WO2024045445A1 - 一种多路阀、液压系统及挖掘机 - Google Patents

一种多路阀、液压系统及挖掘机 Download PDF

Info

Publication number
WO2024045445A1
WO2024045445A1 PCT/CN2022/142657 CN2022142657W WO2024045445A1 WO 2024045445 A1 WO2024045445 A1 WO 2024045445A1 CN 2022142657 W CN2022142657 W CN 2022142657W WO 2024045445 A1 WO2024045445 A1 WO 2024045445A1
Authority
WO
WIPO (PCT)
Prior art keywords
oil
valve
port
working
boom
Prior art date
Application number
PCT/CN2022/142657
Other languages
English (en)
French (fr)
Inventor
黄飞
肖刚
崔骁
徐艳翠
刘少龙
Original Assignee
江苏汇智高端工程机械创新中心有限公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 江苏汇智高端工程机械创新中心有限公司 filed Critical 江苏汇智高端工程机械创新中心有限公司
Priority to AU2022436043A priority Critical patent/AU2022436043A1/en
Publication of WO2024045445A1 publication Critical patent/WO2024045445A1/zh

Links

Images

Classifications

    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2264—Arrangements or adaptations of elements for hydraulic drives
    • E02F9/2267—Valves or distributors
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F3/00—Dredgers; Soil-shifting machines
    • E02F3/04—Dredgers; Soil-shifting machines mechanically-driven
    • E02F3/28—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F3/00—Dredgers; Soil-shifting machines
    • E02F3/04—Dredgers; Soil-shifting machines mechanically-driven
    • E02F3/28—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets
    • E02F3/36—Component parts
    • E02F3/42—Drives for dippers, buckets, dipper-arms or bucket-arms
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F3/00—Dredgers; Soil-shifting machines
    • E02F3/04—Dredgers; Soil-shifting machines mechanically-driven
    • E02F3/28—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets
    • E02F3/36—Component parts
    • E02F3/42—Drives for dippers, buckets, dipper-arms or bucket-arms
    • E02F3/425—Drive systems for dipper-arms, backhoes or the like
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F3/00—Dredgers; Soil-shifting machines
    • E02F3/04—Dredgers; Soil-shifting machines mechanically-driven
    • E02F3/28—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets
    • E02F3/36—Component parts
    • E02F3/42—Drives for dippers, buckets, dipper-arms or bucket-arms
    • E02F3/43—Control of dipper or bucket position; Control of sequence of drive operations
    • E02F3/435—Control of dipper or bucket position; Control of sequence of drive operations for dipper-arms, backhoes or the like
    • 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
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2217—Hydraulic or pneumatic drives with energy recovery arrangements, e.g. using accumulators, flywheels
    • 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
    • E02F9/2278—Hydraulic circuits
    • E02F9/2289—Closed circuit

