WO2023035794A1 - 一种旋转机具液压系统 - Google Patents

一种旋转机具液压系统 Download PDF

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Publication number
WO2023035794A1
WO2023035794A1 PCT/CN2022/107922 CN2022107922W WO2023035794A1 WO 2023035794 A1 WO2023035794 A1 WO 2023035794A1 CN 2022107922 W CN2022107922 W CN 2022107922W WO 2023035794 A1 WO2023035794 A1 WO 2023035794A1
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WIPO (PCT)
Prior art keywords
port
valve
oil
compensation
electromagnetic reversing
Prior art date
Application number
PCT/CN2022/107922
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English (en)
French (fr)
Inventor
金月峰
耿家文
袁泉
张箭
董玉忠
杜冬洋
张洋
孙本强
苗衡
卢杰
张新奎
Original Assignee
徐州徐工挖掘机械有限公司
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Application filed by 徐州徐工挖掘机械有限公司 filed Critical 徐州徐工挖掘机械有限公司
Priority to EP22866268.0A priority Critical patent/EP4368840A1/en
Priority to AU2022343587A priority patent/AU2022343587A1/en
Publication of WO2023035794A1 publication Critical patent/WO2023035794A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/042—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in"
    • 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
    • F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/08—Superstructures; Supports for superstructures
    • E02F9/10—Supports for movable superstructures mounted on travelling or walking gears or on other superstructures
    • E02F9/12—Slewing or traversing gears
    • E02F9/121—Turntables, i.e. structure rotatable about 360°
    • E02F9/123—Drives or control devices specially adapted therefor
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2221—Control of flow rate; Load sensing arrangements
    • E02F9/2225—Control of flow rate; Load sensing arrangements using pressure-compensating 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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/05—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive
    • 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
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30535—In combination with a pressure compensating valve the pressure compensating valve is arranged between pressure source and 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
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40507—Flow control characterised by the type of flow control means or valve with constant 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
    • F15B2211/405—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
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40553—Flow control characterised by the type of flow control means or valve with pressure compensating valves
    • F15B2211/40569—Flow control characterised by the type of flow control means or valve with pressure compensating valves the pressure compensating valve arranged downstream of the flow control means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—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
    • F15B2211/41554—Flow control characterised by the connections of the flow control means in the circuit being connected to a return line 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
    • F15B2211/41563—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and a return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—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
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5157—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and a return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5159—Pressure control characterised by the connections of the pressure control means in the circuit being connected to an output member and a return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7058—Rotary output members

Definitions

  • the invention relates to a hydraulic system of a rotary machine tool, belonging to the technical field of flow control of the excavator hydraulic system.
  • the rotating motor 4 in the prior art is controlled by the implement control valve 3-4 to control the action direction
  • the boom cylinder 5 is extended and retracted by the boom control valve 3-2
  • the main pump 2 is connected to the implement control at the same time.
  • the valve 3-4 and the boom control valve 3-2, the main pump 2 output hydraulic oil to supply the implement motor 4 and the boom cylinder 5 at the same time.
  • the swing motor 4 and the boom cylinder 5 share the same main pump 2, and adjusting the stroke of the boom cylinder 5 during the rotation of the swing motor 4 will cause the rotation speed of the swing motor 4 to drop rapidly, affecting the working efficiency.
  • the technical problem to be solved by the present invention is to overcome the defects of the prior art and provide a hydraulic system for rotary implements, the speed of the rotary motor and implements is independently controlled without being affected by other actions such as boom sticks.
  • the present invention provides a hydraulic system for rotary implements, including a fuel tank, a main pump, a control valve and a rotary motor, the fuel tank is connected to the oil suction port of the main pump, the oil outlet of the main pump is connected to the P port of the control valve, and the control valve
  • the T port of the control valve is connected to the oil tank, and the A port of the control valve and the B port of the control valve are connected to both ends of the rotary motor.
  • the control valve includes a compensation valve, an electric proportional valve and an electromagnetic reversing valve
  • the P port is connected to the first port of the electric proportional valve
  • the P port is connected to the third port of the compensation valve
  • the P port is connected to the fifth port of the compensation valve
  • the electric Port 2 of the proportional valve is connected to port 1 of the compensation valve
  • port 2 of the compensation valve is connected to port 3 of the electromagnetic reversing valve
  • port 2 of the compensation valve is connected to port T
  • port 4 of the compensation valve is connected to port T
  • the oil port four of the electromagnetic reversing valve is connected with the T port
  • the oil port two of the electromagnetic reversing valve is connected with the B port.
