator linkage control system.
Background
The control mode of the straight arm lorry-mounted crane is changed from manual control to electric control intelligent control. Compared with the existing manual control converging multi-way valve, the control freedom degree is limited, lifting personnel are required to be configured during lifting, the problem that the low-speed state compositeness is poor and the processing and manufacturing cost is high is solved compared with the existing single-pump proportional load sensitive multi-way valve scheme, the whole machine speed control is only related to the opening degree of a main valve core, the whole machine system is controlled in a remote control mode, the chassis is controlled in a fixed speed mode, the accelerator is required to be controlled independently for accelerating during acceleration, and the speed regulation interval is required to be enlarged in the action control process in consideration of the fact that the lorry-mounted crane is an efficient machine, so that the working efficiency is improved.
Disclosure of Invention
The invention aims to: the invention aims to provide a current-combined type throttling speed-regulating multi-way valve and an accelerator linkage control system, wherein all control units in the multi-way valve are integrated with a power-on proportional pressure reducing valve to realize proportional relation between the axial opening of a main valve and an input electric signal, so as to realize electric control throttling speed-regulating control; the throttle linkage control system can realize stable low-speed operation of the multi-way valve with a small opening and continuous acceleration operation of the multi-way valve with a large opening, and enlarges a speed regulation interval.
The technical scheme is as follows: the invention comprises a big pump oil inlet unit, a telescopic control unit, a variable amplitude control unit, a winch control unit, an oil return unit, a rotation control unit and a small pump oil inlet unit which are connected in parallel; the telescopic control unit, the amplitude variation control unit, the hoisting control unit and the rotation control unit comprise a one-way valve, a reversing valve, a first electric proportional pressure reducing valve and a second electric proportional pressure reducing valve; the first working oil ports of the first electric proportional pressure reducing valve and the second electric proportional pressure reducing valve are connected with an oil tank, the second working oil ports of the first electric proportional pressure reducing valve and the second electric proportional pressure reducing valve are connected with an oil outlet of the oil inlet unit of the large pump, and the third working oil ports of the first electric proportional pressure reducing valve and the second electric proportional pressure reducing valve are connected with a pilot oil port of the reversing valve; the first working oil port of the reversing valve is provided with a one-way valve, the one-way valve is connected with the oil inlet P1 or P2, the second working oil port of the reversing valve is connected with the oil inlet P1 or P2, the third working oil port of the reversing valve is connected with the oil return port T1 or T2, the fourth working oil port and the sixth working oil port of the reversing valve are used for being connected with a hydraulic actuator, and the fifth working oil port of the reversing valve is connected with the second working oil port or the oil return port of the reversing valve in the subsequent control unit.
Different current signals are applied to the first electric proportional pressure reducing valve and the second electric proportional pressure reducing valve to enable the first electric proportional pressure reducing valve and the second electric proportional pressure reducing valve to be opened in proportion, the generated control pressure controls the axial opening of the reversing valve correspondingly, and accordingly the corresponding hydraulic actuating element is pushed to act.
The large pump oil inlet unit comprises a filtering element, a damping element and a constant-difference pressure reducing valve which are arranged in series, wherein the input end of the filtering element is connected with a pilot X port, and the output end of the constant-difference pressure reducing valve is connected with a second working oil port of the first electric proportional pressure reducing valve and the second electric proportional pressure reducing valve.
The oil return port is provided with an oil return back pressure valve, the input end of the oil return back pressure valve is connected with the oil return ports T1 and T2, and the oil return back pressure valve enables the electric proportional pressure reducing valve to be capable of effectively and stably building pressure when the remote rod inputs an electric signal, so that the valve core is driven to move.
A large-pump main overflow valve is arranged between the oil inlet P1 and the oil return port T1, and a small-pump main overflow valve is arranged between the oil inlet P2 and the oil return port T2.
The invention further comprises an accelerator linkage control system which comprises a current-combined type throttling speed regulation multi-way valve, and the accelerator linkage control system is connected with the accelerator of the bottom vehicle.
The throttle linkage system is opened according to the opening states of the electric control tele-rods in the telescopic tele-rod, the amplitude tele-rod, the winding tele-rod and the rotary tele-rod.
When any one of the telescopic tele rod, the amplitude varying tele rod, the winding tele rod and the rotary tele rod is single-acting, the throttle linkage control system is in a closed state when the electric control tele rod is in a small opening stage, the bottom vehicle is in an idle state, the low-current electric signal proportionally generates low control pressure through the electric proportional pressure reducing valve, and the reversing valve is driven to axially small opening to realize low-speed action; when the electronic control tele-lever is operated in a large opening stage, the accelerator linkage system is in an opening state, the bottom vehicle is in an accelerating state, the high-current electric signal drives the electric proportional pressure reducing valve to proportionally generate high control pressure, the reversing valve is driven to axially open, the bottom vehicle is accelerated, and the input flow is further amplified, so that high-speed operation is realized.
When two of the telescopic tele rod, the amplitude varying tele rod, the winding tele rod and the rotary tele rod are double-acting, when the two acting electric control tele rods are in a small opening stage, the throttle linkage system control system is in a closed state, the bottom vehicle is in an idle state, the low-current electric signal is in a proportional mode through the electric proportional pressure reducing valve to generate low control pressure, the reversing valve is driven to axially form a small opening, and oil liquid of the large pump C1 and the small pump C2 is used for providing oil pressure for the control unit through oil inlet paths of the large pump and the small pump, so that low-speed compound action is realized.