Definitions

  • the invention belongs to the technical field of engineering machinery, and particularly relates to a multi-way valve, a hydraulic system and an excavator.
  • the boom regeneration structure is the internal regeneration of the valve core, which cannot realize the return oil flow of the boom for other actuators, resulting in large energy loss; 2.
  • the bypass and main oil port oil lines are fixed on a valve core for adjustment, which will cause great impact to the whole machine.
  • the main features of the second plan 1.
  • the boom regeneration valve core is used to realize the utilization of the oil return flow when the boom is lowered during the compound action. However, when the boom return oil flow passes through the first boom valve core, the pressure loss is due to the sharply smaller flow channel area.
  • the bypass electronic control is independently adjusted, but it is not a two-way design principle. It is easy to suppress the pressure during startup or due to the connection in the early stage of startup.
  • the oil return area of the oil tank is too large, causing the main pump pressure to be too low to provide a pilot oil source;
  • the arm circuit is complex, and multiple components such as arm cut-off valve, arm regeneration valve and load holding valve are used to realize the basic functions of the arm. , causing the main valve to increase in size and cost, or the multi-way valve does not have the crushing function due to volume requirements; 4.
  • the large cavity of the bucket rod does not have a load-holding valve structure and principle.
  • the existing technology has the following shortcomings: 1.
  • the boom cannot regenerate flow to other actuators or the regeneration amount is very small; 2.
  • the bypass of the current solution cannot be independently adjusted, or the bypass can be independently adjusted but there is pressure suppression at startup, or during the startup phase Due to the large oil return area of the connected oil tank, the main pump pressure is too low to provide a pilot oil source; 3.
  • the principle of the fully electronically controlled multi-way valve arm circuit is complex, and the arm cut-off valve, arm regeneration valve and load holding valve are used. Multiple components such as the bucket rod compound priority and low back pressure oil return function will cause the main valve to increase in size and cost, or it may not have the crushing function due to the volume requirements of the control multi-way valve.
  • the large cavity of the bucket rod does not have a load holding valve, which leads to the risk of the bucket rod falling during hoisting operations.
  • the present invention provides a multi-way valve, a hydraulic system and an excavator.
  • a new excavator multi-way valve principle and configuration is proposed.
  • a multi-way valve which includes a first working link, a second working link, and a third working link; a first main oil inlet, a second main oil inlet, and a main oil return port; and also includes: The first upper vehicle oil supply oil path is connected to the first main oil inlet, the second upper vehicle oil supply oil path is connected to the second main oil inlet, the oil return oil path is connected to the main oil return port, and the first middle oil supply oil path is connected to the second main oil inlet.
  • a position oil supply channel and a second center oil supply channel; the second working link is arranged between the first working link and the third working link;
  • the first working link includes a travel valve group and a rotary valve group; wherein the travel valve group includes a linear travel valve, a left travel valve, and a right travel valve; the rotary valve group includes a rotary valve used to control a rotary hydraulic cylinder;
  • the second working unit includes a boom valve group for controlling the boom hydraulic cylinder and a bucket valve group for controlling the bucket hydraulic cylinder; wherein the boom valve group includes a first boom valve, a second boom valve, and a bucket valve group. arm valve, third boom valve, boom first load holding valve, boom second load holding valve; the bucket valve group includes a bucket valve;
  • the third working link includes a stick valve group for controlling the stick hydraulic cylinder and a backup valve group for controlling the standby hydraulic cylinder; wherein the stick valve group includes a first stick valve, a second stick valve, and a second stick valve group. oil valve, second arm oil return valve, arm small cavity load holding valve, arm large cavity load maintaining valve; the backup valve group includes a backup valve;
  • the first line of the first main oil inlet unidirectionally supplies oil to the first boom valve, bucket valve, second stick oil return valve, and backup valve through the first oil supply line;
  • the first path of the second main oil inlet passes through the right travel valve.
  • the center oil inlet and center oil outlet of the right travel valve are connected, it passes through the rotary valve, the second boom valve, and the first stick valve in sequence.
  • the center oil inlet and outlet form a second center oil supply channel, and at the same time, the center oil outlet of the right travel valve flows unidirectionally to the second upper vehicle oil supply channel; among them, the rotary valve, the second boom valve , the center oil inlet and center oil outlet of the first stick valve are in a normally open state;
  • the second path of one of the first main oil inlet or the second main oil inlet is connected to the left travel valve through the linear travel valve.
  • the center oil inlet and the center oil outlet of the left travel valve are connected, they pass through in turn.
  • the center inlet and outlet ports of the first boom valve, bucket valve, second arm oil return valve, and backup valve form the first center oil supply channel.
  • the center oil outlet of the left travel valve The oil supply line flows to the first upper vehicle; among them, the center oil inlet and center oil outlet of the first boom valve, bucket valve, second stick oil return valve, and backup valve are in a normally open state;
  • the second path of the first main oil inlet or the second main oil inlet passes through the linear traveling valve and then supplies the one-way supply to the rotary valve, the second boom valve, and the first stick valve through the second upper oil supply oil path. Oil.
  • the multi-way valve further includes a first bypass valve, the end of the first intermediate oil supply channel is connected to the oil inlet of the first bypass valve, and the The oil outlet is connected to the oil return passage;
  • the multi-way valve also includes a second bypass valve.
  • the end of the second neutral oil supply channel is connected to the oil inlet of the second bypass valve, and the oil outlet of the second bypass valve is connected to the oil return port. Oil passage;
  • the first bypass valve and the second bypass valve are both four-position two-way valves with the same structure.
  • the oil inlet and the oil outlet are connected through the first damping hole; when in the second working position, When in the working position, the oil inlet and the oil outlet are not connected; when in the third working position, the oil inlet and the oil outlet are connected through the second damping hole; when in the fourth working position, the oil inlet and the oil outlet are connected.
  • the oil outlet is directly connected.
  • the first working link further includes a relief valve connected to the main oil return port, and the first main oil inlet is connected to the oil inlet of the relief valve through a first relief check valve. port; the second main oil inlet is connected to the oil inlet of the relief valve through the second relief check valve.
  • the linear travel valve is a three-position four-way valve, including a first oil inlet, a second oil inlet, a first working oil port, and a second working oil port.
  • the first oil inlet and The first main oil inlet is connected, the second oil inlet is connected with the second main oil inlet, the first working oil port is connected to the left travel working oil circuit, the left travel working oil circuit supplies oil to the left travel valve, the second working oil
  • the oil port supplies oil to the second oil supply line in one direction;
  • the linear travel valve has three working positions:
  • the first oil inlet is connected to the first working oil port, and the second oil inlet is connected to the second working oil port;
  • the first oil inlet is connected to the second working oil port through the third orifice.
  • the first oil inlet is connected to the second working oil port through the one-way valve and the second orifice.
  • the oil inlet is circulated, and the second oil inlet is connected to the first working oil port.
  • the left travel valve is a three-position six-way valve.
  • the center oil inlet of the left travel valve is connected to the center oil outlet, and the first main oil inlet passes through the left travel valve.
  • the working oil flows to the first center oil supply channel through the left travel valve.
  • the center oil outlet of the left travel valve flows unidirectionally to the first upper oil supply channel.
  • the two left travel oil ports pass through the left travel valve.
  • the oil return port is connected to the oil return line; when the left travel valve is in the left and right working positions, the center oil inlet and center oil outlet of the left travel valve are not connected, and the hydraulic oil passes through the left travel valve to achieve a Two oil ports for the left travel feed oil, and the other oil port returns oil, thereby realizing the forward and reverse rotation of the left travel motor;
  • the right travel valve is a three-position six-way valve.
  • the center oil inlet of the right travel valve is connected to the center oil outlet, and the first main oil inlet passes through the right travel valve.
  • the working oil flows to the second center oil supply channel through the right travel valve.
  • the center oil outlet of the right travel valve flows unidirectionally to the second upper oil supply channel.
  • the two oil ports of the right travel valve pass through the right travel valve.
  • the oil return port is connected to the oil return line; when the right travel valve is in the left and right working positions, the center oil inlet and center oil outlet of the right travel valve are not connected, and the hydraulic oil passes through the right travel valve to achieve a Two oil ports of the right traveling motor feed oil, and the other oil port returns oil, thereby realizing the forward and reverse rotation of the right traveling motor.
  • the rotary valve is a three-position six-way valve with a neutral position and two working positions.
  • the oil supply circuit of the second upper vehicle does not supply oil to the rotary hydraulic cylinder; when the rotary valve is in two working positions, the center oil inlet and the center oil outlet of the rotary valve are connected, and at the same time, the second upper vehicle oil supply line does not supply oil to the rotary hydraulic cylinder.
  • the oil supply line of the vehicle supplies oil to one of the two oil ports of the rotary hydraulic cylinder through the rotary valve, and the other oil port is connected to the return oil line through the rotary valve.
  • the first boom valve is a three-position six-way valve with a neutral position and two working positions.
  • the first boom valve When the first boom valve is in the neutral position, only the neutral position of the first boom valve is The oil inlet and the center oil outlet are connected, the first center oil supply channel is connected, and the first upper oil supply channel does not supply oil to the boom hydraulic cylinder; when the first boom valve is located between the two working When in position, the first upper vehicle oil supply circuit supplies oil to one of the two oil ports of the boom hydraulic cylinder through the first boom oil inlet cut-off valve, the first boom valve, and the boom load holding valve respectively.
  • the oil port is connected to the oil return circuit through the first boom valve; the oil inlet of the first boom valve is connected to the first oil supply circuit through the first boom oil inlet cut-off valve, and the first boom valve returns The oil port is connected to the oil return line; the first working oil port is connected to the large cavity oil port of the boom through the boom load holding valve, the second working oil port is connected to the small cavity oil port of the boom, and the middle oil outlet is connected to Center oil inlet of bucket valve;
  • the second boom valve is a three-position six-way valve.
  • the oil inlet is connected to the second oil supply line through the second boom oil inlet check valve.
  • the oil return port is connected to the oil return channel.
  • the middle oil inlet is Connected to the center oil outlet of the rotary valve; the first working oil port is connected to the large cavity oil port of the boom through the load holding valve; the second working oil port is connected to the large cavity oil port of the boom through the load holding valve; the center outlet
  • the oil port is connected to the center oil inlet of the third boom valve; the second boom valve has a center position and two working positions; when the second boom valve is in the center position, only the center oil inlet flows to the center position.
  • the third boom valve is a two-position six-way valve.
  • the oil return port flows unidirectionally to the second upper oil supply circuit through the regeneration check valve.
  • the first working oil port is connected to the boom large cavity oil port through the load holding valve. ;
  • the third boom valve When the third boom valve is in the right working position, only the center oil inlet flows to the center oil outlet; when the third boom valve is in the left working position, the working oil port flows in the direction of the return port. , the oil port of the large cavity of the boom regenerates oil to the second upper oil supply circuit;
  • boom large cavity regeneration oil circuit including the boom large cavity oil replenishment check valve; when the boom rises, the boom large cavity oil port regenerates oil from the oil return channel through the boom large cavity oil replenishment check valve. , to prevent the boom from being sucked out;
  • It also includes a regeneration oil circuit for the small cavity of the boom, including a check valve for oil replenishment in the small cavity of the boom.
  • a regeneration oil circuit for the small cavity of the boom including a check valve for oil replenishment in the small cavity of the boom.
  • the bucket valve is a four-position six-way valve
  • the oil inlet is connected to the first oil supply oil circuit through the bucket oil inlet check valve
  • the oil return port is connected to the return oil circuit
  • Two working oil ports are connected to the bucket hydraulic cylinder oil port; it has one neutral position and three working positions;
  • the first oil supply circuit When the bucket valve is in the neutral position, the first oil supply circuit does not supply oil to the bucket hydraulic cylinder; when the bucket valve is in the three working positions, the first oil supply circuit passes through the bucket
  • the cavity oil port or bucket small cavity oil port supplies oil to one cavity of the bucket valve, and the hydraulic oil in the corresponding other cavity leaks through the bucket small cavity oil port or bucket large cavity oil port and then passes through the bucket.
  • the valve returns oil to the oil return line; the bucket valve works in the second working position at the left end, and the oil return to the small cavity oil port of the bucket is damped to prevent the bucket from being empty; when the bucket is retracted for excavation operation; the bucket valve When working at the first working position at the left end, there is no damping for the oil return to the small cavity oil port of the bucket, which reduces the oil return back pressure during excavation operations.
  • the first stick valve is a three-position six-way valve with a neutral position and two working positions.
  • the first stick valve When the first stick valve is in the neutral position, there is only a second neutral oil supply passage. conduction, the second upper vehicle oil supply oil circuit does not supply oil to the fourth actuator; when the first arm valve is in two working positions, the second upper vehicle oil supply oil channel supplies oil to one of the arm hydraulic cylinders respectively.
  • the oil port supplies oil, and the other oil port of the arm hydraulic cylinder is connected to the return oil circuit through the first arm valve; among them, a load holding device is provided between the oil port of the arm hydraulic cylinder and the working oil port of the first arm valve.
  • Valve in which the load holding valve adopts a poppet valve structure and has zero leakage characteristics;
  • the oil inlet of the first arm valve is connected to the second upper vehicle oil supply oil line through the first arm oil inlet check valve, and the oil return port is connected to the oil return oil line.
  • the first arm valve The middle oil outlet is connected to the second bypass valve.
  • the first working oil port is connected to the small cavity oil port of the arm through the load holding valve of the arm small cavity.
  • the second working oil port is connected to the oil port of the arm small cavity through the load maintaining valve.
  • the large cavity oil port of the stick when the first stick valve is in the left operating position, the oil inlet flows to the second working oil port, and a damping is provided between the first working oil port and the return oil port; when the first working oil port flows to the oil return port, When the first stick valve is in the right working position, the oil inlet flows to the first working oil port, and the second working oil port directly flows to the oil return port;
  • the second arm oil return valve is a four-position six-way valve.
  • the center oil outlet of the second arm oil return valve is connected to the center oil inlet of the backup valve.
  • the oil inlet of the second arm oil return valve is The oil return port of the second arm oil return valve is connected to the oil return line through the second arm oil inlet check valve and the second arm oil inlet valve.
  • the first working oil port of the stick oil return valve is connected to the small cavity oil port of the stick through the load holding valve; the second working oil port of the second stick oil return valve is connected to the large cavity of the stick; the second bucket
  • the rod oil return valve has a neutral position and three working positions.
  • the oil return valve of the second arm When the arm is retracted, when the gravity of the arm exceeds the load, the oil return valve of the second arm is controlled to be in the second working position, the oil inlet flows to the second working oil port, and the first working oil port passes through the one-way The valve flows to the second working oil port, and the first working oil port flows back to the oil return port through the throttle hole. At this time, the return oil of the stick is damped by the throttle hole, and most of the return oil is regenerated to the large cavity of the stick through the one-way valve.
  • the oil port enables rapid movement of the stick and prevents the stick from being retracted and empty;
  • the oil return valve of the second arm When the arm is digging under resistance load, the oil return valve of the second arm is controlled to be in the third working position, the oil inlet flows to the second working oil port, and the first working oil port flows to the second working oil port through the one-way valve. Oil port, the first working oil port directly flows back to the oil return port. At this time, there is no damping limit on the oil return of the stick, the oil return area is large, and the excavation back pressure is small.
  • the backup valve is a three-position six-way valve, the center oil outlet of the backup valve is connected to the oil inlet of the first bypass valve, and the oil outlet of the first bypass valve is connected to the main return line.
  • the multi-way valve also includes an overload oil supply valve, which is provided between the two oil ports of the boom hydraulic cylinder, the bucket hydraulic cylinder, the arm hydraulic cylinder, and the backup hydraulic cylinder and the return oil line. There is an overload oil supply valve.
  • the present invention also provides a hydraulic system, including the multi-way valve described in the first aspect.
  • an excavator includes the hydraulic system described in the second aspect.
  • the boom adopts the principle and structure of the double load holding valve, so that the boom downward flow can return oil through the independent oil return oil channel, and the regeneration flow can enter through the independent regeneration oil channel.
  • the main oil circuit of the system greatly reduces return oil pressure loss and ensures the realization of flow regeneration;
  • the system adopts the principle and structure of two-way electronically controlled centralized bypass regulation to solve the problem of complex oil circuits in the current bypass system, pressure suppression at system start-up or failure of the main valve main oil circuit.
