WO2013033884A1 - Concrete pumping equipment and hydraulic system thereof - Google Patents

Concrete pumping equipment and hydraulic system thereof Download PDF

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Publication number
WO2013033884A1
WO2013033884A1 PCT/CN2011/079340 CN2011079340W WO2013033884A1 WO 2013033884 A1 WO2013033884 A1 WO 2013033884A1 CN 2011079340 W CN2011079340 W CN 2011079340W WO 2013033884 A1 WO2013033884 A1 WO 2013033884A1
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WO
WIPO (PCT)
Prior art keywords
pump
valve
hydraulic
hydraulic system
actuator
Prior art date
Application number
PCT/CN2011/079340
Other languages
French (fr)
Chinese (zh)
Inventor
万梁
Original Assignee
长沙中联重工科技发展股份有限公司
湖南中联重科专用车有限责任公司
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Application filed by 长沙中联重工科技发展股份有限公司, 湖南中联重科专用车有限责任公司 filed Critical 长沙中联重工科技发展股份有限公司
Priority to PCT/CN2011/079340 priority Critical patent/WO2013033884A1/en
Publication of WO2013033884A1 publication Critical patent/WO2013033884A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B15/00—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04B15/02—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts the fluids being viscous or non-homogeneous
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • F15B2211/20584—Combinations of pumps with high and low capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30585—Assemblies of multiple valves having a single valve for multiple output members

Definitions

  • the present invention relates to the field of hydraulic control, and more particularly to a concrete pumping apparatus and a hydraulic system thereof.
  • the hydraulic system of a prior art concrete pumping apparatus includes a pumping subsystem, a distribution subsystem, a mixing and cleaning subsystem, and a boom leg subsystem, each of which drives a different at least one actuator.
  • each subsystem can work at the same time, or can work alone, without being affected by each other; the other is that the pumping subsystem and the distribution subsystem use the same oil pump, but other subsystems are mutually separate.
  • power components ie pumps
  • control components such as valves
  • actuators such as cylinders, motors, etc.
  • auxiliary Components such as filters, etc.
  • the present invention is directed to a concrete pumping apparatus and a hydraulic system thereof to solve the problems of low efficiency, waste of energy and capability of the prior art hydraulic system.
  • a hydraulic system comprising: a first hydraulic subsystem, the first hydraulic subsystem including a first pump and at least one first actuator, a first multi-way reversing valve is disposed between the pump and the first actuator, the first multi-way reversing valve includes at least one first station and at least one second station; the second hydraulic subsystem, the second hydraulic pressure
  • the subsystem includes a second pump and at least one second actuator, the second pump driving the at least one second actuator; the first pump drives the at least one first actuator through the first station, the first pump passes the second station The second pump together drives at least one second actuator.
  • the first hydraulic subsystem further includes a second multi-way reversing valve, and the at least one first actuator is coupled to the first multi-way reversing valve through the second multi-way reversing valve. Step, the second hydraulic subsystem passes the one-way valve, or the shut-off valve, or the reversing valve and the first multi-way reversing valve
  • the first multiplex valve includes a plurality of first valve plates and a plurality of second valve plates, each of the first valve plates includes a first station and a second station, and a portion of the first actuator and the first The valve plate is connected, and the other part of the first actuator is connected to the second valve piece.
  • the second hydraulic subsystem is connected to each of the first valves through a one-way valve, or a shut-off valve, or a reversing valve
  • the hydraulic system further includes a working condition adaptive controller for controlling each first valve to switch from the first station to the second station according to working conditions, and for controlling the opening degree of each of the first valves the size of.
  • the working condition adaptive controller controls each of the first multi-way reversing valves to be in the first station.
  • the condition adaptive controller controls the first Each of the multiplexed valves is in the first station.
  • a concrete pumping apparatus includes the hydraulic system described above. Further, the first hydraulic subsystem in the hydraulic system is the boom leg hydraulic subsystem, and the second hydraulic subsystem in the hydraulic system is the pumping hydraulic subsystem. Further, the hydraulic system controls the commutation of the first multi-way reversing valve of the hydraulic system based on the speed requirements of the concrete pumping equipment for its boom and/or the speed requirements of the pumping.
  • Fig. 1 is a schematic view showing a hydraulic principle of a hydraulic system in a first preferred embodiment
  • Fig. 2 is a schematic view showing a hydraulic principle of a hydraulic system in a second preferred embodiment
  • Fig. 3 schematically shows a control flow chart of a condition adaptive controller in a hydraulic system.
  • a hydraulic system comprising: a first hydraulic subsystem and a second hydraulic subsystem; wherein the first hydraulic subsystem includes a first pump and at least one first actuator, a first multiplex valve is disposed between the pump and the at least one first actuator, the first multiplex valve includes at least one first station and at least one second station; and the second hydraulic subsystem includes a second pump and at least one second actuator, the second pump driving the at least one second actuator; the first pump drives the at least one first actuator through the first station, and the first pump passes the second station together with the second pump Cooperating at least one second actuator.
  • Fig. 1 shows a hydraulic principle diagram of the above hydraulic system in the first preferred embodiment. As shown in FIG.
  • the hydraulic system includes a first hydraulic subsystem and a second hydraulic subsystem; wherein the first hydraulic subsystem includes a first pump 5 and at least one first actuator 6, the first pump 5 and at least one A first multi-way reversing valve 1 is disposed between the first actuators 6, and the first multi-way reversing valve 1 includes a first station (ie, a left position) and a second station (ie, a right position);
  • the subsystem comprises a second pump 4 and at least one second actuator 7, the second pump 4 driving at least one second actuator 7; the first pump 5 drives at least one first actuator 6, a first pump, through a first station 5 through the first The second station together with the second pump 4 drives at least one second actuator 7.
  • the first hydraulic subsystem further comprises a second multiplex valve 3, and the at least one first actuator 6 is connected to the first multiplex valve 1 via the second directional valve 3.
  • the first multi-way valve 1 is kept at the first station, and at this time, the pressure oil of the first pump 5 directly enters the first actuator through the first multi-way valve 1, and The pressure oil of the second pump directly drives the second actuator to work, that is, the first hydraulic subsystem and the second hydraulic subsystem operate independently, without any influence on each other; when all the first executions in the first hydraulic subsystem When the mechanism is in the stop state, the first actuator 6 no longer needs the first pump 5 to supply the pressure oil.
  • the first multiplex valve 1 can be operated at the second station, and the pressure of the first pump 5 is made.
  • the oil enters the second hydraulic subsystem through the first multi-way reversing valve 1.
  • the first pump 5 and the second pump 4 are in a confluent state, thereby improving the hydraulic system and reducing energy consumption.
  • the person skilled in the art can implement the first hydraulic subsystem and the second hydraulic subsystem in various ways (such as a one-way valve, or a shut-off valve, or a reversing valve).
  • the second hydraulic subsystem can be connected to the first multi-way reversing valve 1 through the one-way valve 2, so that when the first When the road reversing valve is in the first position, the pressure oil of the second hydraulic system does not flow into the tank through the first multi-way reversing valve 1.
  • the hydraulic system can only give the second hydraulic pressure if all of the first actuators in the first hydraulic subsystem are in a stop operation.
  • the subsystem provides additional pressure oil, but in most cases only a portion of the first actuator in at least one of the first hydraulic subsystems moves, or the speed of operation is slow, therefore, the first pump 5 Not in full load state, that is, there is still a waste of system capacity.
  • the present invention also provides a second preferred embodiment as shown in Figure 2. As shown in FIG. 1
  • the hydraulic system includes a first hydraulic subsystem and a second hydraulic subsystem; wherein the first hydraulic subsystem includes a first pump 5 and at least one first actuator 6, the first pump 5 and at least one A first multiplex valve 1 is disposed between the first actuators 6, and the first multiplex valve 1 includes at least one first station (ie, a lower position) and at least one second station (ie, a higher position);
  • the second hydraulic system comprises a second pump 4 and at least one second actuator 7, the second pump 4 drives at least one second actuator 7; the first pump 5 drives at least one first actuator 6 through the first station, A pump 5 drives the at least one second actuator 7 together with the second pump 4 through the second station.
