WO2023274210A1 - 一种多级压力控制和压力调速液压系统及作业机械 - Google Patents

一种多级压力控制和压力调速液压系统及作业机械 Download PDF

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WO2023274210A1
WO2023274210A1 PCT/CN2022/101820 CN2022101820W WO2023274210A1 WO 2023274210 A1 WO2023274210 A1 WO 2023274210A1 CN 2022101820 W CN2022101820 W CN 2022101820W WO 2023274210 A1 WO2023274210 A1 WO 2023274210A1
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oil
valve
pressure
speed regulation
hydraulic system
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PCT/CN2022/101820
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English (en)
French (fr)
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姜尚
蓝天
周丽云
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湖南三一中型起重机械有限公司
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Publication of WO2023274210A1 publication Critical patent/WO2023274210A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
    • F15B11/10—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor in which the servomotor position is a function of the pressure also pressure regulators as operating means for such systems, the device itself may be a position indicating system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/042—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in"
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor

Definitions

  • the present application relates to the field of operating equipment, in particular to a multi-stage pressure control and pressure speed regulating hydraulic system and an operating machine.
  • the hydraulic system of the crane chassis, the system actuators include the actions of multiple oil cylinders with different pressure levels and the actions of motor-driven fans that require speed regulation.
  • multiple relief valves and electromagnetic valves are used to control the pressure to achieve multi-stage pressure control.
  • the chassis engine speed changes at any time, the fixed value relief valve cannot meet the speed regulation requirements of the motor, and cannot control the motor speed, and when the engine speed is high, the motor speed may be oversaturated, the system load is too large, and it will not save energy.
  • the present application provides a multi-stage pressure control and pressure speed regulation hydraulic system and working machine, which are used to solve the problems that the existing hydraulic system cannot adjust the speed of the motor and has a complex structure.
  • This application provides a multi-stage pressure control and pressure speed regulation hydraulic system, including:
  • An electromagnetic reversing valve the first working oil port of the electromagnetic reversing valve communicates with the first oil port of the oil cylinder, and the second working oil port of the electromagnetic reversing valve communicates with the second oil port of the oil cylinder;
  • the regulating device includes a solenoid valve, a proportional relief valve and a shuttle valve, the oil inlet of the solenoid valve communicates with the oil outlet of the load sensing pump device, and the oil outlet of the solenoid valve communicates with the oil outlet of the shuttle valve.
  • the first oil port is connected, and the working oil port of the solenoid valve is connected between the second oil port of the shuttle valve and the first oil port of the motor device through the first oil passage; the third oil port of the shuttle valve
  • the second oil passage communicates with the oil inlet of the proportional relief valve, and the oil inlet of the load sensitive pump device communicates with the oil inlet of the proportional relief valve through the feedback oil passage; the electromagnetic commutation
  • the oil inlet of the valve communicates with the oil outlet of the solenoid valve through the third oil passage.
  • the control device further includes a first damper, a second damper and a third damper, the first damper is arranged on the first oil circuit, The second damper is arranged on the second oil circuit, and the third damper is arranged on the third oil circuit.
  • the oil cylinder includes a rod chamber and a rodless chamber, the first oil port of the oil cylinder communicates with the rodless chamber, and the cylinder's The second oil port communicates with the rod cavity.
  • the solenoid valve is a two-position four-way solenoid valve.
  • the electromagnetic reversing valve is a three-position four-way electromagnetic valve.
  • the proportional relief valve is an electric proportional relief valve.
  • the motor device includes a motor, a check valve and a first oil return tank, and the working oil ports of the electromagnetic valve pass through the first oil circuit respectively It communicates with the working oil port of the motor and the oil supply outlet of the one-way valve, and the first oil return tank is respectively connected with the oil supply inlet of the one-way valve, the oil drain port of the motor, and the oil supply port of the motor.
  • the oil return port is connected.
  • the multi-stage pressure control and pressure speed regulation hydraulic system also includes a second oil return tank and a third oil return tank, the second oil return tank communicates with the oil return port of the electromagnetic reversing valve, so The third oil return tank communicates with the oil outlet of the proportional relief valve.