  • the large cavity of the stick uses a load holding valve structure and principle to prevent the stick from falling when the stick is hoisted in the retracted position; a new multi-way valve principle and configuration plan is designed to achieve the goal of adding a boom regeneration valve Based on functions such as independent control of core and bucket rod oil inlet, compared with current excavator multi-way valves, the volume does not increase and the system cost is reduced. Without increasing the volume of the multi-way valve, the excavator boom can be lowered to return oil to other actuators for flow regeneration, bucket rod compound priority and low back pressure oil return, bypass startup without pressure independent adjustment, crushing, and safe lifting. and other excavator functions to achieve low fuel consumption, high efficiency and high controllability of the excavator.
  • Figure 1 is a schematic structural diagram of a multi-way valve according to an embodiment of the present invention.
  • Figure 2 is a configuration diagram of a multi-way valve according to an embodiment of the present invention.
  • Figure 3 is a working principle diagram of the first joint of the multi-way valve according to an embodiment of the present invention.
  • Figure 4 is a working principle diagram of the second link of the multi-way valve according to an embodiment of the present invention.
  • Figure 5 is a working principle diagram of the third joint of the multi-way valve according to an embodiment of the present invention.
  • a multi-way valve includes a first working link 1, a second working link 2, and a third working link 3; it is provided with a first main oil inlet P1, a second main oil inlet P1, and a second main oil inlet P1.
  • Oil inlet P2, main oil return port R3 also includes: the first upper vehicle oil supply oil path 114 connected with the first main oil inlet P1, and the second upper vehicle oil supply oil path connected with the second main oil inlet P2 Oil path 113, oil return path 315 connected to the main oil return port R3, first center oil supply path 115, second center oil supply path 116;
  • the principle of the multi-way valve in this embodiment includes a first working link 1, a second working link 2, and a third working link 3.
  • the first working link 1 includes a linear travel valve 102, a left travel valve 111, Right travel valve 101, rotary valve 110, relief valve 103, first relief check valve 104, second relief check valve 105, pump P1 circuit check valves 106 and 112, pump P2 circuit check valves 107 and 109. Rotate the oil inlet check valve 108.
  • the first working link linear travel valve 102 When the first working link linear travel valve 102 is in the middle working position, it connects P1 and P2 through the orifice 102.1 to realize the combined flow of pump P1 and pump P2;
  • the second working link 2 includes the first Boom valve 202, second boom valve 201, third boom valve 206, bucket valve 215, second bypass link 205, boom first load holding valve 217, boom second load holding valve 210, boom Small cavity oil supply check valve 211, boom regeneration check valve 207, first boom oil inlet cut-off valve 204, second boom oil inlet check valve 203, bucket oil inlet check valve 212;
  • third work Link 3 includes the first stick valve 301, the second stick oil inlet valve 304, the second stick oil return valve 305, the backup valve 313, the first bypass valve 311, the stick small cavity load holding valve 310, the stick Large cavity load holding valve 306, first arm oil inlet check valve 302, and backup oil inlet check valve 309.
  • the second working link 2 is arranged between the first working link 1 and the third working link 3 and is fixedly connected together.
  • the multi-way valve configuration in this embodiment is divided into three blocks, including a first configuration block 4, a second configuration block 5, and a third configuration block 6.
  • One working link 1 corresponds to the first configuration block 4, the second working link 1 corresponds to the second configuration block 5, and the third working link 1 corresponds to the third configuration block 6.
  • the first working unit 1 includes a travel valve group and a rotary valve group; wherein the travel valve group includes a linear travel valve 102, a left travel valve 111, and a right travel valve 101;
  • the rotary valve group includes a rotary valve 110 for controlling a rotary hydraulic cylinder;
  • the second working unit 2 includes a boom valve group for controlling the boom hydraulic cylinder and a bucket valve group for controlling the bucket hydraulic cylinder; wherein the boom valve group includes a first boom valve 202, a third The second boom valve 201, the third boom valve 206, the first boom load holding valve 217, and the second boom load holding valve 210; the bucket valve group includes a bucket valve 215;
  • the third working unit 3 includes a stick valve group for controlling the stick hydraulic cylinder and a standby valve group for controlling the standby hydraulic cylinder; wherein the stick valve group includes a first stick valve 301, a second stick valve 301, and a second stick valve group.
  • the backup valve group includes a backup valve 313;
  • the first line of the first main oil inlet P1 passes through the first oil supply oil line 114 one-way (one-way valve 106) to the first boom valve 202, bucket valve 215, second arm return valve 305, Backup valve 313 supplies oil;
  • the first path of the second main oil inlet P2 passes through the right travel valve 101.
  • the center oil inlet and the center oil outlet of the right travel valve 101 are connected, it passes through the rotary valve 110, the second boom valve 201, and
  • the center oil inlet and outlet of the first stick valve 301 form the second center oil supply passage 116, and at the same time flow to the second upper vehicle through the center oil outlet one-way (one-way valve 107) of the right travel valve 101
  • Oil supply circuit 113; the center oil inlet and center oil outlet of the rotary valve 110, the second boom valve 201, and the first stick valve 301 are in a normally open state;
  • the second path of one of the first main oil inlet P1 or the second main oil inlet P2 passes through the linear travel valve 102 and is connected to the left travel valve 111.
  • the center oil inlet and the center oil outlet of the left travel valve 111 guide
  • the first center oil supply passage 115 is formed through the center inlet and outlet ports of the first boom valve 202, bucket valve 215, second arm oil return valve 305, and backup valve 313 in sequence.
  • the center oil outlet of the left travel valve 111 has a one-way flow (one-way valve 112) to the first upper vehicle oil supply oil path 114; among them, the first boom valve 202, the bucket valve 215, and the second arm oil return valve 305 , the middle oil inlet and the middle oil outlet of the backup valve 313 are in a normally open state;
  • the second path of the first main oil inlet P1 or the second main oil inlet P2 passes through the linear travel valve 102 and then passes through the second onboard oil supply oil path 113 one-way (one-way valve 109) to the rotary valve 110, The second boom valve 201 and the first stick valve 301 supply oil.
  • a first bypass valve 311 is also included.
  • the end of the first intermediate oil supply channel 115 is connected to the oil inlet of the first bypass valve 311 .
  • the oil outlet of the valve 311 is connected to the oil return passage 315;
  • the end of the second middle oil supply channel 116 is connected to the oil inlet of the second bypass valve 205, and the oil outlet of the second bypass valve 205 is connected to Return oil passage 315;
  • the first bypass valve 311 and the second bypass valve 205 are both four-position two-way valves with the same structure.
  • first working position naturally working position
  • second working position the oil inlet and the oil outlet pass through the first damping hole is connected
  • third working position the oil inlet and the oil outlet are connected through the second damping hole
  • fourth working position When in position, the oil inlet and oil outlet are directly connected.
  • the first working link 1 also includes a relief valve 103 connected to the main oil return port R3, and the flow of the first main oil inlet P1 passes through
  • the first overflow check valve 104 and the relief valve 103 can realize the overflow return to the fuel tank, and the flow of the second main oil inlet P2 can realize the overflow return to the fuel tank through the second overflow check valve 105 and the relief valve 103;
  • pumps P1 and P2 realize the linear travel function through the linear travel valve 102.
  • the linear travel valve 102 is a three-position four-way valve, including The first oil inlet, the second oil inlet, the first working oil port, the second working oil port, the first oil inlet is connected with the hydraulic pump IP1, the second oil inlet is connected with the hydraulic pump IIP2, the first working oil The port is connected to the left travel working oil line, which supplies oil to the left travel valve 111, and the second working oil port is connected to the second upper vehicle oil supply oil line 113 (provided with a one-way valve 109);
  • the linear travel valve 102 has three working positions: when the linear travel valve 102 is in the first working position (left working position), the first oil inlet is connected to the first working oil port, and the second oil inlet is connected to the second working oil port.
  • the oil ports are connected; when the linear travel valve 102 is in the second working position (middle working position), the first oil inlet is connected to the second working oil port, and the second oil inlet is connected to the first working oil port, and at the same time, the first oil inlet is connected to the second working oil port.
  • the first oil inlet and the second oil inlet p2 are connected through the first throttle port 102.1 to achieve merging; when the linear travel valve 102 is in the third working position (right working position), the first oil inlet passes through the third throttle The hole 102.4 is connected to the second working oil port. At the same time, the first oil inlet flows to the second oil inlet through the one-way valve 102.3 and the second throttle hole 102.2, and the second oil inlet is connected to the first working oil port.
  • the left travel valve 111 is a three-position six-way valve.
  • the center oil inlet and the center oil outlet of the left travel valve 111 are connected, and the first main oil inlet P1 passes through
  • the working oil of the left travel valve 111 flows to the first center oil supply channel 115 through the left travel valve 111.
  • the center oil outlet of the left travel valve 111 (through the pump P1 circuit check valve 112) flows unidirectionally to the first center oil supply channel 115.
  • the two oil ports for the left travel are connected to the return oil channel through the return port of the left travel valve 111; when the left travel valve 111 is located at the left and right working positions When , the center oil inlet and the center oil outlet of the left travel valve 111 are not connected, and the hydraulic oil enters one of the two left travel oil ports (oil port AtL or oil port BtL) through the left travel valve 111.
  • the other oil port (oil port BtL or oil port AtL) returns oil to realize the forward and reverse rotation of the left walking motor;
  • the right travel valve 101 is a three-position six-way valve.
  • the center oil inlet and the center oil outlet of the right travel valve 101 are connected, and the first main oil inlet P1 passes through
  • the working oil of the right travel valve 101 flows to the second center oil supply channel 116 through the right travel valve 101.
  • the center oil outlet of the right travel valve 101 (through the pump P2 circuit check valve 107) flows unidirectionally to the second center oil supply channel 116.
  • the two oil ports (oil port Atr or oil port Btr) of the right travel are connected to the return oil channel through the oil return port of the right travel valve 101; when the right travel valve 101 is located in the left and right working positions When , the center oil inlet and the center oil outlet of the right travel valve 101 are not connected, and the hydraulic oil enters one of the two right travel oil ports (oil port Atr or oil port Btr) through the right travel valve 101.
  • the other oil port (oil port Btr or oil port Atr) returns oil to realize the forward and reverse rotation of the right traveling motor.
  • the linear travel valve 102 works in the left position, the first oil inlet is connected to the first working oil port, and the second oil inlet is connected to the second working oil port, that is, the flow of pump P2 passes through the linear travel
  • the valve 102 and the one-way valve 109 are sent to the second oil supply line 113 to supply oil to the rotary valve 110, the second boom valve 201, the first stick valve 301 and other actuators.
  • the pump P1 passes through the linear travel valve.
  • 102 supplies the first center oil supply passage 115 to the left travel valve 111, the first boom valve 202, the bucket valve 215, the stick 2 valve 305, and the backup valve 313;
  • the linear travel valve 102 works in the middle working position, the first oil inlet is connected to the second working oil port, and the second oil inlet is connected to the first working oil port. Connected, the first oil inlet and the second oil inlet are connected through the first throttle port 102.1. At this time, part of the flow of P2 passes through the first throttle port 102.1, the one-way valve 106, the first upper vehicle oil supply oil line 114, The bucket oil inlet check valve 212 enters the bucket valve 215.
  • the flow of pump P1 passes through the one-way valve 106, the first oil supply line 114, and the bucket oil inlet check valve 212 and enters the bucket valve 215, realizing The two pumps merge; similarly, when the backup valve 313 moves, the P1 pump P2 oil supplies oil to the P1 oil pump through the central 102.1 throttle hole of the linear travel valve 102, and passes through the one-way valve 106 and the first oil supply line 114 , the backup oil inlet check valve 309 enters the backup valve 313 to realize the backup merging function;
  • the first oil inlet is connected to the second working oil port through the third throttle hole 102.4, and the second oil inlet is connected to the first working oil port.
  • the first oil inlet is connected with the second oil inlet through the one-way valve 102.3 and the second orifice 102.2.
  • the pump P1 passes through the third orifice 102.4 of the linear travel valve and passes through the one-way valve 109 and the second oil inlet.
  • the second upper car oil supply line 113 supplies oil to the rotary valve 110, the second boom valve 201, the first stick valve 301 and other actuators.
  • pump P1 can supply oil to the left travel valve 111 through the one-way valve 102.3 and the second orifice 102.2 in the linear travel valve.
  • the other channel enters the pump P2 oil circuit to merge and supply oil to the right travel valve 101. Since the third Due to the throttling effect of the three orifices 102.4, the pump P1 gives priority to supplying oil to the left travel valve 111 and the right travel valve 101 to ensure priority for the travel function.
  • the rotary valve 110 is a three-position six-way valve with a neutral position and two working positions.
  • the rotary valve 110 When the rotary valve 110 is in the neutral position, only the rotary valve 110 The middle oil inlet and the middle oil outlet are connected, and the second upper oil supply oil circuit 113 does not supply oil to the rotary hydraulic cylinder; when the rotary valve 110 is in two working positions, the middle oil inlet of the rotary valve 110 The oil port is connected to the center oil outlet.
  • the second oil supply line 113 supplies oil to one of the two oil ports (As, Bs) of the rotary hydraulic cylinder through the rotary valve 110, and the other oil port. It is connected to the return oil passage through the rotary valve 110.
  • FIG. 4 shows the working principle of the second working link 2.
  • the second working link 2 includes a first boom valve 202, a second boom valve 201, a third boom valve 206, a bucket valve 215, a second side Through valve 205, first boom load holding valve 217, second boom load holding valve 210, boom oil inlet cut-off valve 204, boom small cavity oil supply check valve 211, boom regeneration check valve 207, The second boom oil inlet check valve 203 and the bucket oil inlet check valve 212.
  • the first boom valve 202 is a three-position six-way valve with a center position and two working positions.
  • the oil outlet is connected, the first neutral oil supply channel 115 is connected, and the first upper oil supply channel 114 does not supply oil to the boom hydraulic cylinder;
  • the first boom valve 202 is located at two working positions , the first upper vehicle oil supply oil path 114 passes through the first boom oil inlet cut-off valve 204, the first boom valve 202, and the boom load holding valve 217 to the two oil ports of the boom hydraulic cylinder (boom large cavity oil One of the oil ports Ab and the boom small cavity oil port Bb) supplies oil, and the other oil port is connected to the oil return path through the first boom valve 202;
  • the oil inlet of the first boom valve 202 communicates with the first boom oil inlet cut-off valve 204 (the first boom oil inlet cut-off control valve 216 is used to control the opening and closing of the first boom oil inlet cut-off valve 204).
  • the oil supply line 114 is connected to the vehicle
  • the oil return port of the first boom valve 202 is connected to the return oil line;
  • the first working oil port is connected to the boom large cavity oil port Ab through the boom load holding valve 217.
  • the second working oil port is connected to the boom small cavity oil port Bb, and the middle oil outlet is connected to the middle oil inlet of the bucket valve 215.
  • the second boom valve 201 is a three-position six-way valve, and the oil inlet is connected to the second upper vehicle oil supply oil path 113 through the second upper vehicle oil inlet check valve 203 (to realize the single use of the second upper vehicle oil supply oil path 113 (supply oil to the second boom oil inlet check valve 203), the oil return port is connected to the oil return channel, the center oil inlet is connected to the center oil outlet of the rotary valve 110; the first working oil port passes through the oil channel 221.
  • Oil passage 224, load holding valve 210, oil passage 219, and oil passage 222 are connected to the boom large cavity oil port Ab; the second working oil port is connected to the boom large cavity through oil passage 220, oil passage 223, load holding valve 217
  • the cavity oil port Ab is connected;
  • the middle oil outlet is connected to the middle oil inlet of the third boom valve 206;
  • the second boom valve 201 has a middle position and two working positions; when the second boom valve 201 is in the middle position When the second boom valve 201 is in the right working position, only the center oil inlet flows in the direction of the center oil outlet (the second center oil supply passage 116); when the second boom valve 201 is in the right working position, the center oil inlet flows in the direction of the center oil outlet (the second center oil supply channel 116)
  • the middle oil outlet and the oil inlet flow in the direction of the first working oil port (oil inlet from the boom chamber Ab), but there is no continuity between the oil return port and the second working oil port; when the second boom valve 201 When
  • the third boom valve 206 is a two-position six-way valve.
  • the oil return port flows unidirectionally to the second upper vehicle oil supply circuit 113 through the regeneration check valve 207.
  • the center oil outlet is connected to the center of the first stick valve 301. position oil inlet (the middle oil outlet of the first stick valve 301 is connected to the return oil line through the second bypass valve 205), the first working oil port passes through the load holding valve 210, and the first line is connected to the boom main
  • the cavity oil port Ab2 is connected, the second channel is connected with the boom large cavity oil port Ab through the oil passage 219 and the oil passage 222, and the middle oil outlet is connected to the middle oil inlet of the third boom valve 206;
  • the center oil inlet supplies oil to the center oil outlet, and the center oil inlet is connected with the oil inlet (to the second center oil supply channel 116 circulation);
  • the middle oil inlet supplies oil to the middle oil outlet, and the first working oil port flows in the direction of the oil return port (boom large cavity oil port Ab , Ab2 returns oil to the second oil supply line 113);
  • It also includes a regeneration oil circuit for the boom large cavity, including a boom large cavity oil replenishment check valve 208; when the boom rises, the boom large cavity oil port Ab passes through the boom large cavity oil replenishment check valve 208 from the oil return channel. Regenerative oil replenishment to prevent the boom from emptying;
  • It also includes a regeneration oil circuit in the boom small cavity, including a one-way oil replenishment check valve 211 in the boom small cavity.