When two remote rods of the telescopic remote rod, the amplitude changing remote rod, the winding remote rod and the rotary remote rod are double-acting, when a certain action is slower, the action is continuously pushed, and the electronic control remote rod is in a large opening stage, the accelerator linkage control system is started, the bottom vehicle is in an acceleration state, the flow provided by the large pump C1 and the small pump C2 is improved, the high-current electric signal generates high control pressure in proportion through the electric proportional pressure reducing valve, the axial large opening of the main valve of the certain action is driven, the input flow is increased, and the action acceleration is realized; and the other action is that the action electric control remote rod is still in a small opening stage, and a low-current electric signal is output so that the electric proportional pressure reducing valve generates low control pressure, and the axial direction of the reversing valve is still in a small opening throttling state. It can be seen that although the input flow is increased, the acceleration state of the motion is weakened, so that the composite motion speed is more balanced.
The beneficial effects are that: compared with the prior art, the technical scheme of the invention has the beneficial effects that:
(1) The opening and closing of the throttle linkage system are determined according to the opening state of the electric control remote rod, so that the throttle multi-way valve can stably run at a low speed in a small opening and can continuously run at an accelerated speed in a large opening, a speed regulation interval is enlarged, and the working efficiency is improved;
(2) The oil is fed to the two pumps respectively for control during low-speed compounding in the common compound working condition, so that the anti-saturation performance is realized; the speed of the compound action is more balanced by means of the speed lifting difference after the acceleration intervention of the accelerator during the high-speed compound;
(3) The electric control setting of the throttle speed regulation double-pump system of the lorry-mounted crane is realized, and the throttle speed regulation double-pump system has certain economical efficiency and popularization.
Drawings
FIG. 1 is a hydraulic schematic diagram of an electric proportional control current-combined type throttling speed regulation multi-way valve;
FIG. 2 is a front view of an electrically proportional controlled, current-combined, throttled, speed-regulating multiway valve;
FIG. 3 is a side view of an electrically proportional controlled, current-combined type throttle speed regulating multiway valve;
fig. 4 is a schematic flow chart of the throttle linkage system.
Detailed Description
The technical scheme of the invention is described in detail below with reference to the detailed description and the attached drawings.
As shown in fig. 1 and 2, the current-combined type throttling speed regulation multiway valve of the invention relates to the following components: the hydraulic oil pump is characterized by comprising a large pump oil inlet unit 1, a large pump main overflow valve 11, a filtering element 12, a damping element 13, a constant difference pressure reducing valve 14, a telescopic control unit 2, a first one-way valve 21, a telescopic reversing valve 22, a telescopic first electric proportional pressure reducing valve 23, a telescopic second electric proportional pressure reducing valve 24, a luffing control unit 3, a second one-way valve 31, a luffing reversing valve 32, a luffing first electric proportional pressure reducing valve 33, a luffing second electric proportional pressure reducing valve 34, a luffing control unit 4, a third one-way valve 41, a luffing reversing valve 42, a luffing first electric proportional pressure reducing valve 43, a luffing second electric proportional pressure reducing valve 44, an oil return unit 5, a fourth one-way valve 51, an oil return back pressure valve 52, a rotary control unit 6, a fifth one-way valve 61, a rotary control valve 62, a rotary first electric proportional pressure reducing valve 63, a rotary second electric proportional pressure reducing valve 64, a small pump oil inlet unit 7, a small pump main overflow valve 71 and an external control port 9. Other elements also involved in this scheme: the hydraulic system comprises a telescopic oil cylinder 81, a luffing oil cylinder 82, a hoisting mechanism 83, a slewing mechanism 84, a large pump C1 and a small pump C2. The large pump C1 provides oil for the expansion and amplitude variation of the crane through the large pump oil inlet joint 1, the small pump C2 provides oil for the rotation of the crane through the small pump oil inlet joint 7, and the large pump and the small pump respectively provide oil for the winch of the crane after being converged through the first oil inlet path and the second oil inlet path.
The large pump oil inlet unit 1, the telescopic control unit 2, the variable amplitude control unit 3, the winch control unit 4, the oil return unit 5, the rotary control unit 6 and the small pump oil inlet unit 7 are connected in parallel.
The large pump oil inlet unit 1 comprises a large pump main overflow valve 11, a filter element 12, a damping element 13 and a constant difference pressure reducing valve 14. The large pump main relief valve 11 is provided between the oil inlet P1 and the oil return port T1. The filter element 12, the damping element 13 and the constant-difference pressure reducing valve 14 are arranged in series, wherein the input end of the filter element 12 is connected with a pilot X port, the output end of the constant-difference pressure reducing valve 14 is connected with a first working oil port of the first electric proportional pressure reducing valve and a second working oil port of the second electric proportional pressure reducing valve, oil pressure of an oil source enters the constant-difference pressure reducing valve 14 through a pilot oil path, the filter element 12 and the damping element 13 to carry out primary pressure reduction, oil pressure lower than the oil pressure is generated, and the electric proportional pressure reducing valve is protected to work in a rated pressure range. The electric proportional pressure reducing valve performs secondary pressure reduction, and the generated control pressure changes in proportion to the input electric signal, so that the valve core spring force is overcome to drive the valve core to move.