  • the states of the multistage pressure control and pressure speed regulation hydraulic system include a standby state, a multistage pressure control state and a pressure speed regulation control state.
  • the switching between the multi-stage pressure control state and the pressure speed regulation control state is performed through the solenoid valve.
  • the present application also provides a work machine, including a main body of the work machine, and a multi-stage pressure control and pressure speed regulation hydraulic system as described in any one of the above, and the multi-stage pressure control and pressure speed regulation hydraulic system is arranged on the On the main body of the working machine.
  • the main body of the working machine is a crane or an excavator.
  • the multi-stage pressure control and pressure speed regulation hydraulic system replaces multiple relief valves and solenoid valves through proportional relief valves, and performs multi-stage pressure control for controlling load-sensitive pumps; in the case of different motor speeds, it can By adjusting the pressure of the proportional relief valve, the pressure difference between the front and rear of the control system is damped, so as to realize the flow control of the system and then adjust the speed of the motor.
  • the multi-stage pressure control and pressure speed regulation of the system are switched between the two states through the solenoid valve.
  • the pressure oil on the high pressure side of the system passes through the shuttle valve and damper in turn and enters the feedback oil circuit of the oil pump.
  • a proportional relief valve is set on the feedback oil circuit. The pressure change of the feedback oil circuit is controlled by low current to ensure that the output pressure of the sensitive pump does not change.
  • Fig. 1 is a structural schematic diagram of a multi-stage pressure control and pressure speed regulation hydraulic system provided by the present application.
  • Fig. 2 is a schematic structural diagram of a work machine provided by the present application.
  • Fig. 1 illustrates a structural schematic diagram of a multi-stage pressure control and pressure speed regulation hydraulic system.
  • the first working oil port of the electromagnetic reversing valve 3 communicates with the first oil port of the oil cylinder 4
  • the second working oil port of the electromagnetic reversing valve 3 communicates with the second oil port of the oil cylinder 4 .
  • the control device 12 includes a solenoid valve 2, a proportional relief valve 11 and a shuttle valve 6.
  • the oil inlet of the solenoid valve 2 is connected with the oil outlet of the load sensing pump device 1, and the oil outlet of the solenoid valve 2 is connected with the first oil outlet of the shuttle valve 6.
  • the working oil port of the solenoid valve 2 is connected between the second oil port of the shuttle valve 6 and the first oil port of the motor device 13 through the first oil circuit; the third oil port of the shuttle valve 6 is connected through the second oil port
  • the oil passage communicates with the oil inlet of the proportional relief valve 11, and the oil inlet of the load sensing pump device 1 communicates with the oil inlet of the proportional relief valve 11 through the feedback oil passage; the oil inlet of the electromagnetic reversing valve 3 passes through the first
  • the three oil passages communicate with the oil outlet of the solenoid valve 2.
  • the multi-stage pressure control and pressure speed regulation hydraulic system uses the proportional relief valve 11 to replace multiple relief valves and solenoid valves 2, and performs multi-stage pressure control to control the load-sensitive pump; in the case of different speeds of the motor 8 Next, by adjusting the pressure of the proportional relief valve 11, the pressure difference between the front and rear of the control system can be damped, so as to realize the flow control of the system, and then adjust the speed of the motor 8.
  • the two states of multi-stage pressure control and pressure speed regulation of the system are switched through the solenoid valve 2, and the pressure oil on the high pressure side of the system passes through the shuttle valve 6 and damped sequentially and then enters the feedback oil circuit of the oil pump, and a proportional overflow is set on the feedback oil circuit Valve 11 controls the pressure change of the feedback oil circuit through low current to ensure that the output pressure of the sensitive pump does not change.
  • the multi-stage pressure control and pressure-speed regulation hydraulic system of the present application has three states: standby state, multi-stage pressure control state and pressure speed-regulation control state, wherein the multi-stage pressure control state and pressure speed-regulation control state The switch between them is switched by solenoid valve 2.