  • a regeneration oil circuit in the boom small cavity, including a one-way oil replenishment check valve 211 in the boom small cavity.
  • the return oil path passes through the boom large cavity oil supply check valve 208 and the first path is connected to the boom large cavity oil port Ab2, and the second path supplies oil to the boom large cavity oil port Ab through the oil passage 222;
  • the return oil path is connected to the boom small cavity oil port Bb through the boom small cavity oil supply check valve 211.
  • the second bypass valve 205 is a four-position two-way valve.
  • the oil inlet and the oil outlet are connected through the damping hole 205.5 on the second bypass valve 205 to return oil. path, when the engine is started and ignited, pump 2 is in an unloaded state due to the connection to the return oil line, so pump 2 does not hold pressure during startup.
  • the pump pressure of main pump 2 is not at the initial stage of startup. It is very low, slightly higher than the pilot pressure, so that it has the ability to supply oil to the pilot oil line through the pressure reducing valve.
  • This principle can be used in hydraulic systems without pilot pump sources to reduce system costs; in hydraulic systems with pilot pump sources
  • the second bypass spool 205 quickly moves to the right end working position 205.4, the oil inlet and the oil outlet are directly connected, and the oil return line connected to pump 2 is in an unloaded state and is at the maximum oil return.
  • pump 2 is in the idle state at the lowest pressure; in a hydraulic system without a pilot pump source, when the system requires the main pump to provide a pilot pressure oil source, during the working process of the excavator, the second bypass spool 205 runs to Working position 205.2 (the oil inlet and the oil outlet are not connected) or working position 205.3 (the oil inlet and the oil outlet are connected through the damping hole), when the maximum handle is operated, the second bypass valve core 205 moves to work Position 205.2. At this time, pump 2 is isolated from the return oil circuit, and all the oil in pump 2 is supplied to the actuator to improve work efficiency.
  • the bucket valve 215 is a four-position six-way valve.
  • the center oil inlet of the bucket valve 215 is connected to the center oil outlet of the first boom valve 202.
  • the center oil outlet of the bucket valve 215 is connected to the center oil outlet of the first boom valve 202.
  • the middle oil inlet of the second bucket arm oil return valve 305 is connected to the first upper vehicle oil supply oil path 114 through the bucket oil inlet check valve 212 (to realize the first upper vehicle oil supply oil path 114 to the shovel
  • the bucket oil inlet check valve 212 has one-way oil supply), the oil return port is connected to the return oil line, and the two working oil ports are connected to the bucket hydraulic cylinder (oil port Ac, oil port Bc); when the bucket valve 215 is at When in the neutral position, the first upper vehicle oil supply circuit 114 does not supply oil to the third actuator (bucket); when the bucket valve 215 is in the three working positions, the first upper vehicle oil supply circuit 115 passes through The bucket large cavity oil port Ac or the bucket small cavity oil port Bc supplies oil to one cavity of the bucket valve 215, and the corresponding hydraulic oil in the other cavity passes through the bucket small cavity oil port Bc or the bucket large cavity oil port.
  • P1 supplies oil to the first boom valve 202 and bucket valve 215 through the one-way valve 106
  • P2 supplies oil to the second boom valve 201, the third boom valve 206 and the second bypass valve 205 through the one-way valve 107 Parallel arrangement.
  • the median flow of pump P2 passes through the oil passage 225, the second boom valve 201, and the third boom valve 206, it enters the first stick valve 301, oil passage 218, and second bypass valve 205 of the third working link 3.
  • the second bypass valve 205 functions to centrally regulate the bypass flow of the pump P2.
  • the P1 and P2 double pumps merge, and the P1 flow enters the boom large cavity oil port Ab through the boom oil inlet cut-off valve 204, the first boom valve 202, and the boom load holding 217.
  • the P2 flow passes through the single Directional valve 203, second boom valve 201, oil passage 224, load holding valve 210, oil passage 219, enter the boom large cavity oil port Ab;
  • the boom large cavity oil port Ab passes through the boom large cavity
  • the oil replenishment check valve 208 performs regenerative oil replenishment from the oil return channel R3 to prevent the boom from emptying;
  • oil is supplied to the oil port Bb of the small boom chamber, and oil is returned to the oil port Ab of the large boom chamber.
  • P1 supplies oil to the small boom chamber through the first boom oil inlet cut-off valve 204 and the first boom valve 202.
  • Oil port Bb supplies oil.
  • the flow of oil return channel R3 can supply oil to the oil port Bb of the small boom cavity through the boom small cavity oil supply check valve 211; the return oil flow of the large boom cavity passes through the boom small cavity oil supply check valve 211.
  • the arm 201 returns to the oil tank (the first boom and the second boom return oil at the same time); the second part of the oil passes through the oil passage 222, the oil passage 219, the load holding valve 210, the third boom valve 206, and the regeneration check valve 207 Then it flows to the P2 oil circuit to supply oil to the P2 oil circuit; therefore, when the boom is lowered and the bucket arm is combined, the oil return flow from the large cavity of the boom not only returns to the oil tank through the first boom valve 202 and the second boom valve 201 , and at the same time, the return oil flow can be regenerated to the P2 oil line through the third boom valve 206 to supply the stick.
  • the oil return back pressure in the large cavity of the boom is controlled by adjusting the oil return area of the second boom valve 201, so that Its back pressure is higher than P2 pressure to achieve flow regeneration.
  • the second working link 2 mainly has 5 new principles and features:
  • the second boom valve 201 has a middle position and two working positions. When it works at the right end working position 201.2, the second oil supply line 113 of the P2 pump passes through the one-way valve 203, the second boom 201, Oil passage 224, load holding valve 210, oil passage 219, and oil passage 222 are connected to the boom large cavity oil port Ab to supply oil to the boom large cavity. Oil port Bb cannot return oil through the second boom valve 201 at this time, so The second boom realizes independent control of boom rising and oil inlet;
  • the second boom valve 201 works at the left end working position 201.1, the second oil supply line 113 of the P2 pump cannot supply oil to the boom large cavity oil port Ab, and the boom large cavity oil port Ab can supply oil through the second boom valve.
  • the arm valve 201 returns to the oil tank, so in the working position 201.1, the second boom valve 201 realizes independent control of the oil return of the boom lowering;
  • the oil tank (the first boom and the second boom return oil at the same time), and the other part of the oil passes through the oil passage 222, the oil passage 219, the load holding valve 210, the third boom 206, and the one-way valve 207 and then regenerates to the P2 circuit. After it is merged with the oil circuit of pump P2, it is supplied to other actuators to realize the regeneration and utilization of the return oil from the large cavity of the boom.
  • the regeneration flow passes through the oil passage 222, the flow passage 219 and the load holding valve 210, it communicates with the first boom 202 and the second boom
  • the return oil flow channel of valve 201 (load holding valve 217, flow channel 223) is in a parallel relationship, and the boom adopts the principle and structural scheme of double load holding valves, so the oil hydraulic loss is small and the regeneration utilization rate is high;
  • the second bypass valve 205 adopts a distributed structure to reduce the volume of the main valve.
  • the median flow of pump P2 passes through the first stick valve 301 in the third working link 3 and then returns to the second working link 2 again, connected through the oil passage 218 Second bypass valve 205.
  • the second bypass valve 205 has four working positions. At the natural working position 205.1, the P2 pump connects the oil return path through the center flow channel of each valve, the oil channel 218, and the damping hole 205.5 on the second bypass valve 205; When the engine is started and ignited, the pump P2 is in an unloaded state due to the connection to the oil passage T, so the pump P2 does not hold pressure during startup.
  • the pump pressure of the main pump P2 is not very low at the initial stage of startup. Higher than the pilot pressure, it has the ability to supply oil to the pilot oil line through the pressure reducing valve.
  • This principle can be used in hydraulic systems without a pilot pump source to reduce system costs.
  • the second bypass valve 205 quickly moves to the right end working position 205.4, and the oil return line connected to the pump P2 is in an unloaded state and is in the maximum oil return area state.
  • the second bypass valve 205 runs to the working position 205.2 or works Position 205.3, when the maximum handle is operated, the second bypass valve 205 moves to the working position 205.2.
  • the pump P2 is isolated from the return oil circuit, and all the oil of pump P2 is supplied to the actuator, improving work efficiency.
  • the bucket valve 215 adopts the principle of four working positions. When the bucket is retracted and running without load, the bucket valve 215 works at the second working position 215.2 at the left end. The AC oil return to the small cavity of the bucket passes through the damping 215.1 to prevent the bucket from absorbing oil. Empty; when the bucket is retracted for excavation operation; the bucket valve 215 works at the first working position 215.3 at the left end, and the AC oil return to the small cavity of the bucket has no damping, which reduces the oil return back pressure during excavation operations.
  • FIG. 5 shows the working principle of the third working link 3.
  • the third working link 3 includes the first arm valve 301, the second arm oil inlet valve 303, the second arm oil return valve 305, and the small arm chamber.
  • the first stick valve 301 is a three-position six-way valve with a neutral position and two working positions.
  • the oil supply line 113 of the upper vehicle does not supply oil to the arm hydraulic cylinder; when the first arm valve 301 is located at the two working positions, the second oil supply oil path 113 of the upper vehicle supplies oil to the arm hydraulic cylinder (the small cavity of the arm) respectively.
  • One of the oil ports (oil port Aa and arm large cavity port Ba) supplies oil, and the other oil port of the arm hydraulic cylinder is connected to the return oil path through the first arm valve 301; among them, the arm hydraulic cylinder oil port is connected to the first arm hydraulic cylinder oil port.
  • a load holding valve is provided between the working oil ports of the first arm valve 301.
  • a large arm chamber is provided between the oil port of the large arm chamber, the oil port of the small arm chamber and the first arm valve 301.
  • the oil inlet of the first arm valve 301 is connected to the second upper vehicle oil supply oil line 113 through the first arm oil inlet check valve 302, and the oil return port is connected to the return oil line.
  • the center oil outlet of the first stick valve 301 is connected to the second bypass valve 205
  • the first working oil port is connected to the stick small cavity oil port Aa through the load holding valve 310
  • the other way is connected to the stick small cavity oil port Aa through the oil passage 317.
  • the first working oil port of the second arm oil return valve 305 is connected; the first channel of the second working oil port passes through the arm large cavity load holding valve 306 and is connected to the arm large cavity oil port Ba1, and the second channel passes through the oil passage 316 Connected to stick oil return port Ba2.
  • the oil inlet flows to the second working oil port, and a damping 301.1 is provided between the first working oil port and the return port; when the first arm valve 301 When the valve 301 is in the right working position, the oil inlet flows to the first working oil port, and the second working oil port directly flows to the oil return port.
  • the second arm oil return valve 305 is a four-position six-way valve.
  • the center oil outlet of the second arm oil return valve 305 is connected to the center oil inlet of the backup valve 313.
  • the second arm oil return valve 305 has The oil inlet is connected to the first oil supply oil line 114 through the second arm oil inlet valve 303 and the second arm oil inlet check valve 304.
  • the oil return port of the second arm oil return valve 305 is connected to the return port. Oil circuit; the first working oil port of the second arm oil return valve 305 is connected to the arm small cavity Aa through the oil passage 317 and the load holding valve 310; the second working oil port of the second arm oil return valve 305 It is connected with the large cavity Ba2 of the bucket rod.
  • the second arm oil return valve 305 has a neutral position and three working positions. When the second arm oil return valve 305 is in the neutral position, only the first neutral oil supply channel 115 is open, and the first upper oil supply channel 115 is open.
  • the vehicle oil supply line 114 does not supply oil to the arm hydraulic cylinder; when the second arm oil return valve 305 is in the first (leftmost) working position, the oil inlet of the second arm oil return valve 305 flows to the first The working oil port is connected, and the second working oil port is connected to the oil inlet;
  • the second stick oil return valve 305 When the stick is retracted and the gravity of the stick exceeds the load, the second stick oil return valve 305 is controlled to be in the second working position (position 305.1), and the oil inlet flows to the second working oil port, and the first working The oil port flows to the second working oil port through the one-way valve 305.4, and the first working oil port flows back to the oil return port through the orifice 305.3. At this time, the return oil of the stick is damped by the orifice 305.3, and most of the oil return passes through the single oil port. Valve 305.4 regenerates to the oil port Ba of the large cavity of the arm to realize rapid movement of the arm and prevent the arm from being sucked in;
  • the second arm oil return valve 305 When the arm is digging under resistance load, the second arm oil return valve 305 is controlled to be in the third working position 305.2, the oil inlet flows to the second working oil port, and the first working oil port flows to the third working oil port through the one-way valve. The second working oil port, the first working oil port directly flows back to the oil return port. At this time, there is no damping limit on the oil return of the stick, the oil return area is large, and the excavation back pressure is small.
  • the median flow rate of pump P1 passes through the oil passage 318, the second arm oil return valve 305, and the backup valve 313, and then passes through the first bypass valve 311 and is connected to the oil return channel 315.
  • the first bypass valve 311 functions to centralize pump P1. Bypass flow regulation.
  • the P1 oil passes through the second stick oil inlet valve 303, one-way valve 304, second stick oil return valve 305 (the oil only passes through, not controlled), oil passage 316, and load holding valve 306 supplies oil to the large cavity Ba1 of the arm; P2 oil supplies oil to the large cavity Ba1 of the arm through the one-way valve 302, the first arm valve 301, the oil passage 316, and the load holding valve 306; oil returns to the small cavity Aa of the arm. Part of the oil returns through the load holding valve 310, oil passage 317, first stick valve 301 and damping 301.1, and the other part returns through the load holding valve 310, oil passage 317, and the second stick valve oil return valve 305.
  • the second arm oil return valve 305 has a flow regeneration function.
  • the second arm oil return valve works at the 305.1 position to realize oil regeneration in the large cavity of the arm.
  • the second arm oil return valve works at the 305.2 position to increase the oil return area and reduce excavation pressure loss.
  • the P1 oil passes through the second stick oil inlet valve 303, one-way valve 304, second stick oil return valve 305 (the oil only passes through, not controlled), oil passage 317, and load holding valve 310 supplies oil to the small cavity Aa of the stick, and the P2 oil supplies oil to the small cavity Aa of the stick through the check valve 302, the first stick valve 301, the oil passage 317, and the load holding valve 310.
  • the oil return from the large cavity Ba1 of the arm returns through the load holding valve 306, the oil passage 316, the first arm valve 301 and the second arm oil return valve 305.
  • the backup valve 313 is a three-position six-way valve.
  • the middle oil outlet of the backup valve 313 is connected to the oil inlet of the first bypass valve 311, and the oil outlet of the first bypass valve 311 is connected to the main return oil. channel;
  • the first oil supply line 114 (through the backup oil inlet check valve 309) unidirectionally supplies oil to the oil inlet, the oil return port is connected to the return oil line, and the two working oil ports are respectively connected to the backup hydraulic cylinder Oil port Ao, oil port Bo; when the backup valve 313 is in the neutral position, only the first neutral oil supply channel 115 is conductive, and the first upper oil supply channel 114 does not supply oil to the backup hydraulic cylinder; when the backup valve When the valve 313 is in two working positions, the first oil supply line 115 supplies oil to one of the two oil ports (Ao, Bo) of the backup hydraulic cylinder through the backup valve 313, and the other oil port passes through the backup valve. 313 is connected to the oil return line.
  • the first bypass valve 311 has the same structure as the second bypass valve 205, and its working principle is similar to that of the second bypass valve 205 (which will not be described again), so that the pump P1 does not hold back the pressure when it is started.
  • the third working link 3 mainly has three new principles and features:
  • the working principle of the first bypass valve 311 is similar to that of the second bypass valve 205, so that the pump P1 does not hold back the pressure when it is started.
  • the second arm oil inlet valve 303 and the second arm oil return valve 305 are used to realize independent control of the oil inlet and oil return of the arm on the pump P1 side; the second arm oil return valve 305 adopts the four-working position principle.
  • the second stick oil return valve 305 operates at the working position 305.1, and the oil return to the small cavity Aa of the stick passes through the damping 305.3, increasing the back pressure of the oil return to the small cavity of the stick.
  • the second stick oil return valve 305 runs at the working position 305.2, and the oil returned from the small cavity Aa of the stick is directly returned to the oil tank, reducing the oil return back pressure during excavation.
  • the first stick valve 301 retracts, the return oil from the small cavity Aa of the stick passes through the damping hole 301.1, and together with the second stick oil return valve 305 determines the pressure state of the small cavity of the stick, preventing emptying or oil return when the stick retracts. Back pressure is too high.
  • the backup valve 313 is placed in the third working link 3 for backup connection to the crushing actuator.
  • the large cavity Ba1 of the arm cylinder oil port adopts the structure and principle of the load holding valve 306. Therefore, when the arm is in the retracted position (the arm does not move) and the boom is raised for lifting operations, the large cavity Ba1 of the arm cylinder
  • the first arm valve 301 and the second arm return valve 303 cannot be returned through the load holding valve 306.
  • the load holding valve 306 adopts a poppet valve structure and has zero leakage characteristics, so the arm can be safely hoisted without falling.
  • a multi-way valve in this embodiment adopts an electrical proportional control method. All multi-way valves with the same functions that use equivalent transformations such as hydraulic control methods, mechanical control methods, etc., fall under the The scope of protection of the patent of this invention:
  • the A/B load circuit of this application is equipped with an overload oil replenishment valve to limit the pressure of the load circuit and prevent air suction. Whenever the overload oil replenishment valve is replaced, such as replacing it with a relief valve, a plug, etc., the invention
  • the simplification of the design also falls within the protection scope of this application.
  • This embodiment provides a hydraulic system, including the multi-way valve described in Embodiment 1.
  • This embodiment provides an excavator, including the hydraulic system described in Embodiment 2.