The telescopic control unit 2 comprises a first one-way valve 21, a telescopic reversing valve 22, a telescopic first electric proportional pressure reducing valve 23 and a telescopic second electric proportional pressure reducing valve 24. The first working oil port (namely, the oil port F4) of the telescopic reversing valve 22 is provided with a first one-way valve 21, an oil inlet of the first one-way valve 21 is connected with a second working oil port of the telescopic reversing valve 22, the second working oil port of the telescopic reversing valve 22 is connected with an oil inlet P1, a third working oil port (namely, the oil port F1) of the telescopic reversing valve 22 is connected with an oil return port T1, a fourth working oil port (namely, the oil port F3) of the telescopic reversing valve 22 is used for being connected with a rod cavity of the telescopic oil cylinder 81, a fifth working oil port of the telescopic reversing valve 22 is connected with a second working oil port of the variable-amplitude reversing valve 32 in the variable-amplitude control unit 3, and a sixth working oil port (namely, the oil port F2) of the telescopic reversing valve 22 is used for being connected with a rodless cavity of the telescopic oil cylinder 81. The first working oil ports of the telescopic first electric proportional pressure reducing valve 23 and the telescopic second electric proportional pressure reducing valve 24 are connected with an oil tank, the second working oil ports of the telescopic first electric proportional pressure reducing valve 23 and the telescopic second electric proportional pressure reducing valve 24 are connected with the output end of the constant-difference pressure reducing valve 14, and the third working oil ports of the telescopic first electric proportional pressure reducing valve 23 and the telescopic second electric proportional pressure reducing valve 24 are connected with the pilot oil port of the telescopic reversing valve 22.
The amplitude variation control unit 3 comprises a second one-way valve 31, an amplitude variation reversing valve 32, an amplitude variation first electric proportional pressure reducing valve 33 and an amplitude variation second electric proportional pressure reducing valve 34. The first working oil port (namely, the oil port G4) of the amplitude changing reversing valve 32 is provided with a second one-way valve 31, an oil inlet of the second one-way valve 31 is connected with an oil inlet of the first one-way valve 21, the second working oil port of the amplitude changing reversing valve 32 is connected with a fifth working oil port of the telescopic reversing valve 22, a third working oil port (namely, the oil port G1) of the amplitude changing reversing valve 32 is connected with an oil return port T1, a fourth working oil port (namely, the oil port G3) of the amplitude changing reversing valve 32 is used for being connected with a rod cavity of the amplitude changing oil cylinder 82, the fifth working oil port of the amplitude changing reversing valve 32 is connected with a second working oil port of the hoisting reversing valve 42 in the hoisting control unit 4, and a sixth working oil port (namely, the oil port G2) of the amplitude changing reversing valve 32 is used for being connected with a rod-free cavity of the amplitude changing oil cylinder 82. The first working oil ports of the amplitude-variable first electric proportional pressure reducing valve 33 and the amplitude-variable second electric proportional pressure reducing valve 34 are connected with an oil tank, the second working oil ports of the amplitude-variable first electric proportional pressure reducing valve 33 and the amplitude-variable second electric proportional pressure reducing valve 34 are connected with the output end of the constant-difference pressure reducing valve 14, and the third working oil ports of the amplitude-variable first electric proportional pressure reducing valve 33 and the amplitude-variable second electric proportional pressure reducing valve 34 are connected with the pilot oil port of the amplitude-variable reversing valve 32.
The winch control unit 4 comprises a third one-way valve 41, a winch reversing valve 42, a winch first electric proportional pressure reducing valve 43 and a winch second electric proportional pressure reducing valve 44. The first working oil port (namely, the oil port H4) of the winch reversing valve 42 is provided with a third one-way valve 41, an oil inlet of the third one-way valve 41 is connected with an oil outlet of the fourth one-way valve 51 and the first working oil port of the winch reversing valve 42, the second working oil port of the winch reversing valve 42 is connected with a fifth working oil port of the variable amplitude reversing valve 32, the third working oil port (namely, the oil port H1) of the winch reversing valve 42 is connected with an oil return port T1, the fourth working oil port (namely, the oil port H3) of the winch reversing valve 42 is used for being connected with a winch mechanism 83, the fifth working oil port of the winch reversing valve 42 is connected with the oil return port T1, and the sixth working oil port (namely, the oil port H2) of the winch reversing valve 42 is used for being connected with the winch mechanism 83. The first working oil ports of the winch first electric proportional pressure reducing valve 43 and the winch second electric proportional pressure reducing valve 44 are connected with an oil tank, the second working oil ports of the winch first electric proportional pressure reducing valve 43 and the winch second electric proportional pressure reducing valve 44 are connected with the output end of the constant-difference pressure reducing valve 14, and the third working oil ports of the winch first electric proportional pressure reducing valve 43 and the winch second electric proportional pressure reducing valve 44 are connected with the pilot oil port of the winch reversing valve 42.
The oil return unit 5 comprises a fourth one-way valve 51 and an oil return back pressure valve 52, and an oil inlet of the fourth one-way valve 51 is connected with a fifth working oil port and an oil return port T1 of the rotary control valve 62. The oil return back pressure valve 52 is arranged at the oil return port, the input end of the oil return back pressure valve 52 is connected with the oil return ports T1 and T2, and the output end of the oil return back pressure valve 52 is connected with the oil tank. By adding the oil return back pressure valve 52 to the oil return port, the pilot oil path maintains certain oil pressure, and the phenomenon that the electric proportional pressure reducing valve generates lower control pressure and cannot drive the main valve core under the low-pressure state with small action opening is prevented.
The rotary control unit 6 includes a fifth check valve 61, a rotary control valve 62, a rotary first electric proportional pressure reducing valve 63, and a rotary second electric proportional pressure reducing valve 64. The first working oil port (i.e., the oil port I4) of the rotary control valve 62 is provided with a fifth one-way valve 61, an oil inlet of the fifth one-way valve 61 is connected with the oil inlet P2, a second working oil port of the rotary control valve 62 is connected with the oil inlet P2, a third working oil port (i.e., the oil port I1) of the rotary control valve 62 is connected with the oil return port T2, a fourth working oil port (i.e., the oil port I3) of the rotary control valve 62 is used for connecting with the rotary mechanism 84, a fifth working oil port of the rotary control valve 62 is connected with the oil inlet of the fourth one-way valve 51, and a sixth working oil port (i.e., the oil port I2) of the rotary control valve 62 is used for connecting with the rotary mechanism 84. The first working oil ports of the rotary first electro-proportional pressure reducing valve 63 and the rotary second electro-proportional pressure reducing valve 64 are connected with an oil tank, the second working oil ports of the rotary first electro-proportional pressure reducing valve 63 and the rotary second electro-proportional pressure reducing valve 64 are connected with the output end of the constant difference pressure reducing valve 14, and the third working oil ports of the rotary first electro-proportional pressure reducing valve 63 and the rotary second electro-proportional pressure reducing valve 64 are connected with the pilot oil port of the rotary control valve 62.