  • the regulating device 12 also includes a first damper 7, a second damper 10 and a third damper 5, the first damper 7 is arranged on the first oil circuit, the second damper 10 is arranged on the second oil circuit, and the second damper 10 is arranged on the second oil circuit.
  • the third damper 5 is set on the third oil circuit.
  • the oil cylinder 4 includes a rod chamber and a rodless chamber, the first oil port of the oil cylinder 4 communicates with the rodless chamber, and the second oil port of the oil cylinder 4 communicates with the rod chamber.
  • the pressure of the cylinder 4 also needs to be adjusted due to the change of the load demand of the cylinder 4.
  • the load sensing pump device 1 is used to output hydraulic oil to drive the cylinder 4 and the motor 8 to work.
  • the proportional relief valve 11 is used to adjust the pressure of the hydraulic system, and the proportional relief valve 11 is used to replace multiple reliefs valve and solenoid valve 2 for multi-stage pressure control to control load sensing pumps.
  • the multi-stage pressure control and pressure speed regulation hydraulic system of the present application has a simpler structure and more diversified functions.
  • the first oil port of the oil cylinder 4 communicates with the rod chamber, and the second oil port of the oil cylinder 4 communicates with the rodless chamber.
  • the proportional relief valve 11 is an electric proportional relief valve.
  • the solenoid valve 2 is a two-position four-way solenoid valve.
  • the electromagnetic reversing valve 3 is a three-position four-way electromagnetic valve.
  • the motor device 13 includes a motor 8, a one-way valve 9 and a first oil return tank, and the working oil port of the solenoid valve 2 is respectively connected with the working oil port of the motor 8 and the one-way valve 9 through the first oil circuit.
  • the oil supply outlet is connected, and the first oil return tank is respectively connected with the oil supply inlet of the check valve 9, the oil drain port of the motor 8, and the oil return port of the motor 8.
  • the motor 8 is used to drive the load to rotate, and the load can be a fan blade, or a hoist or a chassis.
  • the multi-stage pressure control and pressure speed regulation hydraulic system of the present application adjusts the pressure of the proportional relief valve 11 according to the change of the rotation speed of the motor 8 to control the pressure difference between the front and rear of the system damping, thereby realizing the flow control of the system, and then adjusting the rotation speed of the motor 8 .
  • the multi-stage pressure control and pressure speed regulation hydraulic system also includes a second oil return tank and a third oil return tank, the second oil return tank communicates with the oil return port of the electromagnetic reversing valve 3, and the third oil return tank communicates with the oil return port of the electromagnetic reversing valve 3.
  • the oil outlet of the proportional relief valve 11 is connected.
  • the multi-stage pressure control and pressure speed regulation hydraulic system includes a load sensitive pump device 1, an electromagnetic reversing valve 3, a regulating device 12, a second oil return tank and a third oil return tank, wherein the electromagnetic valve 2 is The two-position four-way solenoid valve 2 and the electromagnetic reversing valve 3 are three-position four-way solenoid valves 2 .
  • the first working oil port of the electromagnetic reversing valve 3 communicates with the first oil port of the oil cylinder 4
  • the second working oil port of the electromagnetic reversing valve 3 communicates with the second oil port of the oil cylinder 4 .
  • the oil cylinder 4 includes a rod chamber and a rodless chamber, the first oil port of the oil cylinder 4 communicates with the rodless chamber, and the second oil port of the oil cylinder 4 communicates with the rod chamber.
  • the control device 12 includes a solenoid valve 2, a proportional overflow valve 11, a shuttle valve 6, a first damper 7, a second damper 10 and a third damper 5, the proportional overflow valve 11 is an electric proportional overflow valve, and the inlet of the solenoid valve 2
  • the oil port is connected with the oil outlet of the load sensing pump device 1
  • the oil outlet of the solenoid valve 2 is connected with the first oil port of the shuttle valve 6, and the working oil port of the solenoid valve 2 is connected with the first oil port of the shuttle valve 6 through the first oil passage.