  • control valve includes a relief valve
  • the P port is connected to the first port of the relief valve
  • the second port of the relief valve is connected to the T port.
  • control valve includes a relief valve at the first port, port four of the solenoid reversing valve is connected to port one of the relief valve at the first port, port two of the relief valve at the first port is connected to port A, and the relief valve at the first port is connected to port A.
  • the oil port 2 of the flow valve is connected with the oil port 1 of the electromagnetic reversing valve.
  • control valve includes a second port relief valve
  • the oil port two of the solenoid reversing valve is connected to the second port relief valve port one
  • the second port relief valve oil port two is connected to the T port
  • the second port relief valve port two is connected to the T port.
  • Flow valve oil port one is connected to port B.
  • the electromagnetic reversing valve is a three-position four-way electromagnetic reversing valve.
  • the left position of the three-position four-way electromagnetic reversing valve is oil port one connected to oil port three and oil port two connected to oil port four.
  • the right position of the reversing valve is oil port one connected to oil port four and oil port two connected to oil port three.
  • a throttle valve is included, and the oil outlet port 2 of the compensation valve is connected to the T port through the throttle valve.
  • the invention controls the rotary motor independently, realizes the forward and reverse control of the rotary motor by switching the left position and the right position of the electromagnetic reversing valve, realizes switching the oil circuit of the rotary motor through the electric proportional valve and the compensation valve, and realizes the rotation process of the rotary motor
  • the rotation speed of the rotating motor will not be affected, which improves the working efficiency of the whole machine;
  • the hydraulic oil output by the main pump is discharged to the hydraulic oil tank through the overflow valve 7.
  • the electromagnetic reversing valve When the rotary motor rotates clockwise, if the electromagnetic reversing valve is powered off, the electromagnetic reversing The valve works in the neutral position, the main pump and the rotary motor oil circuit are disconnected, the hydraulic oil tank and the rotary motor oil circuit are disconnected, the rotary motor continues to rotate clockwise under the action of inertia, the pressure in the A to C pipeline decreases, and the D to B The pressure in the pipeline rises.
  • the first port relief valve absorbs oil from the hydraulic oil tank to replenish the pipeline from A to C to prevent it from being sucked.
  • the second port relief valve releases the high-pressure oil from D to B to in the hydraulic tank to prevent system overloading.
  • the first port relief valve will release the high-pressure oil in the pipeline from A to C to the hydraulic oil tank , to prevent the system from overloading, the second port overflow valve absorbs oil from the hydraulic oil tank and replenishes it into the D to B pipeline to prevent it from being sucked, and prevents all hydraulic oil in the oil circuit from flowing into the oil tank, ensuring the smooth operation of the entire oil circuit .
  • Fig. 1 is an oil circuit diagram of the present invention
  • Fig. 2 is an oil circuit diagram of a rotary motor and a boom oil cylinder in the prior art.
  • first”, “second”, etc. are involved in the present invention, they are only used for descriptive purposes, and cannot be understood as indicating or implying their relative importance or implicitly indicating the indicated technical features. quantity. Thus, the features defined as “first” and “second” may explicitly or implicitly include at least one of these features.
  • the technical solutions of the various embodiments can be combined with each other, but it must be based on the realization of those skilled in the art. When the combination of technical solutions is contradictory or cannot be realized, it should be considered that the combination of technical solutions does not exist , nor within the scope of protection required by the present invention.
  • the hydraulic system and control valve of the new excavator rotary implement are mainly composed of a hydraulic oil tank 1, a main pump 2, a control valve 3, a rotary motor 4, and a boom cylinder 5, wherein the control valve 3 is composed of 31 compensation valve, 32 electric proportional valve, 33 First port relief valve, 34 second port relief valve, 35 electromagnetic reversing valve, 36 throttle valve and 37 relief valve.