Landscapes

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

Abstract

本发明公开了一种多路阀、液压系统及挖掘机，多路阀包括第一工作联、第二工作联、第三工作联，第一工作联包括行走阀组和回转阀组；第二工作联包括用于控制动臂液压缸的动臂阀组和用于控制铲斗液压缸的铲斗阀组；第三工作联包括用于控制斗杆液压缸的斗杆阀组和用于控制备用液压缸的备用阀组；在不增加多路阀体积基础上，实现挖掘机动臂下降回油向其它执行机构进行流量再生、斗杆复合优先和低背压回油、旁通启动无憋压独立调节、破碎、安全吊装等挖掘机全部功能，实现挖掘机低油耗、高效率、高操控性作业。

Description

一种多路阀、液压系统及挖掘机 技术领域
本发明属于工程机械技术领域，特别涉及一种多路阀、液压系统及挖掘机。
背景技术
随着国家绿色可持续发展战略实施及环保要求逐渐提升，挖掘机油耗、工作效率、操控性成为各个主机厂和客户重点关注指标。挖掘机在动臂下降过程中，动臂大腔由于自重作用回油量大、压力高，导致液压系统油温升温快，存在能量损失增加了燃油消耗，现有方案采用动臂再生阀芯在挖掘机复合动作时，将动臂回油流量再生到其他执行机构再利用，可以降低燃油消耗，提升工作效率，但是动臂回油流量在经过第一动臂阀芯时由于流道面积急剧变小压损较大，存在再生流量利用率较低或者再生功能不能实现，在原理和结构上存在严重缺陷。在操控性能上，尤其在微动操控性上，目前挖掘机采用旁通、主油口油路固定在一根阀芯上进行调节，旁通油路调节受到主油口油路调节影响，挖掘机冲击较大，整机操控柔和性较差。另外，在某些工况下挖掘机用于吊装重物，由于目前挖掘机斗杆大腔没有负载保持阀结构，当斗杆在内收极限位置提升动臂进行吊装时，斗杆阀芯存在泄漏，导致吊装时斗杆下坠，影响吊装作业。此外，在中大型挖掘机上，破碎作为一项常用功能，要求挖掘机多路阀具有备用联，用于挖掘机破碎，目前在增加了动臂下降再生功能的多路阀中，由于阀芯数量增加，在挖掘机多路阀体积限制条件下备用功能只能去掉，使得挖掘机没有破碎功能；或者是添加备用联功能，但是导致挖掘机多路阀体积增大，导致成本增加，安装不方便。
现有中大型多路阀原理和构型有2种方案，方案一主要特征：1、动臂再生结构是阀芯内部再生，不能实现动臂回油流量用于其它执行机构，能量损耗大；2、旁通、主油口油路固定在一根阀芯上进行调节整机冲击大。方案二主要特征：1、采用动臂再生阀芯实现复合动作时动臂下降回油流量载利用，但是动臂回油流量在经过第一动臂阀芯时由于流道面积急剧变小压损较大，存在再生流量利用率较低或者再生功能不能实现，在原理和结构上存在严重缺陷；2、旁通电控独立调节，但不是双向设计原理，启动时容易憋压或者启动初期由于连接油箱回油面积太大导致主泵压力太低不能提供先导油源等问题；3、斗杆回路复杂，采用斗杆切断阀、斗杆再生阀及负载保持阀等多个元件实现斗杆基本功能，造成主阀体积增大，成本增大或者由于控制多路阀体积需求不具备破碎功能；4、斗杆大腔没有负载保持阀结构和原理。
现有技术存在以下缺陷：1、动臂向其它执行机构不能实现流量再生或者再生量很少；2、目前方案旁通不能独立调节，或者旁通可以独立调节但存在启动憋压、或者启动阶段由于连接油箱回油面积太大导致主泵压力太低不能提供先导油源等现象；3、全电控多路阀斗杆回路原理复杂，采用斗杆切断阀、斗杆再生阀及负载保持阀等多个元件实现斗杆复合优先和低背压回油功能，造成主阀体积增大，成本增大或者由于控制多路阀体积需求不具备破碎功能。4、斗杆大腔没有负载保持阀导致吊装作业时斗杆存在下坠风险。
发明内容
目的：为了克服现有技术中存在的不足，本发明提供一种多路阀、液压系统及挖掘机。提出一种新的挖掘机多路阀原理和构型，动
技术方案：为解决上述技术问题，本发明采用的技术方案为：
第一方面，提供一种多路阀，包括第一工作联、第二工作联、第三工作联；第一主进油口、第二主进油口、主回油口；还包括：与第一主进油口连通的第一上车供油油路，与第二主进油口连通的第二上车供油油路，与主回油口连通的回油油路，第一中位供油油道、第二中位供油油道；所述第二工作联设置在所述第一工作联和第三工作联之间；
所述第一工作联包括行走阀组和回转阀组；其中所述行走阀组包括直线行走阀、左行走阀、右行走阀；所述回转阀组包括用于控制回转液压缸的回转阀；
所述第二工作联包括用于控制动臂液压缸的动臂阀组和用于控制铲斗液压缸的铲斗阀组； 其中所述动臂阀组包括第一动臂阀、第二动臂阀、第三动臂阀、动臂第一负载保持阀、动臂第二负载保持阀；所述铲斗阀组包括铲斗阀；
所述第三工作联包括用于控制斗杆液压缸的斗杆阀组和用于控制备用液压缸的备用阀组；其中所述斗杆阀组包括第一斗杆阀、第二斗杆进油阀、第二斗杆回油阀、斗杆小腔负载保持阀、斗杆大腔负载保持阀；所述备用阀组包括备用阀；
第一主进油口第一路通过第一上车供油油路单向给第一动臂阀、铲斗阀、第二斗杆回油阀、备用阀供油；
第二主进油口第一路经过右行走阀，当右行走阀的中位进油口与中位出油口导通时，依次通过回转阀、第二动臂阀、第一斗杆阀的中位进、出油口形成第二中位供油油道，同时通过右行走阀的中位出油口单向流向第二上车供油油路；其中回转阀、第二动臂阀、第一斗杆阀的中位进油口、中位出油口为常通状态；
第一主进油口或第二主进油口之一第二路经过直线行走阀连至左行走阀，当左行走阀的中位进油口与中位出油口导通时，依次通过第一动臂阀、铲斗阀、第二斗杆回油阀、备用阀的中位进、出油口形成第一中位供油油道，同时通过左行走阀的中位出油口单向流向第一上车供油油路；其中第一动臂阀、铲斗阀、第二斗杆回油阀、备用阀的中位进油口、中位出油口为常通状态；
第一主进油口或第二主进油口之第二路路经过直线行走阀后通过第二上车供油油路单向给回转阀、第二动臂阀、第一斗杆阀供油。
在一些实施例中，所述的多路阀还包括第一旁通阀，所述第一中位供油油道的末端连至第一旁通阀的进油口，第一旁通阀的出油口连至回油油道；
所述的多路阀还包括第二旁通阀，所述第二中位供油油道末端连至第二旁通阀的进油口，第二旁通阀的出油口连至回油油道；
所述第一旁通阀、第二旁通阀均为四位两通阀，结构相同，当处于第一工作位时，进油口和出油口通过第一阻尼孔连通；当处于第二工作位时，进油口和出油口不导通；当处于第三工作位时，进油口和出油口通过第二阻尼孔导通；当处于第四工作位时，进油口和出油口直接连通。
在一些实施例中，所述第一工作联还包括与主回油口相连通的溢流阀，所述第一主进油口通过第一溢流单向阀连至溢流阀的进油口；第二主进油口通过第二溢流单向阀连至溢流阀的进油口。
在一些实施例中，所述直线行走阀为一个三位四通阀，包括第一进油口、第二进油口、第一工作油口、第二工作油口，第一进油口与第一主进油口连通，第二进油口与第二主进油口连通，第一工作油口连至左行走工作油路，左行走工作油路供油给左行走阀，第二工作油口单向给第二上车供油油路供油；
直线行走阀具有三个工作位：
当直线行走阀处于第一工作位时，第一进油口向第一工作油口方向连通，第二进油口向第二工作油口连通；
当直线行走阀处于第二工作位时，第一进油口向第二工作油口方向连通，第二进油口向第一工作油口连通，同时第一进油口与第二进油口p通过第一节流口联通，实现合流；
当直线行走阀处于第三工作位时，第一进油口通过第三节流孔向第二工作油口方向连通，同时第一进油口通过单向阀、第二节流孔向第二进油口流通，第二进油口向第一工作油口连通。
所述左行走阀为三位六通阀，当左行走阀处于中位时，左行走阀的中位进油口与中位出油口导通，第一主进油口经左行走阀的工作油经左行走阀流至第一中位供油油道，同时左行走阀的中位出油口单向流向第一上车供油油路，左行走两个油口通过左行走阀的回油口与回 油油路连通；当左行走阀位于左右两个工作位时，左行走阀的中位进油口与中位出油口不导通，液压油经左行走阀分别实现一个左行走两个油口进油，另一个油口回油，进而实现左行走马达的正向和反向转动；
所述右行走阀为三位六通阀，当右行走阀处于中位时，右行走阀的中位进油口与中位出油口导通，第一主进油口经右行走阀的工作油经右行走阀流至第二中位供油油道，同时右行走阀的中位出油口单向流向第二上车供油油路，右行走两个油口通过右行走阀的回油口与回油油路连通；当右行走阀位于左右两个工作位时，右行走阀的中位进油口与中位出油口不导通，液压油经右行走阀分别实现一个右行走两个油口进油，另一个油口回油，进而实现右行走马达的正向和反向转动。
在一些实施例中，所述回转阀为三位六通阀，具有中位和两个工作位，当回转阀位于中位时，仅有回转阀的中位进油口与中位出油口导通，第二上车供油油路不向回转液压缸供油；当回转阀位于两个工作位时，回转阀的中位进油口与中位出油口导通，同时第二上车供油油路分别通过回转阀向回转液压缸两个油口中一个油口供油，另一个油口通过回转阀与回油油路连通。
在一些实施例中，所述第一动臂阀为三位六通阀，具有中位和两个工作位，当第一动臂阀位于中位时，仅有第一动臂阀的中位进油口与中位出油口导通，第一中位供油油道导通，第一上车供油油路不向动臂液压缸供油；当第一动臂阀位于两个工作位时，第一上车供油油路通过第一动臂进油切断阀、第一动臂阀、动臂负载保持阀分别向动臂液压缸两个油口中一个油口供油，另一个油口通过第一动臂阀与回油油路连通；第一动臂阀进油口通过第一动臂进油切断阀与第一上车供油油路相连通，第一动臂阀回油口与回油油路连通；第一工作油口通过动臂负载保持阀连至动臂大腔油口，第二工作油口连至动臂小腔油口，中位出油口连至铲斗阀的中位进油口；
第二动臂阀为三位六通阀，进油口通过第二动臂进油单向阀与第二上车供油油路相连，回油口与回油通道相连，中位进油口连至回转阀的中位出油口；第一工作油口通过负载保持阀连至动臂大腔油口；第二工作油口通过负载保持阀与动臂大腔油口连通；中位出油口连至第三动臂阀的中位进油口；第二动臂阀具有中位和两个工作位；当第二动臂阀位于中位时，仅有中位进油口流向中位出油口方向导通；当第二动臂阀位于右边工作位时，进油口流向第一工作油口方向导通，回油口与第二工作油口之间不导通；当第二动臂阀位于左边工作位时，第二工作油口流向回油口方向导通，进油口与第一工作油口不导通；
第三动臂阀为两位六通阀，回油口通过再生单向阀单向流向第二上车供油油路，第一工作油口通过负载保持阀与动臂大腔油口相连通；当第三动臂阀位于右边工作位时，仅有中位进油口流向中位出油口方向；当第三动臂阀位于左边工作位时，工作油口流向回油口方向导通，动臂大腔油口再生油至第二上车供油油路；
还包括动臂大腔再生油路，包括动臂大腔补油单向阀；动臂上升时，动臂大腔油口通过动臂大腔补油单向阀从回油通道进行再生补油，防止动臂吸空；
还包括动臂小腔再生油路，包括动臂小腔补油单向阀，动臂单动作下降时，动臂小腔油口通过单向阀从回油通道进行再生补油，防止动臂吸空。
在一些实施例中，所述铲斗阀为四位六通阀，进油口通过铲斗进油单向阀连至第一上车供油油路，回油口连至回油油路，两个工作油口连接铲斗液压缸油口；具有一个中位和三个工作位；
当铲斗阀位于中位时，第一上车供油油路不向铲斗液压缸供油；当铲斗阀位于三个工作位时，第一上车供油油路分别经铲斗大腔油口或铲斗小腔油口为铲斗阀的一个腔体供油，对应的另一个腔体内的液压油经铲斗小腔油口或铲斗大腔油口泄出再经过铲斗阀回油至回油油路；其中铲斗阀工作在左端第二工作位，铲斗小腔油口回油经过阻尼，防止铲斗吸空；在铲 斗内收挖掘运行时；铲斗阀工作在左端第一工作位，铲斗小腔油口回油没有阻尼，降低挖掘作业时回油背压。
在一些实施例中，所述第一斗杆阀为三位六通阀，具有中位和两个工作位，当第一斗杆阀位于中位时，仅有第二中位供油油道导通，第二上车供油油路不向第四致动器供油；当第一斗杆阀位于两个工作位时，第二上车供油油路分别向斗杆液压缸其中一个油口供油，斗杆液压缸另一个油口通过第一斗杆阀与回油油路连通；其中斗杆液压缸油口与第一斗杆阀的工作油口之间均设置有负载保持阀，其中负载保持阀采用锥阀结构，具有零泄漏特性；
进一步地，所述第一斗杆阀的进油口通过第一斗杆进油单向阀与第二上车供油油路相连，回油口与回油油路相连，第一斗杆阀的中位出油口连至第二旁通阀，第一工作油口经过斗杆小腔负载保持阀与斗杆小腔油口相连，第二工作油口经过斗杆大腔负载保持阀与斗杆大腔油口，当所述第一斗杆阀处于左边作位时，进油口流向第二工作油口导通，第一工作油口流向回油口之间设置有阻尼；当所述第一斗杆阀处于右边工作位时，进油口流向第一工作油口导通，第二工作油口直接流向回油口；
所述第二斗杆回油阀为四位六通阀，第二斗杆回油阀的中位出油口与备用阀的中位进油口相连，第二斗杆回油阀的进油口通过第二斗杆进油单向阀、第二斗杆进油阀与第一上车供油油路相连，第二斗杆回油阀的回油口连至回油油路；第二斗杆回油阀的第一工作油口经过负载保持阀与斗杆小腔油口相连；第二斗杆回油阀的第二工作油口与斗杆大腔相连通；所述第二斗杆回油阀具有中位和三个工作位，当第二斗杆回油阀处于中位时，仅有第一中位供油油道导通，第一上车供油油路不向斗杆液压缸供油；当第二斗杆回油阀处于第一工作位时，第二斗杆回油阀的进油口流向第一工作油口导通，第二工作油口流向进油口导通；
在斗杆内收时，当斗杆处于重力超越负载时，控制第二斗杆回油阀处于第二工作位，进油口流向第二工作油口导通，第一工作油口通过单向阀流向第二工作油口，第一工作油口通过节流孔回流向回油口，此时斗杆回油受到节流孔阻尼作用，回油大部分通过单向阀再生到斗杆大腔油口，实现斗杆快速运动和防止斗杆内收吸空；
当斗杆进行挖掘处于阻力负载时，控制第二斗杆回油阀处于第三工作位位置，进油口流向第二工作油口导通，第一工作油口通过单向阀流向第二工作油口，第一工作油口直接回流向回油口，此时斗杆回油没有阻尼限制，回油面积较大，挖掘背压较小。
在一些实施例中，所述备用阀为三位六通阀，备用阀的中位出油口连至第一旁通阀的进油口，第一旁通阀的出油口连至总回油油道；第一上车供油油路单向给进油口供油，回油口连至回油油路，两个工作油口分别连接备用液压缸油口；当备用阀位于中位时，仅有第一中位供油油道导通，第一上车供油油路不向备用液压缸供油；当备用阀位于两个工作位时，第一上车供油油路分别通过备用阀向备用液压缸两个油口中一个油口供油，另一个油口通过备用阀与回油油路连通。
在一些实施例中，所述的多路阀还包括过载补油阀，动臂液压缸、铲斗液压缸、斗杆液压缸、备用液压缸两个油口与回油油路之间均设置有过载补油阀。
第二方面，本发明还提供一种液压系统，包括第一方面所述的多路阀。
第三方面，一种挖掘机，包括第二方面所述的液压系统。
有益效果：本发明提供的多路阀、液压系统及挖掘机，动臂采用双负载保持阀原理和结构，实现动臂下降流量通过独立回油油道回油、再生流量通过独立再生油道进入系统主油路，大幅降低回油压损，保证流量再生实现；系统采用双向电控集中旁路调节原理和结构，解决目前旁通系统油路复杂，系统启动憋压或者主阀主油路不能提供先导油源等问题；斗杆大腔采用负载保持阀结构和原理，实现斗杆内收位置吊装时斗杆不下坠；设计新型多路阀原理和构型方案，实现在增加动臂再生阀芯、斗杆进油独立控制等功能基础上，相比目前挖掘 机多路阀不增加体积，降低系统成本。在不增加多路阀体积基础上，实现挖掘机动臂下降回油向其它执行机构进行流量再生、斗杆复合优先和低背压回油、旁通启动无憋压独立调节、破碎、安全吊装等挖掘机全部功能，实现挖掘机低油耗、高效率、高操控性作业。
附图说明
图1为根据本发明一实施例的多路阀结构示意图；
图2为根据本发明一实施例的多路阀构型图；
图3为根据本发明一实施例的多路阀第一联工作原理图；
图4为根据本发明一实施例的多路阀第二联工作原理图；
[根据细则91更正 30.03.2023]
图5为根据本发明一实施例的多路阀第三联工作原理图；
图中：第一工作联1、第二工作联2、第三工作联3；
右行走阀101、直线行走阀102、溢流阀103、左行走阀111、回转阀110，第一溢流单向阀104、第二溢流单向阀105、泵P1回路单向阀106和112、泵P2回路单向阀107和109、回转进油单向阀108；第二上车供油油路113、第一上车供油油路114、第一中位供油油道115、第二中位供油油道116；