The small pump oil inlet unit 7 comprises a small pump main overflow valve 71, and the small pump main overflow valve 71 is arranged between the oil inlet P2 and the oil return port T2.
According to the scheme, two electric proportional pressure reducing valves of each link are used for realizing bidirectional remote control action, and a pilot proportional direction valve can be used for replacing the two electric proportional pressure reducing valves to serve as a pilot stage to control the movement of the main valve core. The scheme integrates the electric proportional pressure reducing valves on each control unit, and an intelligent remote control double-pump system is realized.
As shown in fig. 3, in this example, a threaded connection port D is reserved at the tail end of the control link of the multi-way valve, and by connecting a flexible shaft or a connecting rod, remote manual emergency control can be realized.
As shown in FIG. 4, the invention further comprises an accelerator linkage control system which comprises a current-combined type throttling speed regulation multi-way valve controlled by electric proportion, and the accelerator linkage control system is connected with the accelerator of the bottom vehicle. And the opening of the throttle linkage system is realized according to the opening states of the electric control tele-rods in the telescopic tele-rod, the amplitude tele-rod, the winding tele-rod and the rotary tele-rod. The opening of the electric control remote rod is related to the accelerator of the bottom car, and the multi-way valve is controlled by the remote rod to realize low-speed stable operation and high-speed high-efficiency operation.
Referring to fig. 2 and 3, the following is an action process of the throttle linkage control system:
in this example, when all the remote rods are motionless, the oil of the large pump C1 enters the multi-way valve through the P1 port, part of the oil is introduced into the pilot X port through the side pressure port, flows through the filter element 12, the damping element 13 and the constant differential pressure reducing valve 14 to the proportional pressure reducing valves, and before the proportional pressure reducing valves are all connected, the proportional pressure reducing valves are in a closed state due to no electric signal input by remote control, the oil of the large pump reaches the oil return port T1 through the telescopic control unit 2, the amplitude control unit 3 and the winch control unit 4, flows through the oil return back pressure valve 52 and returns to the oil tank, the oil of the small pump C2 enters the multi-way valve through the P2 port, flows through the rotary control unit 6 to the oil return port T2, and flows through the oil return back pressure valve 52 and returns to the oil tank. The oil return back pressure valve 52 enables the electric proportional pressure reducing valve to build pressure efficiently and stably when the remote rod inputs an electric signal, so that the valve core is driven to move.
In this example, when the telescopic remote rod is in a small opening stage, the throttle linkage control system is in a closed state, the bottom vehicle is in an idle state, the oil of the large pump C1 enters the multi-way valve through the P1 port, part of the oil is introduced into the pilot X port through the side pressure port, flows through the filter element 12, the damping element 13 and the fixed difference reducing valve 14 to the telescopic first electric proportional reducing valve 23, the small opening of the telescopic remote rod outputs a low current signal to enable the telescopic first electric proportional reducing valve 23 to be opened in proportion, correspondingly generates low control pressure to drive the telescopic reversing valve 22 to be in a lower small opening, and the oil of the large pump C1 flows through the oil port F4 of the telescopic reversing valve 22 to the oil port F2 through the P1 port opening first one-way valve 21, so as to push the telescopic high-low speed operation;
when the telescopic action electronic control remote rod is in a large opening stage, the accelerator linkage control system is in an opening state, the bottom vehicle is in an accelerating state, the large opening of the remote rod outputs a high current signal to enable the telescopic first electric proportional pressure reducing valve 23 to be opened in proportion, correspondingly high control pressure is generated to drive the telescopic reversing valve 22 to be in a large opening at the lower position, the large pump C1 oil liquid opens the first one-way valve 21 through the P1 opening to flow through the oil port F4 to the oil port F2 of the telescopic reversing valve 22, the bottom vehicle is accelerated, and the input flow is further amplified, so that the telescopic action is pushed. The opening of the telescopic extension rod is continuously increased, and the accelerator of the bottom car is continuously accelerated, so that the speed regulation interval of the telescopic extension action is enlarged.
When the telescopic action electric control remote rod is in a small opening stage, the throttle linkage control system is in a closed state, the bottom vehicle is in an idle state, oil of a large pump C1 enters the multi-way valve through a P1 port, part of the oil is introduced into a pilot X port through a side pressure port, and flows through the filter element 12, the damping element 13 and the constant difference reducing valve 14 before reaching the telescopic second electric proportional reducing valve 24, the small opening of the remote rod outputs a low current signal so that the telescopic second electric proportional reducing valve 24 is opened in proportion, correspondingly, low control pressure is generated to drive the telescopic reversing valve 22 to be in an upper small opening, and the oil of the large pump C1 flows through an oil port F1 to an oil port F3 of the telescopic reversing valve 22 through a P1 port to push the telescopic action;
when the telescopic action electric control remote rod is in a large opening stage, the accelerator linkage control system is in an opening state, the bottom vehicle is in an accelerating state, the large opening of the remote rod outputs a high current signal to enable the telescopic second electric proportional pressure reducing valve 24 to be opened in proportion, correspondingly high control pressure is generated to drive the telescopic reversing valve 22 to be in an upper large opening, the large pump C1 oil liquid opens the first one-way valve 21 through the P1 opening to flow through the oil port F1 to the oil port F3 of the telescopic reversing valve 22, the bottom vehicle is accelerated, and the input flow is further amplified, so that the telescopic action is pushed. The opening of the telescopic rod is continuously increased, and the accelerator of the bottom car is continuously accelerated, so that the telescopic action speed regulation interval is enlarged.