  • the oil suction port F of the main pump 2 is connected to the oil tank 1, the oil outlet E of the main pump 2 is connected to the P port of the control valve 3, the P port is connected to the first port of the relief valve 37, and the second port of the relief valve 37 is connected to the T port , T port is connected with hydraulic oil tank 1, P port is connected with electric proportional valve 32 oil port one, P port of control valve 3 is connected with compensation valve 31 oil port three, P port is connected with compensation valve 31 oil port five, electric proportional valve 32 oil port 2 is connected with compensation valve 31 oil port 1, electric proportional valve 32 oil port 2 is connected with compensation valve 31 oil port 1, compensation valve 31 oil outlet 2 is connected with throttle valve 36 oil inlet, compensation valve 31 is output
  • the second oil port is connected to the third oil port of the electromagnetic reversing valve 35, the oil outlet of the throttle valve 36 is connected to the T port, the oil outlet 4 of the compensation valve 31 is connected to the T port, and the fourth oil port of the electromagnetic reversing valve 35 is connected to the T port , the electromagnetic
  • the engine drives the main pump 2 to work.
  • the main pump 2 outputs hydraulic oil and enters the P port of the control valve 3.
  • the hydraulic oil connects the hydraulic oil output by the main pump 2 to the hydraulic oil tank 1 through the compensation valve 31;
  • the electromagnet on the left side or the right side of the electromagnetic reversing valve 35 and the electro-proportional valve 32 are energized, and the current of the electro-proportional valve 32 can be adjusted and controlled according to the speed requirement, so as to realize the internal operation of the electro-proportional valve 32.
  • the main pump 2 When the load of the rotary motor 4 is too large to rotate, the main pump 2 outputs hydraulic oil to the hydraulic oil tank 1 through the overflow valve 37.
  • the rotary motor 4 rotates clockwise, if the electromagnetic reversing valve 35 is powered off, The electromagnetic reversing valve 35 works in the neutral position, the main pump 2 and the rotary motor 4 oil circuit are disconnected, the hydraulic oil tank 1 and the rotary motor 4 oil circuit are disconnected, and the rotary motor 4 continues to rotate clockwise under the action of inertia, A to C
  • the pressure in the pipeline decreases, and the pressure in the pipeline from D to B increases.
  • the first port overflow valve 33 absorbs oil from the hydraulic oil tank 1 to supplement the pipeline from A to C to prevent it from being sucked, and the second port overflows Valve 34 releases high pressure oil from D to B to hydraulic oil tank 1 to prevent system overload.
