WO2021226791A1 - 负载敏感泵系统、液压控制系统和工程机械 - Google Patents

负载敏感泵系统、液压控制系统和工程机械 Download PDF

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Publication number
WO2021226791A1
WO2021226791A1 PCT/CN2020/089616 CN2020089616W WO2021226791A1 WO 2021226791 A1 WO2021226791 A1 WO 2021226791A1 CN 2020089616 W CN2020089616 W CN 2020089616W WO 2021226791 A1 WO2021226791 A1 WO 2021226791A1
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Prior art keywords
control
variable
oil
valve
pump
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PCT/CN2020/089616
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English (en)
French (fr)
Inventor
向小强
刘东宏
仝猛
王建成
陈龙
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徐州重型机械有限公司
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Application filed by 徐州重型机械有限公司 filed Critical 徐州重型机械有限公司
Priority to PCT/CN2020/089616 priority Critical patent/WO2021226791A1/zh
Priority to BR112022022935A priority patent/BR112022022935A2/pt
Publication of WO2021226791A1 publication Critical patent/WO2021226791A1/zh

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    • 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
    • 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

Definitions

  • the present disclosure relates to the technical field of construction machinery, and in particular to a load-sensitive pump system, hydraulic control system and construction machinery.
  • the power unit of the crane mostly uses an engine-driven hydraulic pump set to provide power for the crane’s loading operation system (winding, luffing, telescoping and slewing, etc.).
  • the output torque of the engine changes with the increase in speed and the trend is first to increase and then Decrease, the maximum torque point is often in the middle speed range, and the output torque is very low at low speeds. For example, at 800rpm, the output torque is 800Nm and at 1400rpm it reaches 1600Nm.
  • a load-sensitive pump system is commonly used in crane hydraulic systems, which uses a hydraulic control handle to control a load-sensitive multi-way valve.
  • the valve has a load-sensitive oil circuit connected to a load-sensitive pump.
  • the purpose of the present disclosure is to provide a load-sensing pump system, hydraulic control system and construction machinery, which can effectively improve the utilization rate of the driving mechanism.
  • Some embodiments of the present disclosure provide a load sensing pump system, including:
  • Quantitative pump driven by the same driving mechanism as variable pump
  • Variable control mechanism used to control variable pump
  • the pressure taking valve is configured to act part of the output pressure of the quantitative pump on the control end of the variable control mechanism through the control oil circuit, so as to increase the maximum displacement of the variable pump when the driving speed of the driving mechanism increases.
  • the pressure taking valve is a fixed ratio pressure taking valve, and a part of the output pressure acting on the control end of the variable control mechanism is configured to increase as the working oil pressure of the quantitative pump increases.
  • the pressure taking valve has a first oil inlet, a first oil outlet, and a second oil outlet.
  • the pressure taking valve includes a damping and hydraulic control proportional valve.
  • the oil ports are connected, the damping is arranged on the passage between the first oil inlet and the first oil outlet, the hydraulic proportional valve is arranged on the passage between the first oil inlet and the second oil outlet, the first of the hydraulic proportional valve is The control end is communicated with the first oil inlet, the second control end of the hydraulic proportional valve is communicated with the first oil outlet and the second oil outlet, and the second oil outlet is communicated with the control end of the variable control mechanism.
  • the variable control mechanism includes a power control valve and a variable cylinder used to control the swash plate swing angle of the variable pump.
  • the power control valve can change the oil supply of the control oil circuit to the variable cylinder to achieve the displacement of the variable pump.
  • the variable working oil port of the variable pump communicates with the first control end of the power control valve through the control oil circuit, and the pressure valve acts on the second control end of the power control valve through the control oil circuit part of the output pressure of the quantitative pump.
  • control oil circuit supplies oil to the rodless cavity of the variable cylinder
  • the piston rod of the variable cylinder is used to control the swash plate swing angle of the variable pump
  • the power control valve is a hydraulic proportional valve.
  • the variable pump supplies oil to the rodless cavity of the variable cylinder through the power control valve.
  • the spool of the power control valve is in the second control position, the rodless cavity of the variable cylinder is discharged through the power control valve. Oil.
  • the piston rod is provided with a swash plate swing angle feedback member, and a swash plate swing angle feedback spring in a pre-compressed state is provided between the swash plate swing angle feedback member and the second control end of the power control valve.
  • variable control mechanism further includes a flow control valve and a pressure control valve arranged on the control oil circuit.
  • the load feedback end of the flow control valve is communicated with the load feedback port, and the control oil of the control oil circuit is operated by the variable pump The oil circuit is provided.
  • Some embodiments of the present disclosure provide a hydraulic control system including the aforementioned load sensing pump system.
  • Some embodiments of the present disclosure provide an engineering machine including the aforementioned load sensing pump system.
  • the construction machine is a crane.