  • the first multiplex valve 1 has a plurality of first valve plates ⁇ and a plurality of second valve plates ( Not shown), each of the first valve discs includes a first station and a second station, and a part of the first actuator 6 is connected to the first valve disc, and the other part of the first actuator 6 is Second valve connection (note that the first valve and the second valve may There is a different structure, that is, the second valve piece may not have the second station in the embodiment, that is, the other part of the first actuator connected to the second valve piece is not connected to the second hydraulic system) Therefore, the control of the different first actuators can be achieved separately by the different first valve flaps.
  • each of the first valve spools 1 of the first multiplex valve 1 can be separately controlled such that a part of the first actuator connected to the first valve plate works normally and the other portion stops working, further
  • the first valve piece connected to the other part of the first actuator that is stopped working is in the second station, so that the second hydraulic system can be supplied with pressurized oil, and at the same time, the part of the first actuator that is normally operated is connected
  • the first valve is in the first position so that it can continue to move without being affected. It can be seen that the hydraulic system of FIG. 2 does not need to have all of the first actuators in a stopped state to supply pressurized oil to the second hydraulic subsystem, thereby improving the efficiency of the entire hydraulic system and reducing energy consumption.
  • first valve disc When the first valve disc is in the first position, a person skilled in the art can implement the first hydraulic subsystem and the second hydraulic subsystem in various manners (such as a one-way valve, or a shut-off valve, or a reversing valve). Isolation, so that the two work independently, without any influence on each other.
  • the second hydraulic subsystem can be made to pass through the one-way valve 2 with the first multiplex valve 1 or each first valve ⁇ connection.
  • the present invention also needs to consider the switching timing and opening degree of the first multi-way reversing valve 1 or each of the first valve discs, that is, when the first pump 5 supplies the pressure oil to the second hydraulic subsystem, And how much pressure oil is supplied, which must depend on the actual working conditions, that is, the following two conditions must be met: (1) The first pump 5 is used to supply the pressure oil to the second hydraulic subsystem, and the first hydraulic system must not be affected. The speed of movement of each of the first actuators; (2) The first pump 5 supplies pressure oil to the second hydraulic subsystem only if the second hydraulic subsystem fails to meet the performance specifications required by the operator.
  • the hydraulic system further includes a condition adaptive controller for controlling each first valve to switch from the first station to the second station according to operating conditions, and for controlling each of the first valves The size of the opening of the piece.
  • a condition adaptive controller for controlling each first valve to switch from the first station to the second station according to operating conditions, and for controlling each of the first valves The size of the opening of the piece.
  • the condition adaptive controller controls each of the first multi-way reversing valves to be in the first station.
  • the condition adaptive controller controls Each of the first multiplex valve is in the first station.
  • the condition adaptive controller controls the first At least one of the plurality of directional valves is in the second station.
  • the second aspect of the present invention also provides a concrete pumping apparatus comprising the hydraulic system of each of the above embodiments.
  • the first hydraulic subsystem in the hydraulic system is the boom leg hydraulic subsystem and the second hydraulic subsystem in the hydraulic system is the pumping hydraulic subsystem.
  • the hydraulic system controls the commutation of the first multi-way reversing valve of the hydraulic system in accordance with the speed requirements of the concrete pumping equipment for its boom (and/or legs) and/or the speed requirements of the pumping.
  • the first pump 5 first ensures the movement of the boom legs in the boom leg hydraulic system, so when there is an actuator movement in the boom leg hydraulic subsystem, the first need to be made.
  • the multi-way reversing valve 1 operates in the first position (ie, the left position).
  • the pressure oil of the first pump 5 enters the boom leg hydraulic system through the first multi-way reversing valve 1 and can pass through the one-way
  • the valve 2 is used to restrict the pressure oil of the second pump 4 from entering the fuel tank through the first multi-way reversing valve 1.
  • the pumping hydraulic system works independently with the boom leg hydraulic system, and has no influence on each other;
  • the first multiplex valve 1 can be operated at the second station (ie, the right position).
  • the pressure oil of the first pump 5 passes through the first stage.
  • a multi-way reversing valve 1 and a check valve 2 enter the pumping hydraulic subsystem, that is, the second pump 4 and the first pump 5 are in a confluent state at this time, thereby improving the pumping capacity of the concrete pumping device and the hydraulic system. Efficiency, and increase the load rate of the engine of the concrete pumping equipment, reducing energy consumption .
  • the pumping hydraulic subsystem is connected to the boom leg hydraulic system through the first multi-way reversing valve 1 and the one-way valve 2, wherein the second pump 4 is a pumping hydraulic subsystem.
  • the first pump 5 is an oil pump of the hydraulic system of the boom leg, and the first valve plate is one of the first multi-way reversing valve 1 in the hydraulic system of the boom leg;
  • the system is generally a load-sensitive control system, and the first multi-way reversing valve 1 is an electromagnetic proportional reversing valve, so that multiple first actuators can be simultaneously operated, and the movement speed of each first actuator is steplessly adjusted. Its speed is independent of the size of the load.
  • FIG. 3 illustrates the control flow of the condition adaptive controller in the hydraulic system shown in FIG. 2, which is used to control the commutation of the first multi-way reversing valve.
  • the implementation of the condition adaptive controller includes any one or more of the following steps:
  • the above flow rates are obtained by the following method:
  • the required flow rate of the boom leg hydraulic system is obtained according to the current of each proportional valve in each actuator in the boom leg hydraulic system, according to the rotation speed of the first pump 5 nl
  • the displacement ql obtains the output flow rate Q 2 of the first pump
  • the required flow rate Q 3 of the pumping hydraulic subsystem is obtained according to the requirement of the pumping speed issued by the operator ; according to the rotation speed n 2 of the second pump 4 and the displacement q2
  • the output flow of the second pump Q 4 is obtained by the following method:
  • the required flow rate of the boom leg hydraulic system is obtained according to the current of each proportional valve in each actuator in the boom leg hydraulic system, according to the rotation speed of the first pump 5 nl
  • the displacement ql obtains the output flow rate Q 2 of the first pump
  • the required flow rate Q 3 of the pumping hydraulic subsystem is obtained according to the requirement of the pumping speed issued by the operator ; according to the rotation speed n 2 of the second pump
  • the first multi-valve in each of the first valve disk in a first station is not working, i.e., first A pump does not supply oil to the pumping hydraulic subsystem; preferably, if the demand of the boom leg hydraulic system flows the output flow Q 2 of the first pump, and the demand flow rate of the pumping hydraulic subsystem is 3 ⁇ 4 ⁇ the second pump Output flow Q 4 , then each of the first multi-way reversing valves does not operate in the first station, ie the first pump does not supply oil to the pumping hydraulic subsystem; preferably, if the boom The demand flow of the outrigger hydraulic subsystem flows the output flow Q 2 of the first pump, and the demand flow of the pumping hydraulic subsystem (3 ⁇ 4>the output flow Q 4 of the second pump, then at least one of the first multi-way reversing valves)
  • the first valve plate is operated at the first station, that is, the first pump supplies oil to the pumping hydraulic subsystem
  • the control of the oil supply flow rate of the pumping hydraulic subsystem of the first pump can be realized by controlling the opening degree of the first multi-way reversing valve.
  • the opening degree of each first valve piece of the first multiplex valve is determined by the input current i (or voltage) of the electromagnetic coil, and the working condition adaptive controller pumps the hydraulic pressure according to the first pump 5
  • the magnitude of the system fuel supply flow rate Q combined with the relationship between the current i (or voltage) and the flow rate of each first valve of the first multi-way reversing valve, in real time to the corresponding number of the first multi-way reversing valve A valve output control current i (or voltage), thereby meeting the working requirements of the pumping hydraulic subsystem and the boom leg hydraulic subsystem.