  • the device of the present invention adds a control valve, which can adjust the flow into the motor of the implement, and realizes the independent control of the motor speed of the implement.
  • the speed of the rotating motor is not affected by other actions such as the boom stick, and the rotating speed can be adjusted in real time according to the requirements of the working conditions; the invention has a simple and reliable structure, good versatility, and is suitable for industrialization and application.
  • Hydraulic oil tank 1 main pump 2, swing motor 4, boom cylinder 5, compensation valve 31, 32 electric proportional valve, first port relief valve 33, second port relief valve 34, electromagnetic reversing valve 35, throttling
  • the valve 36 and overflow valve 37 are available in many models in the prior art, and those skilled in the art can select appropriate models according to actual needs, and this embodiment will not give examples one by one.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Operation Control Of Excavators (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

一种旋转机具液压系统,包括油箱、主泵、控制阀和旋转马达，油箱连接主泵的吸油口，主泵的出油口连接控制阀的P口，控制阀的T口连通油箱，控制阀的A口和控制阀的B口连接旋转马达两端。控制阀包括补偿阀、电比例阀和电磁换向阀，P口与电比例阀油口一相连，P口与补偿阀油口三相连，P口与补偿阀油口五相连，电比例阀油口二与补偿阀油口一相连，补偿阀出油口二与电磁换向阀油口三相连，补偿阀出油口二连接T口，补偿阀出油口四与T口相连，电磁换向阀油口四与T口相连，电磁换向阀油口二与B口相连。本装置增加控制阀，可调节进入机具马达的流量，实现对机具马达速度的单独控制。

Description

一种旋转机具液压系统 技术领域
本发明涉及一种旋转机具液压系统，属于挖掘机液压系统流量控制技术领域。
背景技术
随着挖掘机属具的不断创新，越来越多的属具可安装到挖掘机上进行多元化作业，实现一机多能，替代人工作业，加快作业效率。但是目前属具都是采用挖掘机原系统上的泵进行供油，在属具和挖掘机动臂斗杆等动作复合作业时，会降低属具及挖掘机动臂斗杆等动作速度，降低作业效率。
如图2所示，现有技术中的旋转马达4由机具控制阀3-4控制动作方向，动臂油缸5由动臂控制阀3-2控制油缸伸出收回，主泵2同时连接机具控制阀3-4和动臂控制阀3-2，主泵2输出液压油同时供给机具马达4和动臂油缸5。旋转马达4与动臂油缸5共用一个主泵2，旋转马达4旋转过程中调整动臂油缸5行程会引起旋转马达4旋转速度迅速下降，影响作业效率。
发明内容
本发明所要解决的技术问题是克服现有技术的缺陷，提供一种旋转机具液压系统，旋转马达机具速度不受动臂斗杆等其他动作影响，单独控制。
为达到上述目的，本发明提供一种旋转机具液压系统，包括油箱、主泵、控制阀和旋转马达，油箱连接主泵的吸油口，主泵的出油口连接控制阀的P口，控制阀的T口连通油箱，控制阀的A口和控制阀的B口连接旋转马达两端。
优先地，控制阀包括补偿阀、电比例阀和电磁换向阀，P口与电比例阀油口一相连，P口与补偿阀油口三相连，P口与补偿阀油口五相连，电比例阀油口二与补偿阀油口一相连，补偿阀出油口二与电磁换向阀油口三相连，补偿阀出油口二连接T口，补偿阀出油口四与T口相连，电磁换向阀油口四与T口相连，电磁换向阀油口二与B口相连。
优先地，控制阀包括溢流阀，P口连接溢流阀油口一，溢流阀油口二连接到T口。
优先地，控制阀包括第一端口溢流阀，电磁换向阀油口四与第一端口溢流阀油口一相连，第一端口溢流阀油口二与A口相连，第一端口溢流阀油口二与电磁换向阀油口一相 连。
优先地，控制阀包括第二端口溢流阀，电磁换向阀油口二与第二端口溢流阀油口一相连，第二端口溢流阀油口二与T口相连，第二端口溢流阀油口一连通B口。
优先地，电磁换向阀为三位四通电磁换向阀，三位四通电磁换向阀的左位为油口一连通油口三且油口二连通油口四，三位四通电磁换向阀右位为油口一连通油口四且油口二连通油口三。
优先地，包括节流阀，补偿阀出油口二通过节流阀连接T口。
本发明所达到的有益效果：
本发明对旋转马达单独控制，通过电磁换向阀左位和右位的切换实现旋转马达正反转控制，通过电比例阀和补偿阀实现开关旋转马达的油路，实现了在旋转马达旋转过程中做动臂斗杆等其它动作，旋转马达旋转速度不受影响，提高了整机工作效率；
本发明当旋转马达所带负载过大，不能转动时，主泵输出液压油经过溢流阀7泄荷到液压油箱，当旋转马达顺时针转动时，如果电磁换向阀断电，电磁换向阀中位工作，主泵和旋转马达油路断开，液压油箱和旋转马达油路断开，旋转马达在惯性的作用下，继续顺时针旋转，A到C管路中压力降低，D到B管路中压力升高，此时第一端口溢流阀中从液压油箱吸油补充到A到C管路中，防止其吸空，第二端口溢流阀将D到B中高压油泄荷到液压油箱中，防止系统超载.