  • the pressure taking valve introduces part of the pressure change signal of the quantitative pump into the control end of the variable control mechanism, so that the variable control mechanism can increase the variable pump when the driving speed of the drive mechanism increases.
  • the load-sensing pump system of the present disclosure does not require additional electrical controllers or wiring harnesses. Through its own hydraulic control oil circuit, it achieves the effect of variable power control with speed, and has high implementability.
  • Fig. 1 is a schematic structural principle diagram of some embodiments of the load-sensing pump system of the present disclosure.
  • a specific device when it is described that a specific device is located between the first device and the second device, there may or may not be an intermediate device between the specific device and the first device or the second device.
  • the specific device When it is described that a specific device is connected to other devices, the specific device may be directly connected to other devices without intervening devices, or may not be directly connected to other devices but with intervening devices.
  • variable control methods for variable pumps include pressure control, flow control and power control.
  • Pressure control is to limit the maximum pressure of the variable pump outlet within the control range of the variable pump.
  • the variable pump only provides actuators.
  • the required hydraulic oil flow if the working pressure exceeds the pressure setting value set at the pressure valve, the variable pump will adjust to a smaller displacement to reduce the control deviation;
  • flow control is through the use of a variable orifice (such as a directional valve) ) To adjust the pressure difference between the upstream and downstream of the orifice. This pressure difference controls the flow of the variable pump.
  • some embodiments of the present disclosure provide a load-sensitive pump system, including: variable pump 1; fixed pump 2, driven by the same driving mechanism as variable pump 1; variable control mechanism for controlling the variable pump 1; Control oil circuit; and pressure valve 3, configured to act part of the output pressure of the quantitative pump 2 on the control end of the variable control mechanism through the control oil circuit to increase the variable pump when the driving speed of the drive mechanism increases The maximum displacement of 1.
  • variable pump 1 and quantitative pump 2 are driven by the same driving mechanism, for example, driven by an engine.
  • the rotational speeds of variable pump 1 and quantitative pump 2 are communicated with each other.
  • the speed of the drive mechanism is also increased accordingly.
  • the pressure taking valve 3 introduces part of the pressure change signal of the quantitative pump into the control end of the variable control mechanism, so that the variable control mechanism can increase when the drive speed of the drive mechanism increases.
  • the maximum displacement of the variable pump 1 realizes variable control of the power of the variable pump under different input speeds, so that the power utilization rate of the hydraulic pump is improved, which can effectively reduce the maximum working speed of the driving mechanism and realize the energy-saving effect of the hydraulic system.
  • the load-sensing pump system of the present disclosure does not require additional electrical controllers or wiring harnesses, and realizes the effect of variable power control with speed through its own hydraulic control oil circuit, and has high implementability.
  • the pressure-taking valve 3 is a constant-proportional pressure-taking valve, and part of the output pressure acting on the control end of the variable control mechanism is configured to increase as the working oil pressure of the quantitative pump 2 increases, so as to be accurate Obtain the speed change signal of the driving mechanism, effectively improving the control accuracy.
  • the pressure taking valve 3 has a first oil inlet P1, a first oil outlet P2, and a second oil outlet P3.
  • the pressure taking valve 3 includes The damping 31 and the hydraulic control proportional valve 32, the quantitative working oil port B2 of the quantitative pump 2 communicates with the first oil inlet P1, the damping 31 is arranged on the passage between the first oil inlet P1 and the first oil outlet P2, and the hydraulic control
  • the proportional valve 32 is arranged on the passage between the first oil inlet P1 and the second oil outlet P3.
  • the first control end of the hydraulic proportional valve 32 communicates with the first oil inlet P1.
  • the second control of the hydraulic proportional valve 32 is The end is in communication with the first oil outlet P2 and the second oil outlet P3, and the second oil outlet P3 is in communication with the control end of the variable control mechanism.
  • the damping 31 plays the role of reducing pressure.
  • the oil pressure of the first oil inlet P1 acts on the first control end of the hydraulic control proportional valve 32, the first oil outlet P2 and the second oil outlet
  • the oil pressure of port P3 acts on the second control end of the hydraulic control proportional valve 32.
  • the first oil inlet P1 The oil pressure is equal to the sum of the oil pressure at the first oil outlet P2 and the second oil outlet P3, that is, the oil pressure at the second oil outlet P3 is equal to the oil pressure at the first oil inlet P1 minus the first oil outlet
  • the oil pressure of P2 and the oil pressure of the second oil outlet P3 are the pressure drop produced by the damping 31.
  • the damping 31 is reduced proportionally, when the oil pressure of the first oil inlet P1 increases, the first outlet The oil pressure of the oil port P2 and the oil pressure of the second oil outlet P3 both increase, and the oil pressure of the second oil outlet P3 is applied to the control end of the variable control mechanism, so that the variable control when the driving speed of the driving mechanism increases
  • the mechanism can increase the maximum displacement of the variable pump 1.