第二动臂阀201、第一动臂阀202、第二动臂进油单向阀203、动臂进油切断阀204、第二旁通阀205、第三动臂阀206、动臂再生单向阀207、动臂大腔补油单向阀208、动臂大腔过载补油阀209、第二动臂负载保持阀210、动臂小腔补油单向阀211、铲斗进油单向阀212、铲斗大腔过载补油阀213、铲斗小腔过载补油阀214、铲斗阀215、第一动臂进油切断控制阀216、第一动臂负载保持阀217；油道218、油道219、油道220、油道221、油道222、油道223；动臂小腔过载补油阀226；
第一斗杆阀301、第一斗杆进油单向阀302、第二斗杆进油阀303、第二斗杆进油单向阀304、第二斗杆回油阀305、斗杆大腔负载保持阀306、斗杆小腔过载补油阀307、斗杆大腔过载补油阀308、备用进油单向阀309、斗杆小腔负载保持阀310、第一旁通阀311、备用A口过载补油阀312、备用阀313、备用B口过载补油阀314、回油油道315、油道316。
具体实施方式
下面将结合本发明实施例中的附图，对本发明实施例中的技术方案进行清楚、完整地描述，显然，所描述的实施例仅仅是本发明一部分实施例，而不是全部的实施例。以下对至少一个示例性实施例的描述实际上仅仅是说明性的，决不作为对本发明及其应用或使用的任何限制。基于本发明中的实施例，本领域普通技术人员在没有作出创造性劳动前提下所获得的所有其他实施例，都属于本发明保护的范围。
除非另外具体说明，否则在这些实施例中阐述的部件和步骤的相对布置、数字表达式和数值不限制本发明的范围。同时，应当明白，为了便于描述，附图中所示出的各个部分的尺寸并不是按照实际的比例关系绘制的。对于相关领域普通技术人员已知的技术、方法和设备可能不作详细讨论，但在适当情况下，所述技术、方法和设备应当被视为授权说明书的一部分。在这里示出和讨论的所有示例中，任何具体值应被解释为仅仅是示例性的，而不是作为限制。因此，示例性实施例的其它示例可以还包括不同的值。应注意到：相似的标号和字母在下面的附图中表示类似项，因此，一旦某一项在一个附图中被定义，则在随后的附图中不需要对其进行进一步讨论。
在本发明的描述中，若干的含义是一个以上，多个的含义是两个以上，大于、小于、超过等理解为不包括本数，以上、以下、以内等理解为包括本数。如果有描述到第一、第二只是用于区分技术特征为目的，而不能理解为指示或暗示相对重要性或者隐含指明所指示的技术特征的数量或者隐含指明所指示的技术特征的先后关系。
本发明的描述中，参考术语“一个实施例”、“一些实施例”、“示意性实施例”、“示例”、“具体示例”、或“一些示例”等的描述意指结合该实施例或示例描述的具体特征、结构、材料或者 特点包含于本发明的至少一个实施例或示例中。在本说明书中，对上述术语的示意性表述不一定指的是相同的实施例或示例。而且，描述的具体特征、结构、材料或者特点可以在任何的一个或多个实施例或示例中以合适的方式结合。
实施例1
在一些实施例中，如图1所示，一种多路阀，包括第一工作联1、第二工作联2、第三工作联3；设置有第一主进油口P1、第二主进油口P2、主回油口R3；还包括：与第一主进油口P1连通的第一上车供油油路114，与第二主进油口P2连通的第二上车供油油路113，与主回油口R3连通的回油油路315，第一中位供油油道115、第二中位供油油道116；
如图1所示，本实施例所述多路阀原理包含第一工作联1、第二工作联2、第三工作联3，第一工作联1包含直线行走阀102、左行走阀111、右行走阀101、回转阀110，溢流阀103、第一溢流单向阀104、第二溢流单向阀105、泵P1回路单向阀106和112、泵P2回路单向阀107和109、回转进油单向阀108，第一工作联直线行走阀102在中间工作位时，通过节流孔102.1联通P1和P2，实现泵P1和泵P2合流；第二工作联2包含第一动臂阀202、第二动臂阀201、第三动臂阀206、铲斗阀215、第二旁通联205、动臂第一负载保持阀217、动臂第二负载保持阀210、动臂小腔补油单向阀211、动臂再生单向阀207、第一动臂进油切断阀204、第二动臂进油单向阀203、铲斗进油单向阀212；第三工作联3包含第一斗杆阀301、第二斗杆进油阀304、第二斗杆回油阀305、备用阀313、第一旁通联阀311、斗杆小腔负载保持阀310、斗杆大腔负载保持阀306、第一斗杆进油单向阀302、备用进油单向阀309。
所述第二工作联2设置在所述第一工作联1和第三工作联3之间，并固连在一起。
在一些实施例中，如图2所示，本实施例所述多路阀构型分为三块，包含第一构型块4、第二构型块5、第三构型块6，第一工作联1对应第一构型块4，第二工作联1对应第二构型块5，第三工作联1对应第三构型块6。
在一些实施例中，如图1所示，所述第一工作联1包括行走阀组和回转阀组；其中所述行走阀组包括直线行走阀102、左行走阀111、右行走阀101；所述回转阀组包括用于控制回转液压缸的回转阀110；
所述第二工作联2包括用于控制动臂液压缸的动臂阀组和用于控制铲斗液压缸的铲斗阀组；其中所述动臂阀组包括第一动臂阀202、第二动臂阀201、第三动臂阀206、动臂第一负载保持阀217、动臂第二负载保持阀210；所述铲斗阀组包括铲斗阀215；
所述第三工作联3包括用于控制斗杆液压缸的斗杆阀组和用于控制备用液压缸的备用阀组；其中所述斗杆阀组包括第一斗杆阀301、第二斗杆进油阀304、第二斗杆回油阀305、斗杆小腔负载保持阀310、斗杆大腔负载保持阀306；所述备用阀组包括备用阀313；
第一主进油口P1第一路通过第一上车供油油路114单向(单向阀106)给第一动臂阀202、铲斗阀215、第二斗杆回油阀305、备用阀313供油；
第二主进油口P2第一路经过右行走阀101，当右行走阀101的中位进油口与中位出油口导通时，依次通过回转阀110、第二动臂阀201、第一斗杆阀301的中位进、出油口形成第二中位供油油道116，同时通过右行走阀101的中位出油口单向(单向阀107)流向第二上车供油油路113；其中回转阀110、第二动臂阀201、第一斗杆阀301的中位进油口、中位出油口为常通状态；
第一主进油口P1或第二主进油口P2之一第二路经过直线行走阀102连至左行走阀111，当左行走阀111的中位进油口与中位出油口导通时，依次通过第一动臂阀202、铲斗阀215、第二斗杆回油阀305、备用阀313的中位进、出油口形成第一中位供油油道115，同时通过左行走阀111的中位出油口单向(单向阀112)流向第一上车供油油路114；其中第一动臂阀202、铲斗阀215、第二斗杆回油阀305、备用阀313的中位进油口、中位出油口为常通状态；
第一主进油口P1或第二主进油口P2之第二路路经过直线行走阀102后通过第二上车供油 油路113单向(单向阀109)给回转阀110、第二动臂阀201、第一斗杆阀301供油。
在一些实施例中，如图1所示，还包括第一旁通阀311，所述第一中位供油油道115的末端连至第一旁通阀311的进油口，第一旁通阀311的出油口连至回油油道315；
和/或，还包括第二旁通阀205，所述第二中位供油油道116末端连至第二旁通阀205的进油口，第二旁通阀205的出油口连至回油油道315；
所述第一旁通阀311、第二旁通阀205均为四位两通阀，结构相同，当处于第一工作位(自然工作位)时，进油口和出油口通过第一阻尼孔连通；当处于第二工作位时，进油口和出油口不导通；当处于第三工作位时，进油口和出油口通过第二阻尼孔导通；当处于第四工作位时，进油口和出油口直接连通。
进一步地，在一些实施例中，如图1、图3所示，所述第一工作联1还包括与主回油口R3相连通的溢流阀103，第一主进油口P1流量通过第一溢流单向阀104、溢流阀103可以实现溢流返回油箱，第二主进油口P2流量通过第二溢流单向阀105、溢流阀103可以实现溢流返回油箱；
在一些实施例中，如图3所示，为第一工作联1的工作原理，泵P1和泵P2通过直线行走阀102实现直线行走功能，直线行走阀102为一个三位四通阀，包括第一进油口、第二进油口、第一工作油口、第二工作油口，第一进油口与液压泵ⅠP1连通，第二进油口与液压泵ⅡP2连通，第一工作油口连至左行走工作油路，左行走工作油路供油给左行走阀111，第二工作油口与第二上车供油油路113(设置有单向阀109)连通；
直线行走阀102具有三个工作位：当直线行走阀102处于第一工作位(左边工作位)时，第一进油口向第一工作油口方向连通，第二进油口向第二工作油口连通；当直线行走阀102处于第二工作位(中间工作位)时，第一进油口向第二工作油口方向连通，第二进油口向第一工作油口连通，同时第一进油口与第二进油口p2通过第一节流口102.1联通，实现合流；当直线行走阀102处于第三工作位(右边工作位)时，第一进油口通过第三节流孔102.4向第二工作油口方向连通，同时第一进油口通过单向阀102.3、第二节流孔102.2向第二进油口流通，第二进油口向第一工作油口连通。
所述左行走阀111为三位六通阀，当左行走阀111处于中位时，左行走阀111的中位进油口与中位出油口导通，第一主进油口P1经左行走阀111的工作油经左行走阀111流至第一中位供油油道115，同时左行走阀111的中位出油口(通过泵P1回路单向阀112)单向流向第一上车供油油路114，左行走两个油口(油口AtL或油口BtL)通过左行走阀111的回油口与回油油路连通；当左行走阀111位于左右两个工作位时，左行走阀111的中位进油口与中位出油口不导通，液压油经左行走阀111分别实现一个左行走两个油口(油口AtL或油口BtL)进油，另一个油口(油口BtL或油口AtL)回油，进而实现左行走马达的正向和反向转动；
所述右行走阀101为三位六通阀，当右行走阀101处于中位时，右行走阀101的中位进油口与中位出油口导通，第一主进油口P1经右行走阀101的工作油经右行走阀101流至第二中位供油油道116，同时右行走阀101的中位出油口(通过泵P2回路单向阀107)单向流向第二上车供油油路113，右行走两个油口(油口Atr或油口Btr)通过右行走阀101的回油口与回油油路连通；当右行走阀101位于左右两个工作位时，右行走阀101的中位进油口与中位出油口不导通，液压油经右行走阀101分别实现一个右行走两个油口(油口Atr或油口Btr)进油，另一个油口(油口Btr或油口Atr)回油，进而实现右行走马达的正向和反向转动。
当机械行走功能不工作时，直线行走阀102工作在左边位置，第一进油口与第一工作油口连通，第二进油口与第二工作油口连通，即泵P2流量经过直线行走阀102、单向阀109，输送到第二上车供油油路113，给回转阀110、第二动臂阀201、第一斗杆阀301等执行机构供油，泵P1经过直线行走阀102给左行走阀111、第一动臂阀202、铲斗阀215、斗杆2阀305、备用阀313的第一中位供油油道115；
当铲斗阀215和备用阀313需要2个泵合流时，直线行走阀102工作在中间工作位，第一进 油口与第二工作油口连通，第二进油口与第一工作油口连通，第一进油口和第二进油口通过第一节流口102.1联通，此时P2一部分流量通过第一节流口102.1、单向阀106、第一上车供油油路114、铲斗进油单向阀212进入铲斗阀215，同时，泵P1流量经过单向阀106、第一上车供油油路114、铲斗进油单向阀212进入铲斗阀215，实现双泵合流；同理当备用阀313运动时，此时P1泵P2油通过直线行走阀102中位102.1节流孔向P1油泵供油，经过单向阀106、第一上车供油油路114、备用进油单向阀309进入备用阀313，实现备用合流功能；
当左右行走和上车同时动作时，直线行走阀102工作在右位时，第一进油口通过第三节流孔102.4与第二工作油口连通，第二进油口与第一工作油口连通，第一进油口通过单向阀102.3、第二节流孔102.2和第二进油口联通，泵P1一方面通过直线行走阀的第三节流孔102.4经过单向阀109、第二上车供油油路113，给回转阀110、第二动臂阀201、第一斗杆阀301等执行机构供油，可以向上车(回转、动臂、斗杆)供油，同时另一方面泵P1可以通过直线行走阀中单向阀102.3、第二节流孔102.2后一路向左行走阀111供油，另一路进入泵P2油路合流，向右行走阀101供油，由于第三节流孔102.4的节流作用，泵P1优先向左行走阀111和右行走阀101供油，保证行走功能优先。
在一些实施例中，如图1、图3所示，所述回转阀110为三位六通阀，具有中位和两个工作位，当回转阀110位于中位时，仅有回转阀110的中位进油口与中位出油口导通，第二上车供油油路113不向回转液压缸供油；当回转阀110位于两个工作位时，回转阀110的中位进油口与中位出油口导通，同时第二上车供油油路113分别通过回转阀110向回转液压缸两个油口(As、Bs)中一个油口供油，另一个油口通过回转阀110与回油油路连通。
如图4所示为第二工作联2的工作原理，第二工作联2包含第一动臂阀202、第二动臂阀201、第三动臂阀206、铲斗阀215、第二旁通阀205、第一动臂负载保持阀217、第二动臂负载保持阀210、动臂进油切断阀204、动臂小腔补油单向阀211、动臂再生单向阀207、第二动臂进油单向阀203、铲斗进油单向阀212。
第一动臂阀202为三位六通阀，具有中位和两个工作位，当第一动臂阀202位于中位时，仅有第一动臂阀202的中位进油口与中位出油口导通，第一中位供油油道115导通，第一上车供油油路114不向动臂液压缸供油；当第一动臂阀202位于两个工作位时，第一上车供油油路114通过第一动臂进油切断阀204、第一动臂阀202、动臂负载保持阀217分别向动臂液压缸两个油口(动臂大腔油口Ab、动臂小腔油口Bb)中一个油口供油，另一个油口通过第一动臂阀202与回油油路连通；
进一步地，第一动臂阀202进油口通过第一动臂进油切断阀204(第一动臂进油切断控制阀216用于控制第一动臂进油切断阀204的开关)与第一上车供油油路114相连通，第一动臂阀202回油口与回油油路连通；第一工作油口通过动臂负载保持阀217连至动臂大腔油口Ab，第二工作油口连至动臂小腔油口Bb，中位出油口连至铲斗阀215的中位进油口。
在一些实施例中，所述动臂大腔油口有2个，分别为动臂大腔油口Ab、Ab2。第二动臂阀201为三位六通阀，进油口通过第二动臂进油单向阀203与第二上车供油油路113相连(实现第二上车供油油路113单向向第二动臂进油单向阀203供油)，回油口与回油通道相连，中位进油口连至回转阀110的中位出油口；第一工作油口通过油道221、油道224、负载保持阀210、油道219、油道222连至动臂大腔油口Ab；第二工作油口通过油道220、油道223、负载保持阀217与动臂大腔油口Ab连通；中位出油口连至第三动臂阀206的中位进油口；第二动臂阀201具有中位和两个工作位；当第二动臂阀201位于中位时，仅有中位进油口流向中位出油口方向(第二中位供油油道116)导通；当第二动臂阀201位于右边工作位时，中位进油口流向中位出油口、进油口流向第一工作油口方向(动臂大腔Ab进油)导通，回油口与第二工作油口之间不导通；当第二动臂阀201位于左边工作位时，中位进油口流向中位出油口、第二工作油口流向回油口方向(动臂大腔Ab回油)导通，进油口与第一工作油口不导通。
第三动臂阀206为两位六通阀，回油口通过再生单向阀207单向流向第二上车供油油路113，中位出油口连至第一斗杆阀301的中位进油口(第一斗杆阀301的中位出油口经过第二旁通阀205连至回油油路)，第一工作油口通过负载保持阀210后第一路与动臂大腔油口Ab2相连通，第二路通过油道219、油道222与动臂大腔油口Ab相连通，中位出油口连至第三动臂阀206的中位进油口；
当第三动臂阀206位于右边工作位时，中位进油口向中位出油口供油，且中位进油口与进油口相连通(向第二中位供油油道116流通)；当第三动臂阀206位于左边工作位时，中位进油口向中位出油口供油，第一工作油口流向回油口方向导通(动臂大腔油口Ab、Ab2回油至第二上车供油油路113)；