当旋转马达逆时针转动时，如果电磁换向阀断电，电磁换向阀中位工作，主泵和旋转马达油路断开，液压油箱和旋转马达油路断开，旋转马达在惯性的作用下，继续逆时针旋转，A到C管路中压力升高，D到B管路中压力降低，此时第一端口溢流阀中从将A到C管路中高压油泄荷到液压油箱，防止系统超载，第二端口溢流阀从液压油箱中吸油补充到D到B管路中，防止其吸空，避免油路中液压油全部流入油箱中，保障了整个油路工作时的流畅。
附图说明
图1是本发明的油路图；
图2是现有技术中旋转马达与动臂油缸的油路图。
附图标记含义，1、油箱；2、主泵；3、控制阀；4、旋转马达；31、补偿阀；32、电比例阀；33、第一端口溢流阀；34、第二端口溢流阀；35、电磁换向阀；36、节流阀；37、溢流阀；3-1、第一单向阀；3-2、动臂换向阀；3-3、第二单向阀；3-4、旋转马达换向阀；3-5、 第一补油阀；3-6、第一溢流阀；3-7、第二单向阀；3-8、第二溢流阀。
具体实施方式
以下实施例仅用于更加清楚地说明本发明的技术方案，而不能以此来限制本发明的保护范围。
需要说明，若本发明实施例中有方向性指示(诸如上、下、左、右、前、后......)，则其仅用于解释在某一特定姿态下各部件之间的相对位置关系、运动情况等，如果该特定姿态发生改变时，则该方向性指示也相应地随之改变。
另外，若在本发明中涉及“第一”、“第二”等的描述，则其仅用于描述目的，而不能理解为指示或暗示其相对重要性或者隐含指明所指示的技术特征的数量。由此，限定有“第一”、“第二”的特征可以明示或者隐含地包括至少一个该特征。另外，各个实施例之间的技术方案可以相互结合，但是必须是以本领域普通技术人员能够实现为基础，当技术方案的结合出现相互矛盾或无法实现时应当认为这种技术方案的结合不存在，也不在本发明要求的保护范围之内。
该新型挖掘机旋转机具液压系统及控制阀主要由液压油箱1、主泵2、控制阀3、旋转马达4、动臂油缸5构成，其中控制阀3由31补偿阀、32电比例阀、33第一端口溢流阀、34第二端口溢流阀、35电磁换向阀、36节流阀和37溢流阀构成。
主泵2吸油口F与油箱1相连，主泵2出油口E与控制阀3的P口相连，P口连接到37溢流阀油口一，溢流阀37油口二连接到T口，T口与液压油箱1相连，P口与电比例阀32油口一相连，控制阀3的P口与补偿阀31油口三相连，P口与补偿阀31油口五相连，电比例阀32油口二与补偿阀31油口一相连，电比例阀32油口二与补偿阀31油口一相连，补偿阀31出油口二与节流阀36进油口相连，补偿阀31出油口二与电磁换向阀35油口三相连，节流阀36出油口与T口相连，补偿阀31出油口4与T口相连，电磁换向阀35油口四与T口相连，电磁换向阀35油口四与第一端口溢流阀33油口一相连，第一端口溢流阀33油口二与A口相连，第一端口溢流阀33油口二同时与电磁换向阀35油口一相连，电磁换向阀35油口二与B口相连，电磁换向阀35油口二与第二端口溢流阀34油口一相连，第二端口溢流阀34油口二与T口相连，第二端口溢流阀34油口一连通B口，A口与旋转马达4的C口相连，B口与旋转马达4的D口相连。
如此构成的本发明中，工作原理如下：
挖掘机启动后，发动机带动主泵2工作，主泵2输出液压油，进入控制阀3的P口，在不需要旋转马达4工作时候，电比例阀32不得电的情况下，其内部油路断开，液压油通过补偿阀31将主泵2输出的液压油接通到液压油箱1内；
当需要旋转马达4工作时候，电磁换向阀35左侧电磁铁或者右侧电磁铁以及电比例阀32得电，可根据速度需求，调整控制电比例阀32的电流，实现电比例阀32内部油路开口面积的大小，主泵2输出液压油，经过电比例阀32内部油路，再经过补偿阀31内部油路，再经过电磁换向阀35内部油路，进入旋转马达4，驱动旋转马达4转动；
当电磁换向阀35左侧电磁铁得电时，电磁换向阀35左位工作，主泵2输出液压油经过电磁换向阀35左位，经过A口C口进入旋转马达4，旋转马达4顺时针转动；当电磁换向阀35右侧电磁铁得电时，电磁换向阀35右位工作，主泵2输出液压油经过电磁换向阀35右位，经过B口D口进入旋转马达4，旋转马达4逆时针转动；
当旋转马达4所带负载过大，不能转动时，主泵2输出液压油经过溢流阀37泄荷到液压油箱1，当旋转马达4顺时针转动时，如果电磁换向阀35断电，电磁换向阀35中位工作，主泵2和旋转马达4油路断开，液压油箱1和旋转马达4油路断开，旋转马达4在惯性的作用下，继续顺时针旋转，A到C管路中压力降低，D到B管路中压力升高，此时第一端口溢流阀33中从液压油箱1吸油补充到A到C管路中，防止其吸空，第二端口溢流阀34将D到B中高压油泄荷到液压油箱1中，防止系统超载.