  • the concrete pumping device and the hydraulic system thereof of the invention can provide pressure oil to the second hydraulic subsystem through the first pump thereof, thereby significantly improving the efficiency of the hydraulic system, increasing the load rate of the concrete pumping equipment engine, and reducing the energy consumption.
  • the maximum pumping capacity of concrete pumping equipment is increased by more than 15%.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

Provided are concrete pumping equipment and a hydraulic system thereof, wherein the hydraulic system comprises: a first hydraulic subsystem comprising a first pump (5) and at least one first actuator (6), with a first multi-way reversing valve (1) being provided between the first pump (5) and the first actuator (6), the first multi-way reversing valve (1) comprising at least one first working position and at least one second working position; and a second hydraulic subsystem comprising a second pump (4) and at least one second actuator (7), the second pump (4) driving the at least one second actuator (7); the first pump (5) drives the at least one first actuator (6) via the first working position, and the first pump (5), together with the second pump (4), drives the at least one second actuator (7) via the second working position. By supplying the second hydraulic subsystem with pressure oil by means of the first pump (5), the present invention greatly improves the efficiency of the hydraulic system, increases the load rate of a motor of the concrete pumping equipment and reduces energy consumption on one hand, and improves the maximum pumping capacity of the concrete pumping equipment on the other hand.

Description

混凝土泵送设备及其液压*** 技术领域 本发明涉及液压控制领域， 更具体地， 涉及一种混凝土泵送设备及其液压***。 背景技术 现有技术中的混凝土泵送设备的液压***包括泵送子***、 分配子***、 搅拌清 洗子***和臂架支腿子***等几部分， 每个子***驱动不同的至少一个执行机构。 常 用以下两种构成形式有： 一种是各个子***的组成都是独立的， 具有单独的动力元件 (即泵）、 控制元件 （如阀等）、 执行元件 （如油缸、 马达等） 和辅助元件 （如过滤器 等） 等， 各个子***可以同时工作， 也可以单独工作， 相互之间不受影响； 另一种是 泵送子***与分配子***采用相同的油泵， 但其他子***相互分开。 混凝土泵送设备在工作过程中并不是所有液压子***都需要同时工作， 或者虽然 所有的液压子***同时工作时， 但每个子***都未处于满负荷工作状态， 因此， 存在 ***能力闲置浪费的现象。 例如在布料过程中， 如果布料点是柱子或平板， 那么在一 定时间内臂架和支腿就不需要运动，导致臂架支腿液压子***的油泵就处于空转状态， ***效率很低， 存在不必要的能力与能量的浪费。 发明内容 本发明旨在提供一种混凝土泵送设备及其液压***， 以解决现有技术的液压*** 效率低、 存在能量与能力浪费的问题。 为解决上述技术问题， 根据本发明的一个方面， 提供了一种液压***， 其特征在 于， 包括： 第一液压子***， 第一液压子***包括第一泵和至少一个第一执行机构， 第一泵与第一执行机构之间设置有第一多路换向阀， 第一多路换向阀包括至少一个第 一工位和至少一个第二工位； 第二液压子***， 第二液压子***包括第二泵和至少一 个第二执行机构， 第二泵驱动至少一个第二执行机构； 第一泵通过第一工位驱动至少 一个第一执行机构， 第一泵通过第二工位与第二泵一起共同驱动至少一个第二执行机 构。 进一步地， 第一液压子***还包括第二多路换向阀， 至少一个第一执行机构通过 第二多路换向阀与第一多路换向阀连接。 步地， 第二液压子***通过单向阀、 或截止阀、 或换向阀与第一多路换向阀 BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to the field of hydraulic control, and more particularly to a concrete pumping apparatus and a hydraulic system thereof. BACKGROUND OF THE INVENTION The hydraulic system of a prior art concrete pumping apparatus includes a pumping subsystem, a distribution subsystem, a mixing and cleaning subsystem, and a boom leg subsystem, each of which drives a different at least one actuator. The following two forms are commonly used: One is that the components of each subsystem are independent, with separate power components (ie pumps), control components (such as valves), actuators (such as cylinders, motors, etc.) and auxiliary Components (such as filters, etc.), each subsystem can work at the same time, or can work alone, without being affected by each other; the other is that the pumping subsystem and the distribution subsystem use the same oil pump, but other subsystems are mutually separate. In the process of concrete pumping equipment, not all hydraulic subsystems need to work at the same time, or although all hydraulic subsystems work at the same time, each subsystem is not in full working state. Therefore, there is system waste idle. phenomenon. For example, in the fabric process, if the cloth point is a pillar or a flat plate, then the boom and the legs do not need to move for a certain period of time, so that the oil pump of the hydraulic system of the boom leg is idle, the system efficiency is very low, and there is Unnecessary power and waste of energy. SUMMARY OF THE INVENTION The present invention is directed to a concrete pumping apparatus and a hydraulic system thereof to solve the problems of low efficiency, waste of energy and capability of the prior art hydraulic system. In order to solve the above technical problem, according to an aspect of the invention, a hydraulic system is provided, comprising: a first hydraulic subsystem, the first hydraulic subsystem including a first pump and at least one first actuator, a first multi-way reversing valve is disposed between the pump and the first actuator, the first multi-way reversing valve includes at least one first station and at least one second station; the second hydraulic subsystem, the second hydraulic pressure The subsystem includes a second pump and at least one second actuator, the second pump driving the at least one second actuator; the first pump drives the at least one first actuator through the first station, the first pump passes the second station The second pump together drives at least one second actuator. Further, the first hydraulic subsystem further includes a second multi-way reversing valve, and the at least one first actuator is coupled to the first multi-way reversing valve through the second multi-way reversing valve. Step, the second hydraulic subsystem passes the one-way valve, or the shut-off valve, or the reversing valve and the first multi-way reversing valve
进一步地， 第一多路换向阀包括多个第一阀片和多个第二阀片， 每个第一阀片包 括第一工位和第二工位， 一部分第一执行机构与第一阀片连接， 另一部分第一执行机 构与第二阀片连接。 进一步地， 第二液压子***通过单向阀、 或截止阀、 或换向阀与每个第一阀片连 Further, the first multiplex valve includes a plurality of first valve plates and a plurality of second valve plates, each of the first valve plates includes a first station and a second station, and a portion of the first actuator and the first The valve plate is connected, and the other part of the first actuator is connected to the second valve piece. Further, the second hydraulic subsystem is connected to each of the first valves through a one-way valve, or a shut-off valve, or a reversing valve