还包括动臂大腔再生油路，包括动臂大腔补油单向阀208；动臂上升时，动臂大腔油口Ab通过动臂大腔补油单向阀208从回油通道进行再生补油，防止动臂吸空；
还包括动臂小腔再生油路，包括动臂小腔补油单向阀211，动臂单动作下降时，动臂小腔油口Bb通过单向阀211从回油通道进行再生补油，防止动臂吸空。
具体的，回油油路通过动臂大腔补油单向阀208后第一路与动臂大腔油口Ab2连接、第二路经油道222给动臂大腔油口Ab供油；回油油路通过动臂小腔补油单向阀211与动臂小腔油口Bb连接。
所述第二旁通阀205为四位两通阀，在第一工作位(自然工作位)205.1时，进油口和出油口通过第二旁通阀205上阻尼孔205.5联通回油油路,在发动机启动打火时，泵2由于连接回油油路处于空载状态，因此实现启动时泵2不憋压，同时由于阻尼孔205.5的作用，导致主泵2在启动初期泵压力不是很低，稍高于先导压力，使其具备通过减压阀向先导油路供油的能力，这种原理可以用于没有先导泵源的液压系统，降低系统成本；在有先导泵源的液压系统中，当系统启动完毕后，第二旁通阀芯205迅速运动到右端工作位205.4，进油口和出油口直接连通，泵2连接回油油路处于空载状态并且处于最大回油面积状态，泵2以最低压力处于怠机状态；在没有先导泵源的液压系统中，系统需要主泵提供先导压力油源时，在挖掘机工作过程中，第二旁通阀芯205运行至工作位205.2(进油口和出油口不导通)或者工作位205.3(进油口和出油口通过阻尼孔导通)，当最大手柄操作时，第二旁通阀芯205运行至工作位205.2，此时泵2和回油油路隔离，泵2全部油液提供给执行机构，提升工作效率。
铲斗阀215为四位六通阀，铲斗阀215的中位进油口与第一动臂阀202的中位出油口相连通，铲斗阀215的中位出油口连至第二斗杆回油阀305的中位进油口，进油口通过铲斗进油单向阀212连至第一上车供油油路114(实现第一上车供油油路114向铲斗进油单向阀212单向供油)，回油口连至回油油路，两个工作油口分别连接铲斗液压缸(油口Ac、油口Bc)；当铲斗阀215位于中位时，第一上车供油油路114不向第三致动器(铲斗)供油；当铲斗阀215位于三个工作位时，第一上车供油油路115分别经铲斗大腔油口Ac或铲斗小腔油口Bc为铲斗阀215的一个腔体供油，对应的另一个腔体内的液压油经铲斗小腔油口Bc或铲斗大腔油口Ac泄出再经过铲斗阀215回油至回油油路；其中铲斗阀215工作在左端第二工作位215.2，铲斗小腔AC回油经过阻尼215.1，防止铲斗吸空；在铲斗内收挖掘运行时；铲斗阀215工作在左端第一工作位215.3，铲斗小腔AC回油没有阻尼，降低挖掘作业时回油背压。
P1经过单向阀106给第一动臂阀202和铲斗阀215供油，P2经过单向阀107给第二动臂阀201供油，第三动臂阀206和第二旁通阀205并行布置。泵P2中位流量通过油道225、第二动臂阀201、第三动臂阀206后，进入第三工作联3的第一斗杆阀301、油道218、第二旁通阀205后连至回油油道R3，第二旁通阀205作用是对泵P2进行集中旁路流量调节。
动臂上升时，P1和P2双泵合流，P1流量通过动臂进油切断阀204、第一动臂阀202、动臂负载保持217进入动臂大腔油口Ab，同时P2流量通过经过单向阀203、第二动臂阀201、油道224、负载保持阀210、油道219，进入动臂大腔油口Ab；动臂上升时，动臂大腔油口Ab通过 动臂大腔补油单向阀208从回油通道R3进行再生补油，防止动臂吸空；
动臂单动作下降时，动臂小腔油口Bb进油，动臂大腔油口Ab回油，P1通过第一动臂进油切断阀204、第一动臂阀202给动臂小腔油口Bb供油，同时为防止吸空，回油油道R3流量可通过动臂小腔补油单向阀211给动臂小腔油口Bb供油；动臂大腔回油流量通过动臂大腔油口Ab、负载保持阀217后，一路通过第一动臂阀202回油，另一路通过油道223、和第二动臂阀201回油箱(第一动臂和第二动臂同时回油)；
动臂下降与斗杆复合动作时，与动臂单动作一样，一方面动臂大腔油口Ab回油一部分流量通过负载保持阀217、油道223、第一动臂阀202、第二动臂201回油箱(第一动臂和第二动臂同时回油)；第二部分油液通过油道222、油道219、负载保持阀210、第三动臂阀206、再生单向阀207后流到P2油路，给P2油路供油；因此动臂下降和斗杆复合动作时，动臂大腔回油流量不仅通过第一动臂阀202、第二动臂阀201回到油箱，同时可以通过第三动臂阀206将回油流量再生到P2油路，供给斗杆使用，动臂大腔的回油背压大小通过调节第二动臂阀201回油面积进行控制，使其背压压力高于P2压力，实现流量再生。
第二工作联2主要有5个新原理特点：
1、第二动臂阀201具有中位和两个工作位，当其在右端工作位201.2工作时，P2泵第二上车供油油路113通过单向阀203、第二动臂201、油道224、负载保持阀210、油道219、油道222连接动臂大腔油口Ab，给动臂大腔供油，油口Bb此时不能通过第二动臂阀201回油,因此第二动臂实现了动臂上升进油独立控制；
当第二动臂阀201工作在左端工作位201.1时，P2泵第二上车供油油路113不能给动臂大腔油口Ab供油，动臂大腔油口Ab可以通过第二动臂阀201回到油箱，因此在工作位201.1，第二动臂阀201实现了动臂下降回油独立控制；
2、动臂单动作下降时，动臂小腔油口Bb通过单向阀211从回油通道R3进行再生补油，防止动臂吸空；
3、动臂下降和斗杆外摆复合动作时，动臂进油通过动臂进油切断阀204切断，泵P1流量不能进入到动臂小腔油口Bb，动臂小腔油口Bb通过单向阀211进行再生补油，防止动臂吸空；同时动臂大腔油口Ab一部分油液通过负载保持阀217、油道223、第一动臂阀202、第二动臂阀201回油箱(第一动臂和第二动臂同时回油)，另一部分油液经过油道222、油道219、负载保持阀210、第三动臂206、单向阀207后再生到P2回路，与泵P2油路汇合后供给其他执行机构，实现动臂大腔回油再生利用，由于再生流量通过油道222、流道219和负载保持阀210，与第一动臂202、第二动臂阀201回油流道(负载保持阀217、流道223)是并行关系，动臂采用双负载保持阀原理和结构方案，因此油液压损小，再生利用率高；
4、第二旁通阀205采用分布结构，降低主阀体积，泵P2中位流量经过第三工作联3中第一斗杆阀301后再次返回至第二工作联2，通过油道218连接第二旁通阀205。第二旁通阀205有四个工作位，在自然工作位205.1时，P2泵通过各阀中位流道、油道218、第二旁通阀205上阻尼孔205.5联通回油油路；在发动机启动打火时，泵P2由于连接油道T处于空载状态，因此实现启动时泵P2不憋压，同时由于阻尼孔205.5的作用，导致主泵P2在启动初期泵压力不是很低，稍高于先导压力，使其具备通过减压阀向先导油路供油的能力，这种原理可以用于没有先导泵源的液压系统，降低系统成本。在有先导泵源的液压系统中，当系统启动完毕后，第二旁通阀205迅速运动到右端工作位205.4，泵P2连接回油油路处于空载状态并且处于最大回油面积状态，泵P2以最低压力处于怠机状态；在没有先导泵源的液压系统中，系统需要主泵提供先导压力油源时，在挖掘机工作过程中，第二旁通阀205运行至工作位205.2或者工作位205.3，当最大手柄操作时，第二旁通阀205运行至工作位205.2，此时泵P2和回油油路隔离，泵P2全部油液提供给执行机构，提升工作效率。
5、铲斗阀215采用四工作位原理，在铲斗内收空载运行时，铲斗阀215工作在左端第二工 作位215.2，铲斗小腔AC回油经过阻尼215.1，防止铲斗吸空；在铲斗内收挖掘运行时；铲斗阀215工作在左端第一工作位215.3，铲斗小腔AC回油没有阻尼，降低挖掘作业时回油背压。
如图5所示为第三工作联3的工作原理，第三工作联3包含第一斗杆阀301、第二斗杆进油阀303、第二斗杆回油阀305、斗杆小腔负载保持阀310、斗杆大腔负载保持阀306、第一旁通阀311、备用阀313、第一斗杆进油单向阀302、第二斗杆进油单向阀304、备用进油单向阀309。
第一斗杆阀301、第一斗杆进油单向阀302、第二斗杆进油阀303、第二斗杆进油单向阀304、第二斗杆回油阀305、斗杆大腔负载保持阀306、斗杆小腔过载补油阀307、斗杆大腔过载补油阀308、备用进油单向阀309、斗杆小腔负载保持阀310、第一旁通阀311、备用A口过载补油阀312、备用阀313、备用A口过载补油阀314、回油油道315。
第一斗杆阀301为三位六通阀，具有中位和两个工作位，当第一斗杆阀301位于中位时，仅有第二中位供油油道116导通，第二上车供油油路113不向斗杆液压缸供油；当第一斗杆阀301位于两个工作位时，第二上车供油油路113分别向斗杆液压缸(斗杆小腔油口Aa、斗杆大腔油口Ba)其中一个油口供油，斗杆液压缸另一个油口通过第一斗杆阀301与回油油路连通；其中斗杆液压缸油口与第一斗杆阀301的工作油口之间均设置有负载保持阀，进一步地，斗杆大腔油口、斗杆小腔油口与第一斗杆阀301之间分别设置有斗杆大腔负载保持阀306、斗杆小腔负载保持阀310，其中所述斗杆大腔负载保持阀306采用锥阀结构，具有零泄漏特性。
在一些实施例中，所述第一斗杆阀301的进油口通过第一斗杆进油单向阀302与第二上车供油油路113相连，回油口与回油油路相连，第一斗杆阀301的中位出油口连至第二旁通阀205，第一工作油口一路经过负载保持阀310与斗杆小腔油口Aa相连，另一路通过油道317与第二斗杆回油阀305的第一工作油口连接；第二工作油口第一路经过斗杆大腔负载保持阀306与斗杆大腔油口Ba1相连，第二路通过油道316与斗杆回油口Ba2相连。当所述第一斗杆阀301处于左边作位时，进油口流向第二工作油口导通，第一工作油口流向回油口之间设置有阻尼301.1；当所述第一斗杆阀301处于右边工作位时，进油口流向第一工作油口导通，第二工作油口直接流向回油口。
第二斗杆回油阀305为四位六通阀，第二斗杆回油阀305的中位出油口与备用阀313的中位进油口相连，第二斗杆回油阀305的进油口通过第二斗杆进油阀303、第二斗杆进油单向阀304与第一上车供油油路114相连，第二斗杆回油阀305的回油口连至回油油路；第二斗杆回油阀305的第一工作油口连接经过油道317、负载保持阀310与斗杆小腔Aa相连；第二斗杆回油阀305的第二工作油口与斗杆大腔Ba2相连通。
所述第二斗杆回油阀305具有中位和三个工作位，当第二斗杆回油阀305处于中位时，仅有第一中位供油油道115导通，第一上车供油油路114不向斗杆液压缸供油；当第二斗杆回油阀305处于第一(最左)工作位时，第二斗杆回油阀305的进油口流向第一工作油口导通，第二工作油口流向进油口导通；
在斗杆内收时，当斗杆处于重力超越负载时，控制第二斗杆回油阀305处于第二工作位(位置305.1)，进油口流向第二工作油口导通，第一工作油口通过单向阀305.4流向第二工作油口，第一工作油口通过节流孔305.3回流向回油口，此时斗杆回油受到节流孔305.3阻尼作用，回油大部分通过单向阀305.4再生到斗杆大腔油口Ba，实现斗杆快速运动和防止斗杆内收吸空；
当斗杆进行挖掘处于阻力负载时，控制第二斗杆回油阀305处于第三工作位位置305.2，进油口流向第二工作油口导通，第一工作油口通过单向阀流向第二工作油口，第一工作油口直接回流向回油口，此时斗杆回油没有阻尼限制，回油面积较大，挖掘背压较小。
泵P1中位流量通过油道318、第二斗杆回油阀305、备用阀313后经过第一旁通阀311连至回油通道315，第一旁通阀311作用是对泵P1进行集中旁路流量调节。
斗杆内收时，P1油液经过第二斗杆进油阀303、单向阀304、第二斗杆回油阀305(油液只是通过，不进行控制)、油道316、负载保持阀306向斗杆大腔Ba1供油；P2油液经过单向阀 302、第一斗杆阀301、油道316、负载保持阀306向斗杆大腔Ba1供油；斗杆小腔Aa回油油液一部分经过负载保持阀310、油道317、第一斗杆阀301及阻尼301.1回油，另外一部分经过负载保持阀310、油道317、第二斗杆阀回油阀305回油，第二斗杆回油阀305具有流量再生功能，当斗杆内收处于重力超越负载时，第二斗杆回油阀工作在305.1位置，实现斗杆大腔油液再生，当斗杆内收处于阻力负载时，第二斗杆回油阀工作在305.2位置，增大回油面积，减少挖掘压力损失。
斗杆外摆时，P1油液经过第二斗杆进油阀303、单向阀304、第二斗杆回油阀305(油液只是通过，不进行控制)、油道317、负载保持阀310向斗杆小腔Aa供油，P2油液经过单向阀302、第一斗杆阀301、油道317、负载保持阀310向斗杆小腔Aa供油。斗杆大腔Ba1回油通过负载保持阀306、油道316、第一斗杆阀301与第二斗杆回油阀305回油。
所述备用阀313为三位六通阀，备用阀313的中位出油口连至第一旁通阀311的进油口，第一旁通阀311的出油口连至总回油油道；第一上车供油油路114(通过备用进油单向阀309)单向给进油口供油，回油口连至回油油路，两个工作油口分别连接备用液压缸油口Ao、油口Bo；当备用阀313位于中位时，仅有第一中位供油油道115导通，第一上车供油油路114不向备用液压缸供油；当备用阀313位于两个工作位时，第一上车供油油路115分别通过备用阀313向备用液压缸两个油口(Ao、Bo)中一个油口供油，另一个油口通过备用阀313与回油油路连通。
第一旁通阀311与第二旁通阀205结构相同，工作原理与第二旁通阀205类似(不再累述)，实现泵P1启动时不憋压。
第三工作联3主要有3个新原理特点：
1、第一旁通阀311工作原理与第二旁通阀205类似，实现泵P1启动时不憋压。
2、采用第二斗杆进油阀303和第二斗杆回油阀305，实现斗杆在泵P1侧进油和回油独立控制；第二斗杆回油阀305采用四工作位原理，在斗杆内收时，由于斗杆处于超越负载状态，第二斗杆回油阀305运行在工作位305.1上，斗杆小腔Aa回油经过阻尼305.3，提升斗杆小腔回油背压，防止吸空；当斗杆内收时挖掘时，第二斗杆回油阀305运行在工作位305.2上，斗杆小腔Aa回油直接回油箱，降低挖掘时回油背压。第一斗杆阀301内收时，斗杆小腔Aa回油经过阻尼孔301.1，与第二斗杆回油阀305共同决定斗杆小腔压力状态，防止斗杆内收吸空或者回油背压过大。
3、备用阀313放置在第三工作联3，用于备用连接破碎执行机构。
4、斗杆油缸油口大腔Ba1处采用负载保持阀306结构和原理，因此在斗杆处于内收位置(斗杆不运动)同时动臂进行上升进行吊装作业时，斗杆油缸大腔Ba1不能通过负载保持阀306返回第一斗杆阀301和第二斗杆回油阀303，负载保持阀306采用锥阀结构，具有零泄漏特性，因此可以实现斗杆无下坠安全吊装。
另外，本实施例的一种多路阀，采用电比例控制方式，凡采用更换控制方式，如液压控制方式、机械控制方式等形式的等效变换实现的相同功能的多路阀，均落在本发明专利的保护范围；本申请A/B负载回路设置过载补油阀对负载回路进行压力限制和防止吸空，凡采用更换过载补油阀，如换成溢流阀、堵头等形式对本发明设计进行的简化，也属于本申请的保护范围。
实施例2
本实施例提供一种液压系统，包括实施例1所述的多路阀。
实施例3
本实施例提供一种挖掘机，包括实施例2所述的液压系统。
在本申请的描述中，需要理解的是，术语“中心”、“纵向”、“横向”、“前”、“后”、“左”、“右”、“竖直”、“水平”、“顶”、“底”、“内”、“外”等指示的方位或位置关系为基于附图所示的 方位或位置关系，仅是为便于描述本实用新型和简化描述，而不是指示或暗指所指的装置或元件必须具有特定的方位、为特定的方位构造和操作，因而不能理解为对本实用新型保护内容的限制。
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，在不脱离本发明原理的前提下，还可以做出若干改进和润饰，这些改进和润饰也应视为本发明的保护范围。