  • the third oil port of the shuttle valve 6 communicates with the oil inlet of the proportional relief valve 11 through the second oil passage, and the oil inlet of the load sensing pump device 1
  • the oil inlet of the proportional relief valve 11 is communicated through the feedback oil passage;
  • the oil inlet of the electromagnetic reversing valve 3 is communicated with the oil outlet of the solenoid valve 2 through the third oil passage.
  • the first damper 7 is arranged on the first oil passage
  • the second damper 10 is arranged on the second oil passage
  • the third damper 5 is arranged on the third oil passage.
  • the second oil return tank communicates with the oil return port of the electromagnetic reversing valve 3
  • the third oil return tank communicates with the oil outlet of the proportional overflow valve 11
  • the motor device 13 includes a motor 8, a one-way valve 9 and a first oil return tank, and the electromagnetic
  • the working oil port of valve 2 communicates with the working oil port of motor 8 and the oil supply outlet of check valve 9 respectively through the first oil passage
  • the first oil return tank is connected with the oil supply inlet of check valve 9 and the oil drain of motor 8 respectively. port and the oil return port of the motor 8 are connected.
  • the multistage pressure control and pressure speed regulation hydraulic system of the present application has three states: standby state, multistage pressure control state and pressure speed regulation control state.
  • Multi-stage pressure control state When the oil cylinder 4 or other actuators of the system need to be controlled corresponding to different multi-stage pressures, the solenoid valve 2 is de-energized, and the electromagnetic reversing valve 3 is energized to control the oil cylinder 4 to perform telescopic movements.