In this example, when the amplitude-changing remote rod is single-acting, when the amplitude-changing action electric control remote rod is in a small opening stage, the accelerator linkage control system is in a closed state, the bottom vehicle is in an idle state, the oil of the large pump C1 enters the multi-way valve through the P1 port, part of the oil is introduced into the pilot X port through the side pressure port, flows through the filter element 12, the damping element 13 and the fixed differential pressure reducing valve 14 to the amplitude-changing first electric proportional pressure reducing valve 33, the small opening of the remote rod outputs a low-current signal to enable the amplitude-changing first electric proportional pressure reducing valve 33 to be opened in proportion, correspondingly generates low control pressure to drive the amplitude-changing reversing valve 32 to be in a lower small opening, and the oil of the large pump C1 flows through the oil port G4 to the oil port G2 of the amplitude-changing reversing valve 32 through the P1 port opening second one-way valve 31, so that amplitude changing is driven to start low-speed action.
When the amplitude-variable action electric control remote rod is in a large opening stage, the accelerator linkage control system is in an opening state, the bottom vehicle is in an accelerating state, the large opening of the remote rod outputs a high current signal to enable the amplitude-variable first electric proportional pressure reducing valve 33 to be opened in proportion, correspondingly high control pressure is generated to drive the amplitude-variable reversing valve 32 to be in a large opening at the lower position, the large pump C1 oil liquid opens the second one-way valve 31 through the P1 opening to flow through the oil port G4 to the oil port G2 of the amplitude-variable reversing valve 32, the bottom vehicle is accelerated, and the input flow is further amplified, so that the amplitude-variable action is driven at a high speed. The opening of the amplitude-variable starting remote rod is continuously increased, and the accelerator of the bottom car is continuously accelerated, so that the amplitude-variable starting is used for amplifying a speed regulation interval.
When the amplitude-change falling action electric control remote rod is in a small opening stage, the accelerator linkage control system is in a closed state, the bottom vehicle is in an idle state, oil in a large pump C1 enters the multi-way valve through a P1 port, part of the oil is introduced into a pilot X port through a side pressure port, flows through the filter element 12, the damping element 13 and the constant difference reducing valve 14 before reaching the amplitude-change second electric proportional reducing valve 34, the small opening of the remote rod outputs a low-current signal so that the amplitude-change second electric proportional reducing valve 34 is opened in proportion, the amplitude-change reversing valve 32 is driven to be in an upper small opening correspondingly to generate low control pressure, and the oil in the large pump C1 flows through an oil port G1 to an oil port G3 of the amplitude-change reversing valve 32 through a P1 port so as to push amplitude-change falling low-speed actions.
When the amplitude-change falling action electric control remote rod is in a large opening stage, the accelerator linkage control system is in an opening state, the bottom vehicle is in an accelerating state, the large opening of the remote rod outputs a high current signal to enable the amplitude-change second electric proportional pressure reducing valve 34 to be opened in proportion, correspondingly high control pressure is generated to drive the amplitude-change reversing valve 32 to be in an upper large opening, the large pump C1 oil liquid opens the second one-way valve 31 through the P1 opening to flow through the oil port G1 to the oil port G3 of the amplitude-change reversing valve 32, the bottom vehicle is accelerated, and the input flow is further amplified, so that the amplitude-change falling high-speed action is pushed. The opening of the amplitude-variable drop remote rod is continuously increased, and the accelerator of the bottom car is continuously accelerated, so that the amplitude-variable drop action speed regulation interval is enlarged.
In this example, when the winch remote rod is single-acting, when the winch starting electric control remote rod is in a small opening stage, the accelerator linkage control system is in a closed state, the bottom vehicle is in an idle state, the oil of the big pump C1 enters the multi-way valve through the P1 port, part of the oil is introduced into the pilot X port through the side pressure port, flows through the filter element 12, the damping element 13 and the fixed differential pressure reducing valve 14 to the winch first electric proportional pressure reducing valve 43, the small opening of the remote rod outputs a low-current signal to enable the winch first electric proportional pressure reducing valve 43 to be opened in proportion, correspondingly generates low control pressure to drive the winch reversing valve 42 to be in a lower small opening, and the oil of the big pump C1 and the oil of the small pump C2 form a confluence after the oil of the big pump C1 and the oil of the small pump C2 are opened through the P2 port and the fourth one-way valve 51 to flow through the oil port H4 of the winch reversing valve 42 through the third one-way valve 41, so as to push the winch to lift and lift to move at a low speed.
When the winch is started and the electric control remote rod is in a large opening stage, the accelerator linkage control system is in an opening state, the bottom vehicle is in an accelerating state, the large opening of the remote rod outputs a high current signal to enable the winch first electric proportional pressure reducing valve 43 to be opened in proportion, the winch reversing valve 42 is correspondingly driven to be in a lower large opening by generating high control pressure, the oil of the large pump C1 and the oil of the small pump C2 are opened through the P2 port to form a confluence after the fourth one-way valve 51 is opened through the P1 port and the oil of the small pump C2, the confluence flows through an oil port H4 to an oil port H2 of the winch reversing valve 42 through the third one-way valve 41, the bottom vehicle is accelerated, and the input flow is further amplified, so that the rolling-up high-speed action is promoted. The opening of the rolling-up remote rod is continuously increased, and the accelerator of the bottom car is continuously accelerated, so that the winch is started to amplify the speed regulation interval.