进一步地， 液压***还包括工况自适应控制器， 用于根据工况控制每个第一阀片 从第一工位切换到第二工位、 并用于控制每个第一阀片的开度的大小。 进一步地， 当各个第一执行机构的总需求流量大于等于第一泵的输出流量时， 工 况自适应控制器控制第一多路换向阀中的每个第一阀片处于第一工位。 进一步地， 当各个第一执行机构的总需求流量小于第一泵的输出流量、 且各个第 二执行机构的总需求流量小于等于第二泵的输出流量时， 工况自适应控制器控制第一 多路换向阀中的每个第一阀片处于第一工位。 进一步地， 当各个第一执行机构的总需求流量小于第一泵的输出流量、 且至少一 个第二执行机构的需求流量大于第二泵的输出流量时， 工况自适应控制器控制第一多 路换向阀中的至少一个第一阀片处于第二工位。 根据本发明的另一个方面， 提供了一种混凝土泵送设备， 其包括上述液压***。 进一步地， 液压***中的第一液压子***是臂架支腿液压子***， 液压***中的 第二液压子***是泵送液压子***。 进一步地， 液压***根据混凝土泵送设备对其臂架的速度要求和 /或泵送的速度要 求控制液压***的第一多路换向阀换向。 本发明中的混凝土泵送设备及其液压***可通过其第一泵向第二液压子***提供 压力油， 一方面显著提高液压***效率、 提高了混凝土泵送设备发动机的负荷率、 降 低能耗； 另一方面使混凝土泵送设备的最大泵送能力提高 15%以上。 附图说明 构成本申请的一部分的附图用来提供对本发明的进一步理解， 本发明的示意性实 施例及其说明用于解释本发明， 并不构成对本发明的不当限定。 在附图中： 图 1示意性示出了第一种优选实施方式中的液压***的液压原理图； 图 2示意性示出了第二种优选实施方式中的液压***的液压原理图； 以及 图 3示意性示出了液压***中的工况自适应控制器的控制流程图。 具体实施方式 以下结合附图对本发明的实施例进行详细说明， 但是本发明可以由权利要求限定 和覆盖的多种不同方式实施。 本发明的第一方面， 提供一种液压***， 该液压***包括： 第一液压子***和第 二液压子***； 其中， 第一液压子***包括第一泵和至少一个第一执行机构， 第一泵 与至少一个第一执行机构之间设置有第一多路换向阀， 第一多路换向阀包括至少一个 第一工位和至少一个第二工位；第二液压子***包括第二泵和至少一个第二执行机构， 第二泵驱动至少一个第二执行机构；第一泵通过第一工位驱动至少一个第一执行机构， 第一泵通过第二工位与第二泵一起共同驱动至少一个第二执行机构。 因此， 当第一多 路换向阀处于第一工位时， 第一泵向至少一个第一执行机构提供压力油， 此时， 至少 一个第一执行机构正常工作， 且至少一个第二执行机构仅接受来自第二泵所输出的压 力油； 当至少一个第二执行机构需要更多的压力油时， 可将第一多路换向阀切换到第 二工位， 此时， 第一泵向第二执行机构提供压力油， 于是， 第二执行机构此时同时获 得第一泵和第二泵所提供的压力油， 从而能够满足第二执行机构的工作需要， 提高了 液压***的效率， 降低了能耗。 在上述液压***的基础上， 下面结合两个具体的实施例对该液压***进行详细说 明。 图 1示出了第一种优选实施方式下的上述液压***的液压原理图。 如图 1所示， 该液压***包括第一液压子***和第二液压子***； 其中， 第一液压子***包括第一 泵 5和至少一个第一执行机构 6， 第一泵 5与至少一个第一执行机构 6之间设置有第 一多路换向阀 1， 第一多路换向阀 1包括第一工位 （即左位） 和第二工位 （即右位）； 第二液压子***包括第二泵 4和至少一个第二执行机构 7， 第二泵 4驱动至少一个第 二执行机构 7; 第一泵 5通过第一工位驱动至少一个第一执行机构 6，第一泵 5通过第 二工位与第二泵 4一起共同驱动至少一个第二执行机构 7。 优选地， 第一液压子*** 还包括第二多路换向阀 3， 至少一个第一执行机构 6通过第二多路换向阀 3与第一多 路换向阀 1连接。 当第一执行机构需要工作时， 将第一多路阀 1保持在第一工位， 此 时， 第一泵 5的压力油直接通过第一多路阀 1进入第一执行机构中去， 而第二泵的压 力油直接驱动第二执行机构工作， 即第一液压子***和第二液压子***分别独立地工 作， 相互之间没有任何影响； 当第一液压子***中的所有第一执行机构都处于停止状 态时， 第一执行机构 6不再需要第一泵 5提供压力油， 此时， 可以使第一多路换向阀 1工作在第二工位， 使第一泵 5的压力油通过第一多路换向阀 1进入第二液压子*** 中， 此时， 第一泵 5与第二泵 4处于合流状态， 从而提高了液压***的， 降低了能耗。 当第一多路阀 1处于第一工位时， 本领域技术人员可以采用多种方式 （如单向阀、 或 截止阀、 或换向阀） 实现第一液压子***和第二液压子***的隔离， 使二者分别独立 地工作， 相互之间没有任何影响， 优选地， 可以使通过单向阀 2将第二液压子***与 第一多路换向阀 1连接， 这样当第一多路换向阀处于第一工位时， 第二液压子***的 压力油不会通过第一多路换向阀 1而流入油箱。 在图 1所示的第一种优选地实施方式中， 该液压***仅能在第一液压子***中的 所有第一执行机构都处于停止工作的情况下， 第一泵 5才能给第二液压子***提供额 外的压力油， 但在多数情况下， 第一液压子***中的至少一个第一执行机构中仅有一 部分第一执行机构运动， 或者运行的速度很慢， 因此， 第一泵 5未处于满负载状态， 即此时仍然存在***能力的浪费。 为了克服图 1所示的第一种优选实施方式中的不足， 本发明还提供了如图 2所示 的第二种优选实施方式。 如图 2所示， 该液压***包括第一液压子***和第二液压子 ***； 其中， 第一液压子***包括第一泵 5和至少一个第一执行机构 6， 第一泵 5与 至少一个第一执行机构 6之间设置有第一多路换向阀 1， 第一多路换向阀 1包括至少 一个第一工位（即下位）和至少一个第二工位（即上位）； 第二液压子***包括第二泵 4和至少一个第二执行机构 7， 第二泵 4驱动至少一个第二执行机构 7; 第一泵 5通过 第一工位驱动至少一个第一执行机构 6， 第一泵 5通过第二工位与第二泵 4一起共同 驱动至少一个第二执行机构 7， 进一步， 第一多路换向阀 1具有多个第一阀片 Γ和多 个第二阀片（未示出）， 每个第一阀片 Γ都包括一个第一工位和一个第二工位， 且一部 分第一执行机构 6都与第一阀片 Γ连接，另一部分第一执行机构 6与第二阀片连接 (需 要说明的是， 第一阀片与第二阀片可能具有不同的结构， 即第二阀片可能不具有本实 施例中的第二工位， 也就是说与第二阀片连接的该另一部分第一执行机构不与第二液 压子***连接）， 因此，可以通过不同的第一阀片 Γ分别实现对不同的第一执行机构的 控制。 其中， 当某一第一阀片 Γ处于第一工位时， 驱动与该某一第一阀片 Γ相连接的 第一执行机构 6工作， 而当该某一第一阀片 Γ处于第二工位时， 第一泵 5不再向与该 某一第一阀片 Γ连接的第一执行机构 6提供压力油， 从而使该第一执行机构 6停止工 作。 因此， 可以分别对第一多路换向阀 1中的每个第一阀片 Γ进行控制， 从而使得与 第一阀片连接的第一执行机构中的一部分正常工作而另一部分停止工作， 进一步， 停 止工作的该另一部分第一执行机构所连接的第一阀片处于第二工位， 因而可以向第二 液压子***提供压力油， 同时， 正常工作的该一部分第一执行机构所连接的第一阀片 则处于第一工位， 因而可以继续运动而不受影响。 可见， 图 2中的液压***不必要使 所有的第一执行机构都处于停止工作的状态就能向第二液压子***提供压力油， 因而 提高了整个液压***的效率， 降低了能耗。 当第一阀片 Γ处于第一工位时， 本领域技 术人员可以采用多种方式 （如单向阀、 或截止阀、 或换向阀） 实现第一液压子***和 第二液压子***的隔离， 使二者分别独立地工作， 相互之间没有任何影响， 优选地， 可以使通过单向阀 2将第二液压子***与第一多路换向阀 1或每个第一阀片 Γ连接。 进一步， 本发明还需要考虑第一多路换向阀 1或其每个第一阀片 Γ的切换时机及 开度的大小， 即第一泵 5何时向第二液压子***提供压力油， 以及提供多少压力油， 这必须取决于实际的工况， 即必须同时满足以下两个条件： （1 ) 使用第一泵 5向第二 液压子***提供压力油， 必须不影响第一液压子***各第一执行机构的运动速度； （2) 仅在第二液压子***无法满足操作人员要求的性能指标的情况下才由第一泵 5向第二 液压子***提供压力油。 为此， 本液压***还包括工况自适应控制器， 其用于根据工况控制每个第一阀片 从第一工位切换到第二工位、 并用于控制每个所述第一阀片的开度的大小。 优选地， 当各个第一执行机构的总需求流量大于等于第一泵的输出流量时， 工况自适应控制器 控制第一多路换向阀中的每个第一阀片处于第一工位。 优选地， 当各个第一执行机构 的总需求流量小于第一泵的输出流量、 且该至少一个第二执行机构的总需求流量小于 等于第二泵的输出流量时， 工况自适应控制器控制第一多路换向阀中的每个第一阀片 处于第一工位。 优选地， 当各个第一执行机构的总需求流量小于第一泵的输出流量、 且该至少一个第二执行机构的需求流量大于第二泵的输出流量时， 工况自适应控制器 控制第一多路换向阀中的至少一个第一阀片处于第二工位。 在上述各实施例的基础上， 本发明的第二方面还提供一种混凝土泵送设备， 其包 括上述各实施方式中的液压***。优选地， 结合图 1-2， 液压***中的第一液压子*** 是臂架支腿液压子***， 液压***中的第二液压子***是泵送液压子***。 优选地， 液压***根据混凝土泵送设备对其臂架（和 /或支腿）的速度要求和 /或泵送的速度要求 控制液压***的第一多路换向阀换向。 请再参考图 1， 第一泵 5首先保证臂架支腿液压子***中的臂架支腿的运动， 所 以当臂架支腿液压子***中有一个执行机构运动时， 则需要使第一多路换向阀 1工作 在第一位（即左位）， 此时， 第一泵 5的压力油通过第一多路换向阀 1进入臂架支腿液 压子***， 并可通过单向阀 2来限制第二泵 4的压力油通过第一多路换向阀 1进入油 箱， 此时泵送液压子***与臂架支腿液压子***独立工作， 相互之间无影响； 若臂架 支腿液压子***中所有的执行机构都处于停止状态， 则可使第一多路换向阀 1工作在 第二工位 （即右位）， 此时， 第一泵 5的压力油通过第一多路换向阀 1、 单向阀 2进入 泵送液压子***， 即此时第二泵 4与第一泵 5处于合流状态， 从而提高了混凝土泵送 设备的泵送能力及液压***的效率， 并提高了混凝土泵送设备的发动机的负荷率， 降 低了能耗。 请再参考图 2，通过第一多路换向阀 1、单向阀 2将泵送液压子***与臂架支腿液 压子***连接起来， 其中， 第二泵 4为泵送液压子***的油泵， 第一泵 5为臂架支腿 液压子***的油泵，第一阀片 Γ为臂架支腿液压子***中第一多路换向阀 1中的一片； 由于臂架支腿液压子***一般为负载敏感控制***， 第一多路换向阀 1为电磁比例换 向阀， 因而可以实现多个第一执行机构同时动作， 且各第一执行机构的运动速度的无 级调节， 使其速度与负载的大小无关。 因此， 即使臂架支腿液压子***中某些第一执 行机构在运动过程中， 如果第一多路换向阀 1中的至少一个第一阀片工作在第二工位 (即上位）， 则第一泵 5的部分压力油也可以通过第一多路换向阀 1、 单向阀 2进入泵 送液压子***中， 而不影响其他第一执行机构的运动， 从而提高了混凝土泵送设备的 泵送能力及液压***效率， 并提高了混凝土泵送设备的发动机的负荷率， 降低了能耗。 图 3对图 2所示的液压***中的工况自适应控制器的控制流程进行了说明， 该工 况自适应控制器用于对第一多路换向阀的换向进行控制。 如图 3所示， 工况自适应控 制器的实现包括以下步骤中的任一个或多个： Further, the hydraulic system further includes a working condition adaptive controller for controlling each first valve to switch from the first station to the second station according to working conditions, and for controlling the opening degree of each of the first valves the size of. Further, when the total demand flow rate of each of the first actuators is greater than or equal to the output flow rate of the first pump, the working condition adaptive controller controls each of the first multi-way reversing valves to be in the first station. . Further, when the total required flow rate of each of the first actuators is less than the output flow rate of the first pump, and the total demand flow rate of each of the second actuators is less than or equal to the output flow rate of the second pump, the condition adaptive controller controls the first Each of the multiplexed valves is in the first station. Further, when the total required flow rate of each of the first actuators is less than the output flow rate of the first pump, and the demand flow rate of the at least one second actuator is greater than the output flow rate of the second pump, the condition adaptive controller controls the first At least one of the first valve plates of the way diverter valve is in the second station. According to another aspect of the invention, a concrete pumping apparatus is provided that includes the hydraulic system described above. Further, the first hydraulic subsystem in the hydraulic system is the boom leg hydraulic subsystem, and the second hydraulic subsystem in the hydraulic system is the pumping hydraulic subsystem. Further, the hydraulic system controls the commutation of the first multi-way reversing valve of the hydraulic system based on the speed requirements of the concrete pumping equipment for its boom and/or the speed requirements of the pumping. The concrete pumping device and the hydraulic system thereof of the invention can provide pressure oil to the second hydraulic subsystem through the first pump thereof, thereby significantly improving the efficiency of the hydraulic system, increasing the load rate of the concrete pumping equipment engine, and reducing the energy consumption. On the other hand, the maximum pumping capacity of concrete pumping equipment is increased by more than 15%. BRIEF DESCRIPTION OF THE DRAWINGS The accompanying drawings, which are incorporated in FIG. In the drawings: Fig. 1 is a schematic view showing a hydraulic principle of a hydraulic system in a first preferred embodiment; Fig. 2 is a schematic view showing a hydraulic principle of a hydraulic system in a second preferred embodiment; Fig. 3 schematically shows a control flow chart of a condition adaptive controller in a hydraulic system. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The embodiments of the present invention are described in detail below with reference to the accompanying drawings. In a first aspect of the invention, a hydraulic system is provided, the hydraulic system comprising: a first hydraulic subsystem and a second hydraulic subsystem; wherein the first hydraulic subsystem includes a first pump and at least one first actuator, a first multiplex valve is disposed between the pump and the at least one first actuator, the first multiplex valve includes at least one first station and at least one second station; and the second hydraulic subsystem includes a second pump and at least one second actuator, the second pump driving the at least one second actuator; the first pump drives the at least one first actuator through the first station, and the first pump passes the second station together with the second pump Cooperating at least one second actuator. Therefore, when the first multiplex valve is in the first station, the first pump supplies pressurized oil to the at least one first actuator, at which time at least one first actuator operates normally, and at least one second actuator Only receiving the pressure oil from the second pump; when at least one second actuator requires more pressure oil, the first multiplex valve can be switched to the second station, at which time, the first pump The second actuator provides the pressure oil, so that the second actuator simultaneously obtains the pressure oil provided by the first pump and the second pump, thereby meeting the working requirements of the second actuator, improving the efficiency of the hydraulic system, and reducing Energy consumption. Based on the above hydraulic system, the hydraulic system will be described in detail below in conjunction with two specific embodiments. Fig. 1 shows a hydraulic principle diagram of the above hydraulic system in the first preferred embodiment. As shown in FIG. 1, the hydraulic system includes a first hydraulic subsystem and a second hydraulic subsystem; wherein the first hydraulic subsystem includes a first pump 5 and at least one first actuator 6, the first pump 5 and at least one A first multi-way reversing valve 1 is disposed between the first actuators 6, and the first multi-way reversing valve 1 includes a first station (ie, a left position) and a second station (ie, a right position); The subsystem comprises a second pump 4 and at least one second actuator 7, the second pump 4 driving at least one second actuator 7; the first pump 5 drives at least one first actuator 6, a first pump, through a first station 5 through the first The second station together with the second pump 4 drives at least one second actuator 7. Preferably, the first hydraulic subsystem further comprises a second multiplex valve 3, and the at least one first actuator 6 is connected to the first multiplex valve 1 via the second directional valve 3. When the first actuator needs to work, the first multi-way valve 1 is kept at the first station, and at this time, the pressure oil of the first pump 5 directly enters the first actuator through the first multi-way valve 1, and The pressure oil of the second pump directly drives the second actuator to work, that is, the first hydraulic subsystem and the second hydraulic subsystem operate independently, without any influence on each other; when all the first executions in the first hydraulic subsystem When the mechanism is in the stop state, the first actuator 6 no longer needs the first pump 5 to supply the pressure oil. At this time, the first multiplex valve 1 can be operated at the second station, and the pressure of the first pump 5 is made. The oil enters the second hydraulic subsystem through the first multi-way reversing valve 1. At this time, the first pump 5 and the second pump 4 are in a confluent state, thereby improving the hydraulic system and reducing energy consumption. When the first multi-way valve 1 is in the first station, the person skilled in the art can implement the first hydraulic subsystem and the second hydraulic subsystem in various ways (such as a one-way valve, or a shut-off valve, or a reversing valve). The isolation, so that the two work independently, without any influence between each other, preferably, the second hydraulic subsystem can be connected to the first multi-way reversing valve 1 through the one-way valve 2, so that when the first When the road reversing valve is in the first position, the pressure oil of the second hydraulic system does not flow into the tank through the first multi-way reversing valve 1. In the first preferred embodiment shown in FIG. 1, the hydraulic system can only give the second hydraulic pressure if all of the first actuators in the first hydraulic subsystem are in a stop operation. The subsystem provides additional pressure oil, but in most cases only a portion of the first actuator in at least one of the first hydraulic subsystems moves, or the speed of operation is slow, therefore, the first pump 5 Not in full load state, that is, there is still a waste of system capacity. In order to overcome the deficiencies in the first preferred embodiment shown in Figure 1, the present invention also provides a second preferred embodiment as shown in Figure 2. As shown in FIG. 2, the hydraulic system includes a first hydraulic subsystem and a second hydraulic subsystem; wherein the first hydraulic subsystem includes a first pump 5 and at least one first actuator 6, the first pump 5 and at least one A first multiplex valve 1 is disposed between the first actuators 6, and the first multiplex valve 1 includes at least one first station (ie, a lower position) and at least one second station (ie, a higher position); The second hydraulic system comprises a second pump 4 and at least one second actuator 7, the second pump 4 drives at least one second actuator 7; the first pump 5 drives at least one first actuator 6 through the first station, A pump 5 drives the at least one second actuator 7 together with the second pump 4 through the second station. Further, the first multiplex valve 1 has a plurality of first valve plates 多个 and a plurality of second valve plates ( Not shown), each of the first valve discs includes a first station and a second station, and a part of the first actuator 6 is connected to the first valve disc, and the other part of the first actuator 6 is Second valve connection (note that the first valve and the second valve may There is a different structure, that is, the second valve piece may not have the second station in the embodiment, that is, the other part of the first actuator connected to the second valve piece is not connected to the second hydraulic system) Therefore, the control of the different first actuators can be achieved separately by the different first valve flaps. Wherein, when a certain first valve piece is at the first station, driving is connected to the certain first valve piece The first actuator 6 operates, and when the certain first valve flap is in the second station, the first pump 5 no longer supplies pressure oil to the first actuator 6 connected to the certain first valve flap , thereby causing the first actuator 6 to stop working. Therefore, each of the first valve spools 1 of the first