  • the pressure oil passes through the shuttle valve 6 and the second damper 10 to the feedback oil circuit in turn, and the proportional relief valve 11 is given a current value corresponding to the demand pressure through the controller to adjust the pressure of the feedback oil circuit to realize the output of the load-sensitive pump device 1.
  • Multi-level pressure control The system can also realize constant pressure and constant flow control under the action of the third damper 5 when the pressure of the relief valve is not reached.
  • Fig. 2 is a schematic structural diagram of a work machine provided by the present application.
  • the work machine 14 includes a work machine main body 140, which also includes a multi-stage pressure control and pressure speed regulation hydraulic system 141 described in any one of the above, and the multi-stage pressure control and pressure speed regulation hydraulic system 141 is set on the main body 140 of the working machine.
  • the main body of the working machine is a crane or an excavator.
  • the multi-stage pressure control and pressure speed regulation hydraulic system is provided with a simpler structure and more diversified functions.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
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Abstract

一种多级压力控制和压力调速液压系统及作业机械，液压系统包括负载敏感泵装置（1）、电磁换向阀（3）和调控装置（12），电磁换向阀（3）的第一工作油口与油缸（4）的第一油口连通，电磁换向阀（3）的第二工作油口与油缸（4）的第二油口连通。通过比例溢流阀（11）来替代多个溢流阀和电磁阀，对控制负载敏感泵进行多级压力控制；在马达（8）转速不同的情况下，可以通过调整比例溢流阀（11）的压力，控制系统阻尼前后压差，从而实现系统流量控制，进而调节马达（8）的转速。系统的多级压力控制与压力调速两种状态之间通过电磁阀（2）进行切换，系统高压侧的压力油依次通过梭阀（6）和阻尼后进入油泵反馈油路，在反馈油路上设置比例溢流阀（11），通过低电流控制反馈油路的压力变化，保证负载敏感泵输出压力不发生变化。

Description

一种多级压力控制和压力调速液压系统及作业机械 技术领域
本申请涉及作业设备领域，尤其涉及一种多级压力控制和压力调速液压系统及作业机械。
发明背景
起重机底盘液压系统，系统执行元件包括多个不同压力等级的油缸动作和需要调速的马达驱动风扇动作。而现有技术均通过多个溢流阀和电磁阀来进行控制，来实现多级压力控制。且底盘发动机转速随时变化，定值溢流阀无法实现对马达的调速需求，无法控制马达转速，且发动机转速高时，可能出现马达转速过饱和、系统负载过大，不节能。
发明内容
本申请提供一种多级压力控制和压力调速液压系统及作业机械，用以解决现有的液压系统存在无法对马达进行速度调节，以及结构复杂的问题。
本申请提供一种多级压力控制和压力调速液压系统，包括：
负载敏感泵装置；
电磁换向阀，所述电磁换向阀的第一工作油口与油缸的第一油口连通，所述电磁换向阀的第二工作油口与所述油缸的第二油口连通；