When the electric control remote rod of the winch falling action is in a small opening stage, the throttle linkage control system is in a closed state, the bottom vehicle is in an idle state, oil of the large pump C1 enters the multi-way valve through the P1 port, part of the oil is introduced into the pilot X port through the side pressure port, flows through the filter element 12, the damping element 13 and the constant difference reducing valve 14 to the front of the winch second electric proportional reducing valve 44, the small opening of the remote rod outputs a low current signal so that the winch second electric proportional reducing valve 44 is opened in proportion, the winch reversing valve 42 is driven to be in an upper small opening correspondingly to generate low control pressure, oil of the large pump C1 and oil of the small pump C2 are formed to flow into an oil port H1 to an oil port H3 of the winch reversing valve 42 through the third one-way valve 41 after the fourth one-way valve 51 is opened through the P2 port, and accordingly the winch falling action is pushed.
When the electric control remote rod of the winch falling action is in a large opening stage, the accelerator linkage control system is in an opening state, the bottom vehicle is in an accelerating state, the large opening of the remote rod outputs a high current signal to enable the winch second electric proportional pressure reducing valve 44 to be opened in proportion, the corresponding high control pressure is generated to drive the amplitude changing reversing valve 32 to be in an upper large opening, the oil of the large pump C1 and the oil of the small pump C2 are opened through the P2 to form a confluence through the third one-way valve 41 after the fourth one-way valve 51 is opened, and the input flow is further amplified, so that the winch falling high-speed action is promoted. The opening of the winch falling remote rod is continuously increased, and the accelerator of the bottom car is continuously accelerated, so that the speed regulation interval of the winch falling action is enlarged.
In this example, when the rotary tele-lever is in a small opening stage, the throttle linkage control system is in a closed state, the bottom vehicle is in an idle state, the oil of the large pump C1 enters the multi-way valve through the port P1, part of the oil is introduced into the pilot port X through the side pressure port, flows through the filter element 12, the damping element 13 and the fixed differential pressure reducing valve 14 to the rotary first electric proportional pressure reducing valve 63, the small opening of the tele-lever outputs a low current signal to enable the rotary first electric proportional pressure reducing valve 63 to be opened in proportion, the rotary control valve 62 is driven to be in a lower small opening correspondingly to generate low control pressure, and the oil of the small pump C2 flows through the port I4 to the port I2 of the rotary control valve 62 through the port P2 to open the fifth one-way valve 61, so that the rotary forward low-speed operation is pushed;
when the rotary forward-acting electric control remote rod is in a large opening stage, the accelerator linkage control system is in an opening state, the bottom vehicle is in an accelerating state, the large opening of the remote rod outputs a high current signal to enable the rotary first electric proportional pressure reducing valve 63 to be opened in proportion, correspondingly high control pressure is generated to drive the rotary control valve 62 to be in a large opening at the lower position, the small pump C2 oil liquid opens the fifth one-way valve 61 through the P2 opening to flow through the oil port I4 to the oil port I2 of the rotary control valve 62, the bottom vehicle is accelerated, and the input flow is further amplified, so that rotary forward-high-speed acting is pushed. The opening of the rotary forward and reverse lever is continuously increased, and the accelerator of the bottom car is continuously accelerated, so that the rotary forward action speed regulation interval is enlarged.
When the rotary reverse-acting electric control remote rod is in a small opening stage, the throttle linkage control system is in a closed state, the bottom vehicle is in an idle state, oil in a large pump C1 enters the multi-way valve through a P1 port, part of the oil is introduced into a pilot X port through a side pressure port, flows through the filter element 12, the damping element 13 and the constant difference reducing valve 14 to the rotary second electric proportional reducing valve 64, the small opening of the remote rod outputs a low-current signal so that the rotary second electric proportional reducing valve 64 is proportionally opened, the rotary control valve 62 is correspondingly driven to be in an upper small opening by generating low control pressure, and the oil in the small pump C2 flows through an oil port I1 to an oil port I3 of the rotary control valve 62 through a P2 port, so that rotary reverse-acting low-speed is pushed.
When the rotary reverse action electric control remote rod is in a large opening stage, the accelerator linkage control system is in an opening state, the bottom vehicle is in an accelerating state, the large opening of the remote rod outputs a high current signal to enable the rotary second electric proportional pressure reducing valve 64 to be opened in proportion, correspondingly high control pressure is generated to drive the rotary control valve 62 to be in an upper large opening, the small pump C2 oil liquid opens the fifth one-way valve 61 through the P2 opening to flow through the oil port I1 to the oil port I3 of the rotary control valve 62, the bottom vehicle is accelerated, and the input flow is further amplified, so that rotary reverse high-speed action is pushed. The opening of the rotary reverse remote rod is continuously increased, and the accelerator of the bottom car is continuously accelerated, so that the rotary reverse action speed regulation interval is enlarged.