当旋转马达4逆时针转动时，如果电磁换向阀35断电，电磁换向阀35中位工作，主泵2和旋转马达4油路断开，液压油箱1和旋转马达4油路断开，旋转马达4在惯性的作用下，继续逆时针旋转，A到C管路中压力升高，D到B管路中压力降低，此时第一端口溢流阀33中从将A到C管路中高压油泄荷到液压油箱1，防止系统超载，第二端口溢流阀34从液压油箱1中吸油补充到D到B管路中，防止其吸空。
本发明装置增加控制阀，可调节进入机具马达的流量，实现对机具马达速度的单独控制。旋转马达机具速度不受动臂斗杆等其他动作影响，可根据工况需求实时调整旋转速度；本发明结构简单可靠、通用性好，适合产业化推广应用。
液压油箱1、主泵2、旋转马达4、动臂油缸5、补偿阀31、32电比例阀、第一端口溢流阀33、第二端口溢流阀34、电磁换向阀35、节流阀36和溢流阀37上述部件在现有技术中可采用的型号很多，本领域技术人员可根据实际需求选用合适的型号，本实施例不 再一一举例。
以上所述仅是本发明的优选实施方式，应当指出，对于本技术领域的普通技术人员来说，在不脱离本发明技术原理的前提下，还可以做出若干改进和变形，这些改进和变形也应视为本发明的保护范围。

Claims (7)

  1. 一种旋转机具液压系统，其特征在于，包括油箱(1)、主泵(2)、控制阀(3)和旋转马达(4)，油箱(1)连接主泵(2)的吸油口，主泵(2)的出油口连接控制阀(3)的P口，控制阀(3)的T口连通油箱(1)，控制阀(3)的A口和控制阀(3)的B口连接旋转马达(4)两端。
  2. 根据权利要求1所述的一种旋转机具液压系统，其特征在于，控制阀(3)包括补偿阀(31)、电比例阀(32)和电磁换向阀(35)，P口与电比例阀(32)油口一相连，P口与补偿阀(31)油口三相连，P口与补偿阀(31)油口五相连，电比例阀(32)油口二与补偿阀(31)油口一相连，补偿阀(31)出油口二与电磁换向阀(35)油口三相连，补偿阀(31)出油口二连接T口，补偿阀(31)出油口四与T口相连，电磁换向阀(35)油口四与T口相连，电磁换向阀(35)油口二与B口相连。
  3. 根据权利要求1所述的一种旋转机具液压系统，其特征在于，控制阀(3)包括溢流阀(37)，P口连接溢流阀(37)油口一，溢流阀(37)油口二连接到T口。
  4. 根据权利要求2所述的一种旋转机具液压系统，其特征在于，控制阀(3)包括第一端口溢流阀(33)，电磁换向阀(35)油口四与第一端口溢流阀(33)油口一相连，第一端口溢流阀(33)油口二与A口相连，第一端口溢流阀(33)油口二与电磁换向阀(35)油口一相连。
  5. 根据权利要求2所述的一种旋转机具液压系统，其特征在于，控制阀(3)包括第二端口溢流阀(34)，电磁换向阀(35)油口二与第二端口溢流阀(34)油口一相连，第二端口溢流阀(34)油口二与T口相连，第二端口溢流阀(34)油口一连通B口。
  6. 根据权利要求2所述的一种旋转机具液压系统，其特征在于，电磁换向阀(35)为三位四通电磁换向阀，三位四通电磁换向阀的左位为油口一连通油口三且油口二连通油口四，三位四通电磁换向阀右位为油口一连通油口四且油口二连通油口三。
  7. 根据权利要求2所述的一种旋转机具液压系统，其特征在于，包括节流阀(36)，补偿阀(31)出油口二通过节流阀(36)连接T口。
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