调控装置，包括电磁阀、比例溢流阀和梭阀，所述电磁阀的进油口与所述负载敏感泵装置的出油口连通，所述电磁阀的出油口与所述梭阀的第一油口连通，所述电磁阀的工作油口通过第一油路连通于所述梭阀的第二油口和马达装置的第一油口之间；所述梭阀的第三油口通过第二油路与所述比例溢流阀的进油口连通，所述负载敏感泵装置的进油口通过反馈油路与所述比例溢流阀的进油口连通；所述电磁换向阀的进油口通过第三油路与所述电磁阀的出油口连通。
根据本申请提供的一种多级压力控制和压力调速液压系统，所述调控装置还包括第一阻尼、第二阻尼和第三阻尼，所述第一阻尼设置于所述第一油路上，所述第二阻尼设置于第二油路上，所述第三阻尼设置于第三油路上。
根据本申请提供的一种多级压力控制和压力调速液压系统，所述油缸包括有杆腔和无杆腔，所述油缸的第一油口与所述无杆腔连通，所述油缸的第二油口与所述有杆腔连通。
根据本申请提供的一种多级压力控制和压力调速液压系统，所述电磁阀为两位四通电磁阀。
根据本申请提供的一种多级压力控制和压力调速液压系统，所述电磁换向阀为三位四通电磁阀。
根据本申请提供的一种多级压力控制和压力调速液压系统，所述比例溢流阀为电比例溢流阀。
根据本申请提供的一种多级压力控制和压力调速液压系统，所述马达装置包括马达、单向阀和第一回油箱，所述电磁阀的工作油口通过所述第一油路分别与所述马达的工作油口、所述单向阀的补油出口连通，所述第一回油箱分别与所述单向阀的补油入口、所述马达的泄油口、所述马达的回油口连通。
根据本申请提供的一种多级压力控制和压力调速液压系统，还包括第二回油箱和第三回油箱，所述第二回油箱与所述电磁换向阀的回油口连通，所述第三回油箱与所述比例溢流阀的出油口连通。
根据本申请提供的一种多级压力控制和压力调速液压系统，所述多级压力控制和压力调速液压系统的状态包括待机状态、多级压力控制状态和压力调速控制状态。
根据本申请提供的一种多级压力控制和压力调速液压系统，所述多级压力控制状态与所述压力调速控制状态之间的切换是通过所述电磁阀进行切换。
本申请还提供一种作业机械，包括作业机械主体，还包括如上任意一项所述的多级压力控制和压力调速液压系统，所述多级压力控制和压力调速液压系统设置于所述作业机械主体上。
根据本申请提供的作业机械，所述作业机械主体为起重机或挖掘机。
本申请提供的多级压力控制和压力调速液压系统通过比例溢流阀来替代多个溢流阀和电磁阀，对控制负载敏感泵进行多级压力控制；在马达转速不同的情况下，可以通过调整比例溢流阀的压力，控制系统阻尼前后压差，从而实现系统流量控制，进而调节马达的转速。系统的多级压力控制与压力调速两种状态之间通过电磁阀进行切换，系统高压侧的压力油依次通过梭阀和阻尼后进入油泵反馈油路，在反馈油路上设置比例溢流阀，通过低电流控制反馈油路的压力变化，保证敏感泵输出压力不发生变化。
附图简要说明
为了更清楚地说明本申请或现有技术中的技术方案，下面将对实施例或现有技术描述中所需要使用的附图作简单地介绍，显而易见地，下面描述中的附图是本申请的一些实施例，对于本领域普通技术人员来讲，在不付出创造性劳动的前提下，还可以根据这些附图获得其他的附图。
图1是本申请提供的一种多级压力控制和压力调速液压系统的结构示意图。
图2是本申请提供的一种作业机械的结构示意图。
附图标记：
1、负载敏感泵装置；2、电磁阀；3、电磁换向阀；4、油缸；5、第三阻尼；6、梭阀；7、第一阻尼；8、马达；9、单向阀；10、第二阻尼；11、比例溢流阀；12、调控装置；13、马达装置；14、作业机械。
实施本发明的方式
为使本申请的目的、技术方案和优点更加清楚，下面将结合本发明申请中的附图，对本申请中的技术方案进行清楚、完整地描述，显然，所描述的实施例是本申请一部分实施例，而不是全部的实施例。基于本申请中的实施例，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，都属于本申请保护的范围。
下面结合图1描述本申请的多级压力控制和压力调速液压系统及作业机械。
图1示例了一种多级压力控制和压力调速液压系统的结构示意图，如图1所示，多级压力控制和压力调速液压系统包括负载敏感泵装置1、电磁换向阀3和调控装置12，电磁换向阀3的第一工作油口与油缸4的第一油口连通，电磁换向阀3的第二工作油口与油缸4的第二油口连通。调控装置12包括电磁阀2、比例溢流阀11和梭阀6，电磁阀2的进油口与负载敏感泵装置1的出油口连通，电磁阀2的出油口与梭阀6的第一油口连通，电磁阀2的工作油口通过第一油路连通于梭阀6的第二油口和马达装置13的第一油口之间；梭阀6的第三油口通过第二油路与比例溢流阀11的进油口连通，负载敏感泵装置1的进油口通过反馈油路与比例溢流阀11的进油口连通；电磁换向阀3的进油口通过第三油路与电磁阀2的出油口连通。