multiplex valve 1 can be separately controlled such that a part of the first actuator connected to the first valve plate works normally and the other portion stops working, further The first valve piece connected to the other part of the first actuator that is stopped working is in the second station, so that the second hydraulic system can be supplied with pressurized oil, and at the same time, the part of the first actuator that is normally operated is connected The first valve is in the first position so that it can continue to move without being affected. It can be seen that the hydraulic system of FIG. 2 does not need to have all of the first actuators in a stopped state to supply pressurized oil to the second hydraulic subsystem, thereby improving the efficiency of the entire hydraulic system and reducing energy consumption. When the first valve disc is in the first position, a person skilled in the art can implement the first hydraulic subsystem and the second hydraulic subsystem in various manners (such as a one-way valve, or a shut-off valve, or a reversing valve). Isolation, so that the two work independently, without any influence on each other. Preferably, the second hydraulic subsystem can be made to pass through the one-way valve 2 with the first multiplex valve 1 or each first valve Γ connection. Further, the present invention also needs to consider the switching timing and opening degree of the first multi-way reversing valve 1 or each of the first valve discs, that is, when the first pump 5 supplies the pressure oil to the second hydraulic subsystem, And how much pressure oil is supplied, which must depend on the actual working conditions, that is, the following two conditions must be met: (1) The first pump 5 is used to supply the pressure oil to the second hydraulic subsystem, and the first hydraulic system must not be affected. The speed of movement of each of the first actuators; (2) The first pump 5 supplies pressure oil to the second hydraulic subsystem only if the second hydraulic subsystem fails to meet the performance specifications required by the operator. To this end, the hydraulic system further includes a condition adaptive controller for controlling each first valve to switch from the first station to the second station according to operating conditions, and for controlling each of the first valves The size of the opening of the piece. Preferably, when the total demand flow rate of each of the first actuators is greater than or equal to the output flow rate of the first pump, the condition adaptive controller controls each of the first multi-way reversing valves to be in the first station. . Preferably, when the total required flow rate of each of the first actuators is less than the output flow rate of the first pump, and the total demand flow rate of the at least one second actuator is less than or equal to the output flow rate of the second pump, the condition adaptive controller controls Each of the first multiplex valve is in the first station. Preferably, when the total required flow rate of each of the first actuators is less than the output flow rate of the first pump, and the required flow rate of the at least one second actuator is greater than the output flow of the second pump, the condition adaptive controller controls the first At least one of the plurality of directional valves is in the second station. In addition to the above embodiments, the second aspect of the present invention also provides a concrete pumping apparatus comprising the hydraulic system of each of the above embodiments. Preferably, in conjunction with Figures 1-2, the first hydraulic subsystem in the hydraulic system is the boom leg hydraulic subsystem and the second hydraulic subsystem in the hydraulic system is the pumping hydraulic subsystem. Preferably, the hydraulic system controls the commutation of the first multi-way reversing valve of the hydraulic system in accordance with the speed requirements of the concrete pumping equipment for its boom (and/or legs) and/or the speed requirements of the pumping. Referring again to FIG. 1, the first pump 5 first ensures the movement of the boom legs in the boom leg hydraulic system, so when there is an actuator movement in the boom leg hydraulic subsystem, the first need to be made. The multi-way reversing valve 1 operates in the first position (ie, the left position). At this time, the pressure oil of the first pump 5 enters the boom leg hydraulic system through the first multi-way reversing valve 1 and can pass through the one-way The valve 2 is used to restrict the pressure oil of the second pump 4 from entering the fuel tank through the first multi-way reversing valve 1. At this time, the pumping hydraulic system works independently with the boom leg hydraulic system, and has no influence on each other; When all the actuators in the hydraulic system of the leg are in a stopped state, the first multiplex valve 1 can be operated at the second station (ie, the right position). At this time, the pressure oil of the first pump 5 passes through the first stage. A multi-way reversing valve 1 and a check valve 2 enter the pumping hydraulic subsystem, that is, the second pump 4 and the first pump 5 are in a confluent state at this time, thereby improving the pumping capacity of the concrete pumping device and the hydraulic system. Efficiency, and increase the load rate of the engine of the concrete pumping equipment, reducing energy consumption . Referring again to FIG. 2, the pumping hydraulic subsystem is connected to the boom leg hydraulic system through the first multi-way reversing valve 1 and the one-way valve 2, wherein the second pump 4 is a pumping hydraulic subsystem. The first pump 5 is an oil pump of the hydraulic system of the boom leg, and the first valve plate is one of the first multi-way reversing valve 1 in the hydraulic system of the boom leg; The system is generally a load-sensitive control system, and the first multi-way reversing valve 1 is an electromagnetic proportional reversing valve, so that multiple first actuators can be simultaneously operated, and the movement speed of each first actuator is steplessly adjusted. Its speed is independent of the size of the load. Therefore, even if some of the first actuators in the boom leg hydraulic system are in motion, if at least one of the first directional spool valves 1 is operated at the second station (ie, the upper position), Then part of the pressure oil of the first pump 5 can also enter the pumping hydraulic subsystem through the first multi-way reversing valve 1 and the check valve 2 without affecting the movement of the other first actuators, thereby improving concrete pumping. The pumping capacity of the equipment and the efficiency of the hydraulic system increase the load rate of the engine of the concrete pumping equipment and reduce the energy consumption. FIG. 3 illustrates the control flow of the condition adaptive controller in the hydraulic system shown in FIG. 2, which is used to control the commutation of the first multi-way reversing valve. As shown in FIG. 3, the implementation of the condition adaptive controller includes any one or more of the following steps:
( 1 ) 检测与计算臂架支腿液压子***的需求流量 、 第一泵的输出流量 Q2、 泵 送液压子***的需求流量 Q3和第二泵的输出流量 Q4。 优选地， 采用以下方法得到上述各流量： 根据臂架支腿液压子***中各个执行机 构中的各比例阀的电流得到臂架支腿液压子***的需求流量 ，根据第一泵 5的转速 nl及排量 ql得到第一泵的输出流量 Q2 ; 根据操作人员发出的泵送速度的要求得到泵 送液压子***的需求流量 Q3 ;根据第二泵 4的转速 n2及排量 q2得到第二泵的输出流 量 Q4。 (2)根据臂架支腿液压子***的需求流量^和第一泵的输出流量 Q2的比较结果; 或根据臂架支腿液压子***的需求流量 和第一泵的输出流量 Q2的比较结果、 及泵 送液压子***的需求流量 Q3和第二泵的输出流量 Q4的比较结果决定第一泵是否向泵 送液压子***供油， 进一步， 还可确认第一泵向泵送液压子***提供的流量的大小。 优选地， 如果臂架支腿液压子***的需求流量 第一泵的输出流量 Q2， 则第一 多路换向阀中的每个第一阀片都不工作在第一工位， 即第一泵不给泵送液压子***供 油； 优选地， 如果臂架支腿液压子***的需求流量 第一泵的输出流量 Q2， 且泵送 液压子***的需求流量 ¾≤第二泵的输出流量 Q4， 则第一多路换向阀中的每个第一阀 片都不工作在第一工位， 即第一泵不给泵送液压子***供油； 优选地， 如果臂架支腿液压子***的需求流量 第一泵的输出流量 Q2， 且泵送 液压子***的需求流量 (¾>第二泵的输出流量 Q4， 则第一多路换向阀中的至少一个第 一阀片都工作在第一工位， 即第一泵向泵送液压子***供油。 优选地， 可根据泵送液 压子***实际需要补充的流量（即泵送液压子***的需求流量 Q3—第二泵的输出流量 Q4)和臂架支腿液压子***能够提供的多余流量（即第一泵的输出流量 Q2—臂架支腿 液压子***的需求流量 来确定第一泵 5向泵送液压子***供油流量 Q的大小，例 如，如果泵送液压子***实际需要补充的流量 >臂架支腿液压子***能够提供的多余流 量， 则 0 =臂架支腿液压子***能够提供的多余流量； 如果泵送液压子***实际需要 补充的流量 <臂架支腿液压子***能够提供的多余流量，则 0 =泵送液压子***实际需 要补充的流量。 (1) Detecting and calculating the demand flow of the boom leg hydraulic system, the output flow Q 2 of the first pump, the demand flow Q 3 of the pumping hydraulic subsystem, and the output flow Q 4 of the second pump. Preferably, the above flow rates are obtained by the following method: The required flow rate of the boom leg hydraulic system is obtained according to the current of each proportional valve in each actuator in the boom leg hydraulic system, according to the rotation speed of the first pump 5 nl And the displacement ql obtains the output flow rate Q 2 of the first pump ; the required flow rate Q 3 of the pumping hydraulic subsystem is obtained according to the requirement of the pumping speed issued by the operator ; according to the rotation speed n 2 of the second pump 4 and the displacement q2 The output flow of the second pump Q 4 . (2) According to the demand flow of the hydraulic system of the boom leg and the output flow Q 2 of the first pump; or according to the demand flow of the hydraulic system of the boom leg and the output flow Q 2 of the first pump The comparison result, and the comparison result of the demand flow rate Q 3 of the pumping hydraulic subsystem and the output flow rate Q 4 of the second pump determine whether the first pump supplies oil to the pumping hydraulic subsystem, and further, the first pump to the pump can be confirmed The amount of flow sent by the hydraulic subsystem. Preferably, if the output flow demand flow jib leg first pump hydraulic subsystem Q 2, the first multi-valve in each of the first valve disk in a first station is not working, i.e., first A pump does not supply oil to the pumping hydraulic subsystem; preferably, if the demand of the boom leg hydraulic system flows the output flow Q 2 of the first pump, and the demand flow rate of the pumping hydraulic subsystem is 3⁄4 ≤ the second pump Output flow Q 4 , then each of the first multi-way reversing valves does not operate in the first station, ie the first pump does not supply oil to the pumping hydraulic subsystem; preferably, if the boom The demand flow of the outrigger hydraulic subsystem flows the output flow Q 2 of the first pump, and the demand flow of the pumping hydraulic subsystem (3⁄4>the output flow Q 4 of the second pump, then at least one of the first multi-way reversing valves) The first valve plate is operated at the first station, that is, the first pump supplies oil to the pumping hydraulic subsystem. Preferably, the flow required by the pumping hydraulic subsystem can be supplemented (ie, the required flow rate of the pumping hydraulic subsystem) Q 3 - second pump output flow Q 4) and a boom hydraulic subsystem is capable of legs For excess flow (i.e., the output of the first pump flow rate Q 2 - Boom demand flow leg hydraulic subsystem to determine a first pumping hydraulic pump 5 to oil flow rate Q subsystem size, e.g., if the hydraulic pump The actual flow that the subsystem needs to replenish > the excess flow that the boom leg hydraulic subsystem can provide, then 0 = the excess flow that the boom leg hydraulic subsystem can provide; if the pumping hydraulic subsystem actually needs additional flow <arm The excess flow that the leg hydraulic system can provide is 0 = the pumping hydraulic subsystem actually needs additional flow.
(3 ) 根据第一泵向泵送液压子***供油流量 Q 的大小控制第一多路换向阀的至 少一个第一阀片的开度， 以实现对第一泵向泵送液压子***的供油流量的控制。 优选 地， 由于第一多路换向阀为电磁比例阀， 因此， 通过对第一多路换向阀的开度控制， 就可以实现对第一泵给泵送液压子***供油流量的控制。 优选地， 第一多路换向阀的 每个第一阀片的开度由其电磁线圈的输入电流 i (或电压）决定， 工况自适应控制器根 据第一泵 5向泵送液压子***供油流量 Q的大小， 结合第一多路换向阀的每个第一阀 片的电流 i (或电压）与流量之间的关系特性， 实时向第一多路换向阀的相应第一阀片 输出控制电流 i (或电压）， 从而同时满足了泵送液压子***与臂架支腿液压子***的 工作要求。 本发明中的混凝土泵送设备及其液压***可通过其第一泵向第二液压子***提供 压力油， 一方面显著提高液压***效率、 提高了混凝土泵送设备发动机的负荷率、 降 低能耗； 另一方面使混凝土泵送设备的最大泵送能力提高 15%以上。 以上所述仅为本发明的优选实施例而已， 并不用于限制本发明， 对于本领域的技 术人员来说， 本发明可以有各种更改和变化。 凡在本发明的精神和原则之内， 所作的 任何修改、 等同替换、 改进等， 均应包含在本发明的保护范围之内。 (3) controlling the opening degree of the at least one first valve piece of the first multi-way reversing valve according to the magnitude of the oil supply flow rate Q of the pumping hydraulic subsystem according to the first pump, so as to realize the pumping hydraulic system to the first pump Control of the fuel supply flow. Preferably, since the first multi-way reversing valve is an electromagnetic proportional valve, the control of the oil supply flow rate of the pumping hydraulic subsystem of the first pump can be realized by controlling the opening degree of the first multi-way reversing valve. . Preferably, the opening degree of each first valve piece of the first multiplex valve is determined by the input current i (or voltage) of the electromagnetic coil, and the working condition adaptive controller pumps the hydraulic pressure according to the first pump 5 The magnitude of the system fuel supply flow rate Q, combined with the relationship between the current i (or voltage) and the flow rate of each first valve of the first multi-way reversing valve, in real time to the corresponding number of the first multi-way reversing valve A valve output control current i (or voltage), thereby meeting the working requirements of the pumping hydraulic subsystem and the boom leg hydraulic subsystem. The concrete pumping device and the hydraulic system thereof of the invention can provide pressure oil to the second hydraulic subsystem through the first pump thereof, thereby significantly improving the efficiency of the hydraulic system, increasing the load rate of the concrete pumping equipment engine, and reducing the energy consumption. On the other hand, the maximum pumping capacity of concrete pumping equipment is increased by more than 15%. The above is only the preferred embodiment of the present invention, and is not intended to limit the present invention, and various modifications and changes can be made to the present invention. Any modifications, equivalent substitutions, improvements, etc. made within the spirit and scope of the present invention are intended to be included within the scope of the present invention.