In the example, when the remote control stretching and hoisting double action are carried out, when the two action electric control tele rods are in a small opening stage, the throttle linkage control system is in a closed state, the bottom vehicle is in an idle state, the oil of the large pump C1 enters the multi-way valve through the port P1, part of the oil is led into the port X through the side pressure port, the oil flows through the filtering element 12, the damping element 13 and the fixed difference reducing valve 14 to the stretching first electric proportional reducing valve 23 and the hoisting first electric proportional reducing valve 43, the small opening of the stretching tele rod outputs a low current signal to enable the stretching first electric proportional reducing valve 23 to be opened in proportion, the corresponding low control pressure is generated to drive the stretching reversing valve 22 to be in a small opening at a lower position, the oil of the large pump C1 flows through the port F4 of the stretching reversing valve 22 to the port F2 through the port P1, so that the stretching low speed quick action is pushed, and the hoisting tele rod small opening of the telescopic tele rod outputs a low current signal to enable the hoisting first electric proportional reducing valve 43 to be opened in proportion, and the corresponding low control pressure is generated to drive the hoisting valve 42 to be in a small opening at a lower position, the small opening, the small pump C2 flows through the port P2 to drive the reversing valve 4 to flow through the fourth reversing valve 4H 51 to push the oil to flow through the reversing valve 41 to a small opening of the reversing valve 4; at this time, if the winch action needs to be accelerated, the electric control remote rod for winch starting is pushed to be in a large opening stage, the accelerator linkage control system is in an opening state, the bottom vehicle is in an accelerating state, the large opening of the remote rod outputs a high current signal to enable the winch first electric proportional pressure reducing valve 43 to be opened in proportion, correspondingly high control pressure is generated to drive the winch reversing valve 42 to be in a large opening at the lower position, the oil liquid of the small pump C2 is opened through the fourth one-way valve 51 through the P2 port, the third one-way valve 41 flows through the oil port H4 to the oil port H2 of the winch reversing valve 42, the bottom vehicle is accelerated, and the input flow is further amplified, so that the winch is pushed to lift and move at a high speed. And when the electric control remote rod of the telescopic action is still in the small opening stage, a low-electric current electric signal is output so that the amplitude-variable first electric proportional pressure reducing valve 33 generates low control pressure, and the telescopic reversing valve 22 is still in the small opening throttling state, although the input flow is increased, the telescopic action is not obviously promoted, and the speed of the telescopic action and the hoisting action is more balanced.
In this example, when the two action electric control tele rods are in the small opening stage, the throttle linkage control system is in a closed state, the bottom vehicle is in an idle state, the oil of the large pump C1 enters the multi-way valve through the port P1, part of the oil is introduced into the port X through the side pressure port, the oil flows through the filter element 12, the damping element 13 and the fixed difference reducing valve 14 to the winch first electric proportional reducing valve 43 and the rotating first electric proportional reducing valve 63, the winch is started to output a low-current signal by the small opening of the tele rod so that the winch first electric proportional reducing valve 43 is opened in proportion, the corresponding low-control pressure is generated to drive the winch reversing valve 42 to be in a lower small opening, the oil of the large pump C1 flows through the port H4 of the reversing valve 42 to the port H2 through the port P1, so as to push the winch to lift at a low speed, and meanwhile, the small opening of the gyration tele rod is opened in proportion to output the low-current signal so that the rotating first electric proportional reducing valve 63 is opened, the corresponding low-control pressure is generated to drive the winch control valve 62 to be in a lower small opening, and the small pump C2 flows through the port P2 to open the third one-way valve 41 to drive the oil to flow through the port I2 of the winch to the port I2; at this time, if the winch action needs to be accelerated, the electric control remote rod for winch starting is pushed to be in a large opening stage, the accelerator linkage control system is in an opening state, the bottom vehicle is in an accelerating state, the large opening of the remote rod outputs a high current signal to enable the winch first electric proportional pressure reducing valve 43 to be opened in proportion, correspondingly high control pressure is generated to drive the winch reversing valve 42 to be in a large opening at the lower position, the oil of the large pump C1 flows through the oil port H4 to the oil port H2 of the winch reversing valve 42 by opening the third one-way valve 41 through the P1 port, the bottom vehicle is accelerated, and the input flow is further amplified, so that the winch is pushed to lift and move at a high speed. When the rotary forward motion electric control remote rod is still in the small opening stage, a low electric current electric signal is output to enable the first electric proportional pressure reducing valve 63 to generate low control pressure, the rotary control valve 62 is still in the small opening throttling state, although the input flow is increased, the rotary forward motion is not obviously improved, and the rolling-up and rotary forward composite motion speeds are balanced.
In this example, different actions can define different accelerator opening states according to actual working conditions, the winch action requires working efficiency to open the accelerator linkage control system at a small angle of the remote rod, and the swing action requires stable working to open the accelerator linkage control system at a large angle of the remote rod.
The scheme integrates the electric proportional pressure reducing valve on the control unit of the multi-way valve to realize the proportional relation between the axial opening of the main valve and the input electric signal, thereby realizing the electric control throttling speed regulation control, having low cost and being beneficial to popularization and application; the throttle linkage control system is associated with a bottom car throttle, and the opening of the throttle linkage system is realized according to the opening state of the electric control remote rod, so that the throttle multi-way valve can stably run at a low speed with a small opening, and the throttle multi-way valve can continuously run at an accelerated speed with a large opening, so that the speed regulation interval is enlarged, and the working efficiency is improved; the combined flow type throttling speed regulating multi-way valve has anti-saturation property by means of double-pump oil inlet control respectively during the combination of winch or rotation and other action electric control at low speed, and the speed of the combined action is more balanced by means of the speed lifting difference after acceleration intervention of an accelerator during the combination at high speed.