Claims (12)

  1. 一种多路阀，其特征在于，包括第一工作联、第二工作联、第三工作联；第一主进油口、第二主进油口、主回油口；还包括：与第一主进油口连通的第一上车供油油路，与第二主进油口连通的第二上车供油油路，与主回油口连通的回油油路，第一中位供油油道、第二中位供油油道；所述第二工作联设置在所述第一工作联和第三工作联之间；
    所述第一工作联包括行走阀组和回转阀组；其中所述行走阀组包括直线行走阀、左行走阀、右行走阀；所述回转阀组包括用于控制回转液压缸的回转阀；
    所述第二工作联包括用于控制动臂液压缸的动臂阀组和用于控制铲斗液压缸的铲斗阀组；其中所述动臂阀组包括第一动臂阀、第二动臂阀、第三动臂阀、动臂第一负载保持阀、动臂第二负载保持阀；所述铲斗阀组包括铲斗阀；
    所述第三工作联包括用于控制斗杆液压缸的斗杆阀组和用于控制备用液压缸的备用阀组；其中所述斗杆阀组包括第一斗杆阀、第二斗杆进油阀、第二斗杆回油阀、斗杆小腔负载保持阀、斗杆大腔负载保持阀；所述备用阀组包括备用阀；
    第一主进油口第一路通过第一上车供油油路单向给第一动臂阀、铲斗阀、第二斗杆回油阀、备用阀供油；
    第二主进油口第一路经过右行走阀，当右行走阀的中位进油口与中位出油口导通时，依次通过回转阀、第二动臂阀、第一斗杆阀的中位进、出油口形成第二中位供油油道，同时通过右行走阀的中位出油口单向流向第二上车供油油路；其中回转阀、第二动臂阀、第一斗杆阀的中位进油口、中位出油口为常通状态；
    第一主进油口或第二主进油口之一第二路经过直线行走阀连至左行走阀，当左行走阀的中位进油口与中位出油口导通时，依次通过第一动臂阀、铲斗阀、第二斗杆回油阀、备用阀的中位进、出油口形成第一中位供油油道，同时通过左行走阀的中位出油口单向流向第一上车供油油路；其中第一动臂阀、铲斗阀、第二斗杆回油阀、备用阀的中位进油口、中位出油口为常通状态；
    第一主进油口或第二主进油口之第二路路经过直线行走阀后通过第二上车供油油路单向给回转阀、第二动臂阀、第一斗杆阀供油。
  2. 根据权利要求1所述的多路阀，其特征在于，还包括第一旁通阀，所述第一中位供油油道的末端连至第一旁通阀的进油口，第一旁通阀的出油口连至回油油道；
    还包括第二旁通阀，所述第二中位供油油道末端连至第二旁通阀的进油口，第二旁通阀的出油口连至回油油道；
    所述第一旁通阀、第二旁通阀均为四位两通阀，结构相同，当处于第一工作位时，进油口和出油口通过第一阻尼孔连通；当处于第二工作位时，进油口和出油口不导通；当处于第三工作位时，进油口和出油口通过第二阻尼孔导通；当处于第四工作位时，进油口和出油口直接连通。
  3. 根据权利要求1所述的多路阀，其特征在于，所述第一工作联还包括与主回油口相连通的溢流阀，所述第一主进油口通过第一溢流单向阀连至溢流阀的进油口；第二主进油口通过第二溢流单向阀连至溢流阀的进油口。
  4. 根据权利要求1所述的多路阀，其特征在于，所述直线行走阀为一个三位四通阀，包括第一进油口、第二进油口、第一工作油口、第二工作油口，第一进油口与第一主进油口连通，第二进油口与第二主进油口连通，第一工作油口连至左行走工作油路，左行走工作油路供油给左行走阀，第二工作油口单向给第二上车供油油路供油；
    直线行走阀具有三个工作位：当直线行走阀处于第一工作位时，第一进油口向第一工作油口方向连通，第二进油口向第二工作油口连通；当直线行走阀处于第二工作位时，第一进油口向第二工作油口方向连通，第二进油口向第一工作油口连通，同时第一进油口与第二进油口通过第一节流口联通，实现合流；当直线行走阀处于第三工作位时，第一进油口通过第 三节流孔向第二工作油口方向连通，同时第一进油口通过单向阀、第二节流孔向第二进油口流通，第二进油口向第一工作油口连通；
    所述左行走阀为三位六通阀，当左行走阀处于中位时，左行走阀的中位进油口与中位出油口导通，第一主进油口经左行走阀的工作油经左行走阀流至第一中位供油油道，同时左行走阀的中位出油口单向流向第一上车供油油路，左行走两个油口通过左行走阀的回油口与回油油路连通；当左行走阀位于左右两个工作位时，左行走阀的中位进油口与中位出油口不导通，液压油经左行走阀分别实现一个左行走两个油口进油，另一个油口回油，进而实现左行走马达的正向和反向转动；
    所述右行走阀为三位六通阀，当右行走阀处于中位时，右行走阀的中位进油口与中位出油口导通，第一主进油口经右行走阀的工作油经右行走阀流至第二中位供油油道，同时右行走阀的中位出油口单向流向第二上车供油油路，右行走两个油口通过右行走阀的回油口与回油油路连通；当右行走阀位于左右两个工作位时，右行走阀的中位进油口与中位出油口不导通，液压油经右行走阀分别实现一个右行走两个油口进油，另一个油口回油，进而实现右行走马达的正向和反向转动。
  5. 根据权利要求1所述的多路阀，其特征在于，所述回转阀为三位六通阀，具有中位和两个工作位，当回转阀位于中位时，仅有回转阀的中位进油口与中位出油口导通，第二上车供油油路不向回转液压缸供油；当回转阀位于两个工作位时，回转阀的中位进油口与中位出油口导通，同时第二上车供油油路分别通过回转阀向回转液压缸两个油口中一个油口供油，另一个油口通过回转阀与回油油路连通。
  6. 根据权利要求1所述的多路阀，其特征在于，所述第一动臂阀为三位六通阀，具有中位和两个工作位，当第一动臂阀位于中位时，仅有第一动臂阀的中位进油口与中位出油口导通，第一中位供油油道导通，第一上车供油油路不向动臂液压缸供油；当第一动臂阀位于两个工作位时，第一上车供油油路通过第一动臂进油切断阀、第一动臂阀、动臂负载保持阀分别向动臂液压缸两个油口中一个油口供油，另一个油口通过第一动臂阀与回油油路连通；第一动臂阀进油口通过第一动臂进油切断阀与第一上车供油油路相连通，第一动臂阀回油口与回油油路连通；第一工作油口通过动臂负载保持阀连至动臂大腔油口，第二工作油口连至动臂小腔油口，中位出油口连至铲斗阀的中位进油口；
    第二动臂阀为三位六通阀，进油口通过第二动臂进油单向阀与第二上车供油油路相连，回油口与回油通道相连，中位进油口连至回转阀的中位出油口；第一工作油口通过负载保持阀连至动臂大腔油口；第二工作油口通过负载保持阀与动臂大腔油口连通；中位出油口连至第三动臂阀的中位进油口；第二动臂阀具有中位和两个工作位；当第二动臂阀位于中位时，仅有中位进油口流向中位出油口方向导通；当第二动臂阀位于右边工作位时，进油口流向第一工作油口方向导通，回油口与第二工作油口之间不导通；当第二动臂阀位于左边工作位时，第二工作油口流向回油口方向导通，进油口与第一工作油口不导通；
    第三动臂阀为两位六通阀，回油口通过再生单向阀单向流向第二上车供油油路，第一工作油口通过负载保持阀与动臂大腔油口相连通；当第三动臂阀位于右边工作位时，仅有中位进油口流向中位出油口方向；当第三动臂阀位于左边工作位时，工作油口流向回油口方向导通，动臂大腔油口再生油至第二上车供油油路；
    还包括动臂大腔再生油路，包括动臂大腔补油单向阀；动臂上升时，动臂大腔油口通过动臂大腔补油单向阀从回油通道进行再生补油，防止动臂吸空；
    还包括动臂小腔再生油路，包括动臂小腔补油单向阀，动臂单动作下降时，动臂小腔油口通过单向阀从回油通道进行再生补油，防止动臂吸空。
  7. 根据权利要求1所述的多路阀，其特征在于，所述铲斗阀为四位六通阀，进油口通过铲斗进油单向阀连至第一上车供油油路，回油口连至回油油路，两个工作油口连接铲斗液压缸 油口；具有一个中位和三个工作位；
    当铲斗阀位于中位时，第一上车供油油路不向铲斗液压缸供油；当铲斗阀位于三个工作位时，第一上车供油油路分别经铲斗大腔油口或铲斗小腔油口为铲斗阀的一个腔体供油，对应的另一个腔体内的液压油经铲斗小腔油口或铲斗大腔油口泄出再经过铲斗阀回油至回油油路；其中铲斗阀工作在左端第二工作位，铲斗小腔油口回油经过阻尼，防止铲斗吸空；在铲斗内收挖掘运行时；铲斗阀工作在左端第一工作位，铲斗小腔油口回油没有阻尼，降低挖掘作业时回油背压。
  8. 根据权利要求1所述的多路阀，其特征在于，所述第一斗杆阀为三位六通阀，具有中位和两个工作位，当第一斗杆阀位于中位时，仅有第二中位供油油道导通，第二上车供油油路不向第四致动器供油；当第一斗杆阀位于两个工作位时，第二上车供油油路分别向斗杆液压缸其中一个油口供油，斗杆液压缸另一个油口通过第一斗杆阀与回油油路连通；其中斗杆液压缸油口与第一斗杆阀的工作油口之间均设置有负载保持阀，其中负载保持阀采用锥阀结构，具有零泄漏特性；所述第一斗杆阀的进油口通过第一斗杆进油单向阀与第二上车供油油路相连，回油口与回油油路相连，第一斗杆阀的中位出油口连至第二旁通阀，第一工作油口经过斗杆小腔负载保持阀与斗杆小腔油口相连，第二工作油口经过斗杆大腔负载保持阀与斗杆大腔油口，当所述第一斗杆阀处于左边作位时，进油口流向第二工作油口导通，第一工作油口流向回油口之间设置有阻尼；当所述第一斗杆阀处于右边工作位时，进油口流向第一工作油口导通，第二工作油口直接流向回油口；
    所述第二斗杆回油阀为四位六通阀，第二斗杆回油阀的中位出油口与备用阀的中位进油口相连，第二斗杆回油阀的进油口通过第二斗杆进油单向阀、第二斗杆进油阀与第一上车供油油路相连，第二斗杆回油阀的回油口连至回油油路；第二斗杆回油阀的第一工作油口经过负载保持阀与斗杆小腔油口相连；第二斗杆回油阀的第二工作油口与斗杆大腔相连通；所述第二斗杆回油阀具有中位和三个工作位，当第二斗杆回油阀处于中位时，仅有第一中位供油油道导通，第一上车供油油路不向斗杆液压缸供油；当第二斗杆回油阀处于第一工作位时，第二斗杆回油阀的进油口流向第一工作油口导通，第二工作油口流向进油口导通；
    在斗杆内收时，当斗杆处于重力超越负载时，控制第二斗杆回油阀处于第二工作位，进油口流向第二工作油口导通，第一工作油口通过单向阀流向第二工作油口，第一工作油口通过节流孔回流向回油口，此时斗杆回油受到节流孔阻尼作用，回油大部分通过单向阀再生到斗杆大腔油口，实现斗杆快速运动和防止斗杆内收吸空；
    当斗杆进行挖掘处于阻力负载时，控制第二斗杆回油阀处于第三工作位位置，进油口流向第二工作油口导通，第一工作油口通过单向阀流向第二工作油口，第一工作油口直接回流向回油口，此时斗杆回油没有阻尼限制。
  9. 根据权利要求1所述的多路阀，其特征在于，所述备用阀为三位六通阀，备用阀的中位出油口连至第一旁通阀的进油口，第一旁通阀的出油口连至总回油油道；第一上车供油油路单向给进油口供油，回油口连至回油油路，两个工作油口分别连接备用液压缸油口；当备用阀位于中位时，仅有第一中位供油油道导通，第一上车供油油路不向备用液压缸供油；当备用阀位于两个工作位时，第一上车供油油路分别通过备用阀向备用液压缸两个油口中一个油口供油，另一个油口通过备用阀与回油油路连通。
  10. 根据权利要求1所述的多路阀，其特征在于，还包括过载补油阀，动臂液压缸、铲斗液压缸、斗杆液压缸、备用液压缸两个油口与回油油路之间均设置有过载补油阀。
  11. 一种液压系统，其特征在于，包括权利要求1-10任一项所述的多路阀。
  12. 一种挖掘机，其特征在于，包括权利要求11所述的液压系统。
PCT/CN2022/142657 2022-08-29 2022-12-28 一种多路阀、液压系统及挖掘机 WO2024045445A1 (zh)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU2022436043A AU2022436043A1 (en) 2022-08-29 2022-12-28 Multi-way valve, hydraulic system and excavator

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN202211039781.6 2022-08-29
CN202211039781.6A CN115341615B (zh) 2022-08-29 2022-08-29 一种多路阀、液压系统及挖掘机

Publications (1)

Publication Number Publication Date
WO2024045445A1 true WO2024045445A1 (zh) 2024-03-07

Family

ID=83954674

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2022/142657 WO2024045445A1 (zh) 2022-08-29 2022-12-28 一种多路阀、液压系统及挖掘机

Country Status (3)

Country Link
CN (1) CN115341615B (zh)
AU (1) AU2022436043A1 (zh)
WO (1) WO2024045445A1 (zh)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN115341615B (zh) * 2022-08-29 2023-09-01 江苏汇智高端工程机械创新中心有限公司 一种多路阀、液压系统及挖掘机
CN116877519B (zh) * 2023-06-30 2024-06-14 江苏汇智高端工程机械创新中心有限公司 一种重载矿用挖掘机液压主阀及系统

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010047984A (ja) * 2008-08-21 2010-03-04 Sumitomo (Shi) Construction Machinery Co Ltd 油圧ショベルの油圧回路
CN204590113U (zh) * 2015-04-21 2015-08-26 山河智能装备股份有限公司 中型液压挖掘机多路阀组
CN209414291U (zh) * 2018-12-11 2019-09-20 烟台艾迪液压科技有限公司 一种挖掘机用新型整体多路阀
CN211898661U (zh) * 2017-02-27 2020-11-10 山东常林机械集团股份有限公司 一种用于液压挖掘机的多路控制阀
CN115341615A (zh) * 2022-08-29 2022-11-15 江苏汇智高端工程机械创新中心有限公司 一种多路阀、液压系统及挖掘机

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05187042A (ja) * 1992-01-08 1993-07-27 Yutani Heavy Ind Ltd 建設機械の油圧回路
CN102518612B (zh) * 2011-12-08 2014-12-03 上海三一重机有限公司 一种液压挖掘机斗杆再生功能实现装置
CN108316389B (zh) * 2018-04-16 2023-09-22 福建晋工机械有限公司 一种轮式挖掘机用多路阀
CN211973647U (zh) * 2020-01-20 2020-11-20 广西玉柴重工有限公司 一种双泵共轨多路阀液压系统
CN113882459B (zh) * 2021-09-30 2023-02-17 徐州徐工挖掘机械有限公司 挖掘机能量回收系统及挖掘机

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010047984A (ja) * 2008-08-21 2010-03-04 Sumitomo (Shi) Construction Machinery Co Ltd 油圧ショベルの油圧回路
CN204590113U (zh) * 2015-04-21 2015-08-26 山河智能装备股份有限公司 中型液压挖掘机多路阀组
CN211898661U (zh) * 2017-02-27 2020-11-10 山东常林机械集团股份有限公司 一种用于液压挖掘机的多路控制阀
CN209414291U (zh) * 2018-12-11 2019-09-20 烟台艾迪液压科技有限公司 一种挖掘机用新型整体多路阀
CN115341615A (zh) * 2022-08-29 2022-11-15 江苏汇智高端工程机械创新中心有限公司 一种多路阀、液压系统及挖掘机

Also Published As

Publication number Publication date
AU2022436043A1 (en) 2024-03-14
CN115341615A (zh) 2022-11-15
CN115341615B (zh) 2023-09-01

Similar Documents

Publication Publication Date Title
WO2024045445A1 (zh) 一种多路阀、液压系统及挖掘机
CN105090154B (zh) 一种卸荷阀块、开闭芯液压系统及工程机械
JP5574375B2 (ja) エネルギ回生用制御回路および作業機械
CN110700337B (zh) 一种挖掘机动臂节能控制系统及控制方法
CN102887447B (zh) 变幅液压缸液压控制回路、起重机及变幅控制方法
CN101775822B (zh) 挖掘机动臂下降液压控制回路
US20220289542A1 (en) Fork leveling system and method, and telescopic boom forklift
WO2012094991A1 (zh) 一种提高挖掘机挖掘操纵特性和平整作业特性的装置
WO2021031639A1 (zh) 一种卷扬势能实时回收利用系统及其控制方法
CN113882459B (zh) 挖掘机能量回收系统及挖掘机
WO2021057727A1 (zh) 一种再生控制液压系统
CN117627991A (zh) 多路阀、液压系统及挖掘机
CN205776443U (zh) 挖掘机动臂势能分级回收及释放装置
WO2024113770A1 (zh) 液压控制系统及作业机械
CN202954380U (zh) 一种液压挖掘机的斗杆液压控制回路
CN210829927U (zh) 一种液压控制系统
CN104912137A (zh) 具有能量回馈功能的挖掘机液压系统
WO2014000376A1 (zh) 挖掘机液压系统、挖掘机及挖掘机液压系统的控制方法
CN211312642U (zh) 一种挖掘机动臂节能控制系统
CN211778291U (zh) 一种挖掘机多路阀
CN113928981A (zh) 工程车辆及其液压驱动系统
CN114542540A (zh) 流量再生液压系统和工程机械
CN111442008A (zh) 一种用于控制高空作业车伸臂的差动平衡阀
CN211898661U (zh) 一种用于液压挖掘机的多路控制阀
CN218266573U (zh) 负载口独立控制系统及工程机械

Legal Events

Date Code Title Description
WWE Wipo information: entry into national phase

Ref document number: 2022436043

Country of ref document: AU

ENP Entry into the national phase

Ref document number: 2022436043

Country of ref document: AU

Date of ref document: 20221228

Kind code of ref document: A

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

Ref document number: 22957255

Country of ref document: EP

Kind code of ref document: A1