Claims

权 利 要 求 书 Claim
1. 一种液压***， 其特征在于， 包括： A hydraulic system, comprising:
第一液压子***， 所述第一液压子***包括第一泵和至少一个第一执行机 构， 所述第一泵与所述第一执行机构之间设置有第一多路换向阀， 所述第一多 路换向阀包括至少一个第一工位和至少一个第二工位；  a first hydraulic subsystem, the first hydraulic subsystem includes a first pump and at least one first actuator, and a first multi-way reversing valve is disposed between the first pump and the first actuator The first multiplex valve includes at least one first station and at least one second station;
第二液压子***， 所述第二液压子***包括第二泵和至少一个第二执行机 构， 所述第二泵驱动所述至少一个第二执行机构；  a second hydraulic subsystem, the second hydraulic subsystem comprising a second pump and at least one second actuator, the second pump driving the at least one second actuator;
所述第一泵通过所述第一工位驱动所述至少一个第一执行机构， 所述第一 泵通过所述第二工位与所述第二泵一起共同驱动所述至少一个第二执行机构。  The first pump drives the at least one first actuator through the first station, the first pump driving the at least one second execution together with the second pump through the second station mechanism.
2. 根据权利要求 1所述的液压***， 其特征在于， 所述第一液压子***还包括第 二多路换向阀， 所述至少一个第一执行机构通过所述第二多路换向阀与所述第 一多路换向阀连接。 2. The hydraulic system according to claim 1, wherein the first hydraulic subsystem further comprises a second multi-way reversing valve, and the at least one first actuator is reversible by the second multi-way A valve is coupled to the first multi-way reversing valve.
3. 根据权利要求 1所述的液压***， 其特征在于， 所述第二液压子***通过单向 阀、 或截止阀、 或换向阀与所述第一多路换向阀连接。 3. The hydraulic system according to claim 1, wherein the second hydraulic subsystem is coupled to the first multiplex valve by a one-way valve, or a shut-off valve, or a directional valve.
4. 根据权利要求 1所述的液压***， 其特征在于， 所述第一多路换向阀包括多个 第一阀片和多个第二阀片， 每个所述第一阀片包括所述第一工位和所述第二工 位， 一部分所述第一执行机构与所述第一阀片连接， 另一部分所述第一执行机 构与所述第二阀片连接。 4. The hydraulic system according to claim 1, wherein the first multiplex valve includes a plurality of first valve plates and a plurality of second valve plates, each of the first valve plates including a The first station and the second station, a part of the first actuator is connected to the first valve piece, and another part of the first actuator is connected to the second valve piece.
5. 根据权利要求 4所述的液压***， 其特征在于， 所述第二液压子***通过单向 阀、 或截止阀、 或换向阀与所述每个第一阀片连接。 5. The hydraulic system according to claim 4, wherein the second hydraulic subsystem is coupled to each of the first valve sheets by a one-way valve, or a shut-off valve, or a reversing valve.
6. 根据权利要求 4或 5所述的液压***， 其特征在于， 所述液压***还包括工况 自适应控制器， 用于根据工况控制每个所述第一阀片从所述第一工位切换到第 二工位、 并用于控制每个所述第一阀片的开度的大小。 The hydraulic system according to claim 4 or 5, wherein the hydraulic system further comprises a condition adaptive controller, configured to control each of the first valves from the first according to operating conditions The station is switched to the second station and is used to control the size of the opening of each of the first valve sheets.
7. 根据权利要求 6所述的液压***， 其特征在于， 当各个所述第一执行机构的总 需求流量大于等于所述第一泵的输出流量时， 所述工况自适应控制器控制所述 第一多路换向阀中的每个所述第一阀片处于所述第一工位。 The hydraulic system according to claim 6, wherein when the total demand flow rate of each of the first actuators is greater than or equal to an output flow rate of the first pump, the operating condition adaptive controller control station Each of the first multi-way reversing valves is in the first station.
8. 根据权利要求 6所述的液压***， 其特征在于， 当各个所述第一执行机构的总 需求流量小于所述第一泵的输出流量、 且各个所述第二执行机构的总需求流量 小于等于所述第二泵的输出流量时， 所述工况自适应控制器控制所述第一多路 换向阀中的每个所述第一阀片处于所述第一工位。 8. The hydraulic system according to claim 6, wherein a total demand flow rate of each of the first actuators is smaller than an output flow rate of the first pump, and a total demand flow rate of each of the second actuators When the output flow rate of the second pump is less than or equal to, the operating condition adaptive controller controls each of the first multi-way reversing valves to be in the first station.
9. 根据权利要求 6所述的液压***， 其特征在于， 当各个所述第一执行机构的总 需求流量小于第一泵的输出流量、 且所述至少一个第二执行机构的需求流量大 于所述第二泵的输出流量时， 所述工况自适应控制器控制所述第一多路换向阀 中的至少一个所述第一阀片处于所述第二工位。 9. The hydraulic system according to claim 6, wherein when a total demand flow rate of each of the first actuators is smaller than an output flow rate of the first pump, and a demand flow rate of the at least one second actuator is greater than When the output flow rate of the second pump is described, the condition adaptive controller controls at least one of the first multi-way reversing valves to be in the second station.
10. 一种混凝土泵送设备， 其特征在于， 其包括根据权利要求 1-9中任一项所述的 液压***。 A concrete pumping apparatus, characterized in that it comprises a hydraulic system according to any one of claims 1-9.
11. 根据权利要求 10所述的混凝土泵送设备，其特征在于，所述液压***中的第一 液压子***是臂架支腿液压子***， 所述液压***中的第二液压子***是泵送 液压子***。 11. The concrete pumping apparatus according to claim 10, wherein the first hydraulic subsystem in the hydraulic system is a boom leg hydraulic system, and the second hydraulic subsystem in the hydraulic system is Pump the hydraulic subsystem.
12. 根据权利要求 11所述的混凝土泵送设备，其特征在于，所述液压***根据所述 混凝土泵送设备对其臂架的速度要求和 /或泵送的速度要求控制所述液压*** 的第一多路换向阀换向。 12. The concrete pumping apparatus according to claim 11, wherein the hydraulic system controls the hydraulic system according to a speed requirement of the concrete pumping device for its boom and/or a speed requirement of pumping The first multi-way reversing valve is reversed.
PCT/CN2011/079340 2011-09-05 2011-09-05 Concrete pumping equipment and hydraulic system thereof WO2013033884A1 (en)

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Publication number Priority date Publication date Assignee Title
JP2005331007A (en) * 2004-05-19 2005-12-02 Sumitomo (Shi) Construction Machinery Manufacturing Co Ltd Hydraulic circuit of hydraulic shovel
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