本申请提供的多级压力控制和压力调速液压系统通过比例溢流阀11来替代多个溢流阀和电磁阀2，对控制负载敏感泵进行多级压力控制；在马达8转速不同的情况下，可以通过调整比例溢流阀11的压力，控制系统阻尼前后压差，从而实现系统流量控制，进而调节马达8的转速。系统的多级压力控制与压力调速两种状态之间通过电磁阀2进行切换，系统高压侧的压力油依次通过梭阀6和阻尼后进入油泵反馈油路，在反馈油路上设置比例溢流阀11，通过低电流控制反馈油路的压力变化，保证敏感泵输出压力不发生变化。
示例性地，本申请的多级压力控制和压力调速液压系统具有待机状态、多级压力控制状态和压力调速控制状态三种状态，其中，多级压力控制状态与压力调速控制状态之间的切换是通过电磁阀2进行切换。
根据本申请的实施例，调控装置12还包括第一阻尼7、第二阻尼10和第三 阻尼5，第一阻尼7设置于第一油路上，第二阻尼10设置于第二油路上，第三阻尼5设置于第三油路上。
根据本申请的实施例，油缸4包括有杆腔和无杆腔，油缸4的第一油口与无杆腔连通，油缸4的第二油口与有杆腔连通。油缸4工作时，由于油缸4的负载需求变化，油缸4的压力也需要随同调整，通过控制输入有杆腔和无杆腔内的液压油的压力，来控制油缸4输出相匹配的动力。负载敏感泵装置1用于输出液压油驱动油缸4和马达8工作，在多级压力控制状态，比例溢流阀11用于调节液压系统的压力，通过比例溢流阀11来替代多个溢流阀和电磁阀2，对控制负载敏感泵进行多级压力控制。相较于现有的液压控制系统，本申请的多级压力控制和压力调速液压系统，结构更简单，功能更多样化。
根据本申请的一个实施例，油缸4的第一油口与有杆腔连通，油缸4的第二油口与无杆腔连通。
根据本申请的实施例，比例溢流阀11为电比例溢流阀。
根据本申请的实施例，电磁阀2为两位四通电磁阀。
根据本申请的实施例，电磁换向阀3为三位四通电磁阀。
根据本申请的实施例，马达装置13包括马达8、单向阀9和第一回油箱，电磁阀2的工作油口通过第一油路分别与马达8的工作油口、单向阀9的补油出口连通，第一回油箱分别与单向阀9的补油入口、马达8的泄油口、马达8的回油口连通。马达8用于驱动负载转动，负载可以是扇叶，也可以是卷扬机或底盘。现有的液压系统由于无法对马达8进行转速控制，当马达8转速高时，可能出现马达8转速过饱和系统负载过大，不节能。而本申请的多级压力控制和压力调速液压系统根据马达8的转速变化，通过调整比例溢流阀11的压力，控制系统阻尼前后压差，从而实现系统流量控制，进而调节马达8的转速。
根据本申请的实施例，多级压力控制和压力调速液压系统还包括第二回油箱和第三回油箱，第二回油箱与电磁换向阀3的回油口连通，第三回油箱与比例溢流阀11的出油口连通。
根据本申请的实施例，多级压力控制和压力调速液压系统包括负载敏感泵装置1、电磁换向阀3、调控装置12、第二回油箱和第三回油箱，其中，电磁阀2为两位四通电磁阀2，电磁换向阀3为三位四通电磁阀2。电磁换向阀3的第一工作油口与油缸4的第一油口连通，电磁换向阀3的第二工作油口与油缸4的第二油口连通。油缸4包括有杆腔和无杆腔，油缸4的第一油口与无杆腔连通，油缸4的第二油口与有杆腔连通。
调控装置12包括电磁阀2、比例溢流阀11、梭阀6、第一阻尼7、第二阻尼10和第三阻尼5，比例溢流阀11为电比例溢流阀，电磁阀2的进油口与负载敏感泵装置1的出油口连通，电磁阀2的出油口与梭阀6的第一油口连通，电磁阀2 的工作油口通过第一油路连通于梭阀6的第二油口和马达装置13的第一油口之间；梭阀6的第三油口通过第二油路与比例溢流阀11的进油口连通，负载敏感泵装置1的进油口通过反馈油路与比例溢流阀11的进油口连通；电磁换向阀3的进油口通过第三油路与电磁阀2的出油口连通。第一阻尼7设置于第一油路上，第二阻尼10设置于第二油路上，第三阻尼5设置于第三油路上。
第二回油箱与电磁换向阀3的回油口连通，第三回油箱与比例溢流阀11的出油口连通，马达装置13包括马达8、单向阀9和第一回油箱，电磁阀2的工作油口通过第一油路分别与马达8的工作油口、单向阀9的补油出口连通，第一回油箱分别与单向阀9的补油入口、马达8的泄油口、马达8的回油口连通。
本申请的多级压力控制和压力调速液压系统具有待机状态、多级压力控制状态和压力调速控制状态三种状态。
(1)、待机状态：当系统不需要工作时，比例溢流阀11不得电，比例溢流阀11的压力为零，使负载敏感泵装置1的反馈油路压力为零，此时负载敏感泵装置1处于待机压力状态。