Claims (10)

1. A current-combining type throttling speed-regulating multi-way valve is characterized in that: the device comprises a large pump oil inlet unit (1), a telescopic control unit (2), a variable amplitude control unit (3), a winch control unit (4), an oil return unit (5), a rotary control unit (6) and a small pump oil inlet unit (7) which are connected in parallel; the telescopic control unit (2), the amplitude variation control unit (3), the winch control unit (4) and the rotary control unit (6) comprise one-way valves, reversing valves, a first electric proportional pressure reducing valve and a second electric proportional pressure reducing valve;
the first working oil ports of the first electric proportional pressure reducing valve and the second electric proportional pressure reducing valve are connected with an oil tank, the second working oil ports of the first electric proportional pressure reducing valve and the second electric proportional pressure reducing valve are connected with an oil outlet of the large pump oil inlet unit (1), and the third working oil ports of the first electric proportional pressure reducing valve and the second electric proportional pressure reducing valve are connected with a pilot oil port of the reversing valve;
the first working oil port of the reversing valve is provided with a one-way valve, the one-way valve is connected with the oil inlet P1 or P2, the second working oil port of the reversing valve is connected with the oil inlet P1 or P2, the third working oil port of the reversing valve is connected with the oil return port T1 or T2, the fourth working oil port and the sixth working oil port of the reversing valve are used for being connected with a hydraulic actuator, and the fifth working oil port of the reversing valve is connected with the second working oil port or the oil return port of the reversing valve in the subsequent control unit.
2. The combined flow type throttling speed regulating multi-way valve according to claim 1, wherein: different current signals are applied to the first electric proportional pressure reducing valve and the second electric proportional pressure reducing valve to enable the first electric proportional pressure reducing valve and the second electric proportional pressure reducing valve to be opened in proportion, the axial opening of the reversing valve is controlled corresponding to the generated control pressure, and then the hydraulic executing element is pushed to act.
3. The combined flow type throttling speed regulating multi-way valve according to claim 1, wherein: the large pump oil inlet unit (1) comprises a filtering element (12), a damping element (13) and a constant-difference pressure reducing valve (14) which are arranged in series, wherein the input end of the filtering element (12) is connected with a pilot X-port, and the output end of the constant-difference pressure reducing valve (14) is connected with a second working oil port of the first electric proportional pressure reducing valve and the second electric proportional pressure reducing valve.
4. The combined flow type throttling speed regulating multi-way valve according to claim 1, wherein: an oil return back pressure valve (52) is arranged at the oil return port, and the input end of the oil return back pressure valve (52) is connected with oil return ports T1 and T2.
5. The combined flow type throttling speed regulating multi-way valve according to claim 1, wherein: a large-pump main overflow valve (11) is arranged between the oil inlet P1 and the oil return port T1, and a small-pump main overflow valve (71) is arranged between the oil inlet P2 and the oil return port T2.
6. An accelerator linkage control system is characterized in that: the combined flow type throttling speed regulation multiway valve comprising the electric proportional control of claim 1, wherein the throttle linkage control system is connected with a bottom car throttle.
7. The throttle coordinated control system according to claim 6, wherein: the throttle linkage system is opened according to the opening states of the electric control tele-rods in the telescopic tele-rod, the amplitude tele-rod, the winding tele-rod and the rotary tele-rod.
8. The throttle coordinated control system according to claim 7, wherein: when any one of the telescopic tele rod, the amplitude varying tele rod, the winding tele rod and the rotary tele rod is single-acting, the throttle linkage control system is in a closed state when the electric control tele rod is in a small opening stage, the bottom vehicle is in an idle state, the low-current electric signal drives the electric proportional pressure reducing valve to proportionally generate low control pressure, and the reversing valve is driven to axially small opening to realize low-speed action;
when the electronic control tele-lever is operated in a large opening stage, the accelerator linkage system is in an opening state, the bottom vehicle is in an accelerating state, the high-current electric signal drives the electric proportional pressure reducing valve to proportionally generate high control pressure, the reversing valve is driven to axially open, the bottom vehicle is accelerated, and the input flow is further amplified, so that high-speed operation is realized.
9. The throttle coordinated control system according to claim 7, wherein: when two of the telescopic tele rod, the amplitude varying tele rod, the winding tele rod and the rotary tele rod are double-acting, when the two acting electric control tele rods are in a small opening stage, the throttle linkage system control system is in a closed state, the bottom vehicle is in an idle state, the low-current electric signal is in a proportional mode through the electric proportional pressure reducing valve to generate low control pressure, the reversing valve is driven to axially form a small opening, and oil liquid of the large pump C1 and the small pump C2 is used for providing oil pressure for the control unit through oil inlet paths of the large pump and the small pump, so that low-speed compound action is realized.
10. The throttle coordinated control system according to claim 7, wherein: when two of the telescopic tele rod, the amplitude varying tele rod, the winding tele rod and the rotary tele rod are double-acting, when a certain action speed is slow, the action electric tele rod is continuously pushed to be in a large opening stage, the accelerator linkage control system is started, the bottom vehicle is in an acceleration state, the flow provided by the large pump C1 and the small pump C2 is improved, the high-current electric signal drives the electric proportional pressure reducing valve to generate high control pressure in proportion, the axial large opening of a certain action main valve is driven, the input flow is increased, and the action acceleration is realized;
and the other action is that the action electric control remote rod is still in a small opening stage, and the electric proportional pressure reducing valve is driven by the output low-current electric signal to generate low control pressure, so that the reversing valve is still in a small opening throttling state in the axial direction. Although the input flow is increased, the action acceleration state is weakened, so that the composite action speed is more balanced.
CN202310695722.2A 2023-06-12 2023-06-12 Flow-combining type throttle speed regulation multi-way valve and throttle linkage control system Pending CN116771744A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202310695722.2A CN116771744A (en) 2023-06-12 2023-06-12 Flow-combining type throttle speed regulation multi-way valve and throttle linkage control system

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202310695722.2A CN116771744A (en) 2023-06-12 2023-06-12 Flow-combining type throttle speed regulation multi-way valve and throttle linkage control system

Publications (1)

Publication Number Publication Date
CN116771744A true CN116771744A (en) 2023-09-19

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CN202310695722.2A Pending CN116771744A (en) 2023-06-12 2023-06-12 Flow-combining type throttle speed regulation multi-way valve and throttle linkage control system

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Country Link
CN (1) CN116771744A (en)

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