(2)、多级压力控制状态：当系统的油缸4或者其他执行元件需要对应不同的多级压力进行控制时，电磁阀2不得电，电磁换向阀3得电控制油缸4进行伸缩动作。压力油依次通过梭阀6、第二阻尼10至反馈油路，通过控制器给比例溢流阀11赋予与需求压力对应的电流值，调整反馈油路的压力，实现对负载敏感泵装置1输出多级压力控制。该系统在未达到溢流阀压力时，在第三阻尼5的作用下，还可实现恒压恒流控制。
(3)、压力调速控制状态：需要对系统的马达8转速进行控制时，电磁阀2得电，压力油给马达8供油，同时压力油依次通过梭阀6、第二阻尼10至反馈油路，控制器给比例溢流阀11赋予对应的电流值，调整反馈油路压力。在马达8转速不同的情况下，都可以通过控制第一阻尼7前后的压差，实现系统流量控制，进而调节马达8的转速。系统在多级压力控制状态与压力调速控制状态之间切换是依靠电磁阀2进行切换。
图2是本申请提供的一种作业机械的结构示意图。如图2所示，作业机械14包括作业机械主体140，其中，还包括上述任意一项所述的多级压力控制和压力调速液压系统141，多级压力控制和压力调速液压系统141设置于作业机械主体140上。作业机械主体为起重机或挖掘机。
本申请的实施例提供的作业机械，设置的多级压力控制和压力调速液压系统结构更简单，功能更多样化。
最后：以上实施例仅用以说明本申请的技术方案，而非对其限制；尽管参照前述实施例对本申请进行了详细的说明，本领域的普通技术人员应当理解：其依然可以对前述各实施例所记载的技术方案进行修改，或者对其中部分技术特征进 行等同替换；而这些修改或者替换，并不使相应技术方案的本质脱离本申请各实施例技术方案的精神和范围。

Claims (12)

  1. 一种多级压力控制和压力调速液压系统，包括：
    负载敏感泵装置；
    电磁换向阀，所述电磁换向阀的第一工作油口与油缸的第一油口连通，所述电磁换向阀的第二工作油口与所述油缸的第二油口连通；
    调控装置，包括电磁阀、比例溢流阀和梭阀，所述电磁阀的进油口与所述负载敏感泵装置的出油口连通，所述电磁阀的出油口与所述梭阀的第一油口连通，所述电磁阀的工作油口通过第一油路连通于所述梭阀的第二油口和马达装置的第一油口之间；所述梭阀的第三油口通过第二油路与所述比例溢流阀的进油口连通，所述负载敏感泵装置的进油口通过反馈油路与所述比例溢流阀的进油口连通；所述电磁换向阀的进油口通过第三油路与所述电磁阀的出油口连通。
  2. 根据权利要求1所述的多级压力控制和压力调速液压系统，其中，所述调控装置还包括第一阻尼、第二阻尼和第三阻尼，所述第一阻尼设置于所述第一油路上，所述第二阻尼设置于第二油路上，所述第三阻尼设置于第三油路上。
  3. 根据权利要求1或2所述的多级压力控制和压力调速液压系统，其中，所述油缸包括有杆腔和无杆腔，所述油缸的第一油口与所述无杆腔连通，所述油缸的第二油口与所述有杆腔连通。
  4. 根据权利要求1至3任一项所述的多级压力控制和压力调速液压系统，其中，所述电磁阀为两位四通电磁阀。
  5. 根据权利要求1至4任一项所述的多级压力控制和压力调速液压系统，其中，所述电磁换向阀为三位四通电磁阀。
  6. 根据权利要求1至5任一项所述的多级压力控制和压力调速液压系统，其中，所述比例溢流阀为电比例溢流阀。
  7. 根据权利要求1至6任一项所述的多级压力控制和压力调速液压系统，其中，所述马达装置包括马达、单向阀和第一回油箱，所述电磁阀的工作油口通过所述第一油路分别与所述马达的工作油口、所述单向阀的补油出口连通，所述第一回油箱分别与所述单向阀的补油入口、所述马达的泄油口、所述马达的回油口连通。
  8. 根据权利要求7所述的多级压力控制和压力调速液压系统，其中，还包括第二回油箱和第三回油箱，所述第二回油箱与所述电磁换向阀的回油口连通，所述第三回油箱与所述比例溢流阀的出油口连通。
  9. 根据权利要求1至8任一项所述的多级压力控制和压力调速液压系统，其中，所述多级压力控制和压力调速液压系统的状态包括待机状态、多级压力控制 状态和压力调速控制状态。
  10. 根据权利要求9所述的多级压力控制和压力调速液压系统，其中，所述多级压力控制状态与所述压力调速控制状态之间的切换是通过所述电磁阀进行切换。
  11. 一种作业机械，包括作业机械主体，其中，还包括权利要求1至10中任意一项所述的多级压力控制和压力调速液压系统，所述多级压力控制和压力调速液压系统设置于所述作业机械主体上。
  12. 根据权利要求11所述的作业机械，其中，所述作业机械主体为起重机或挖掘机。
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