  • the oil pressure of the second oil outlet P3 is only a small part of the oil pressure of the first oil outlet P2, and the oil pressure of the first oil outlet P2 accounts for the majority, so the setting of the pressure valve 3 It will not affect the power output of the first oil outlet P2 as the working power output port.
  • the variable control mechanism includes a power control valve 6 and a variable cylinder 7 for controlling the swash plate swing angle of the variable pump 1.
  • the power control valve 6 can be changed. Control the oil supply of the oil circuit to the variable cylinder 7 to realize the adjustable displacement of the variable pump 1.
  • the variable working oil port B1 of the variable pump 1 passes through the control oil circuit and the first control end of the power control valve 6 (left in Figure 1 The control end) is connected, and the pressure taking valve 3 acts on the second control end (the right control end in Fig.
  • the control oil circuit supplies oil to the rodless cavity of the variable cylinder 7, the piston rod of the variable cylinder 7 is used to control the swash plate swing angle of the variable pump 1, and the power control valve 6 is hydraulically controlled.
  • Proportional valve when the spool of the power control valve 6 is in the first control position (the left position shown in Figure 1), the variable pump 1 supplies oil to the rodless cavity of the variable cylinder 7 through the power control valve 6, and in the power control When the spool of the valve 6 is in the second control position (the right position shown in FIG. 1 ), the rodless cavity of the variable cylinder 7 drains oil through the power control valve 6.
  • the oil pressure of the second oil outlet P3 acts on the second control end of the power control valve 6, which is beneficial to maintaining the power control valve 6 in the second control position (right position shown in Figure 1)
  • the swash angle of the controlled variable pump 1 is increased, thereby increasing the displacement of the variable pump 1.
  • the piston rod is provided with a swash plate swing angle feedback member 8, and the swash plate swing angle feedback member 8 and the second control end of the power control valve 6 are provided in a pre-compressed state.
  • the swashplate swing angle feedback spring 9. By setting the swash plate swing angle feedback spring 9 in the pre-stressed state, the oil pressure of the second oil outlet P3 and the swash plate swing angle feedback spring 9 act together on the second control end of the power control valve 6, and act on the power The oil pressure of the variable working oil port B1 of the variable pump 1 at the first control end of the control valve 6 is balanced.
  • variable control mechanism further includes a flow control valve 5 and a pressure control valve 4 arranged on the control oil circuit, and the load feedback end of the flow control valve 5 In communication with the load feedback port X, the control oil of the control oil circuit is provided by the working oil circuit of the variable pump 1.
  • the flow control valve 5 and the pressure control valve 4 are technical means known in the art and will not be repeated here.
  • Fig. 1 The following takes the embodiment shown in Fig. 1 as an example and is applied to a crane, and the driving mechanism is an engine as an example to illustrate the control principle of the load-sensing pump system of the present disclosure as follows:
  • variable pump 1 When the crane is on the truck, the engine speed usually works at a low speed, and the maximum output torque of the engine is low. In order to prevent the engine turtle from stalling due to excessive load, the variable pump 1 needs to limit its maximum displacement output.
  • the power control valve 6 moves the spool to the right to the left under the action of the oil pressure of the variable working port B1 of the variable pump 1, and then drives the swash plate swing angle feedback
  • the part 8 and the piston rod move to the right, and the variable pump 1 supplies oil to the rodless cavity of the variable cylinder 7 through the power control valve 6, so that the piston rod moves to the left, and finally balances, so that the pump displacement is stable at Vmax1;
  • the oil pressure of the second oil outlet P3 output by the pressure taking valve 3 increases correspondingly with the speed, and the pressure output to the control port Y of the variable pump 1 also increases.
  • the power control valve 6 can move left to work to the right position.
  • the rodless cavity of the variable cylinder 7 drains oil through the power control valve 6, causing the piston rod to move to the left.
  • the pump displacement stabilizes at Vmax2. Compared with the maximum displacement Vmax1 of the variable pump at the same speed, the displacement is increased, and the system output torque is also increased accordingly. In this way, at the same large speed, the displacement of the variable pump 1 increases, and the hydraulic system Higher power utilization;
  • the pressure control valve 4 is used to limit the maximum pressure of the variable pump 1. When the outlet pressure of the variable pump 1 exceeds this value, the outlet pressure of the variable pump 1 directly acts on the rodless cavity of the variable cylinder 7, so that the displacement of the variable pump 1 reduce.
  • Some embodiments of the present disclosure provide a hydraulic control system including the aforementioned load sensing pump system.
  • Some embodiments of the present disclosure provide an engineering machine including the aforementioned load sensing pump system.
  • the load sensing pump system of the present disclosure is particularly suitable for cranes. Therefore, in some embodiments, the construction machinery is a crane.

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Abstract

一种负载敏感泵系统、液压控制系统和工程机械，负载敏感泵系统包括：变量泵（1）；定量泵（2），与变量泵（1）由同一驱动机构驱动；变量控制机构，用于控制变量泵（1）；控制油路；以及取压阀（3），被配置为通过控制油路将定量泵（2）的部分输出压力作用于变量控制机构的控制端，以在驱动机构的驱动转速升高时增大变量泵（1）的最大排量。

Description

负载敏感泵系统、液压控制系统和工程机械 技术领域
本公开涉及工程机械技术领域，尤其涉及一种负载敏感泵系统、液压控制系统和工程机械。
背景技术
起重机的动力装置多采用发动机驱动液压泵组，为起重机的上车作业系统(卷扬、变幅、伸缩和回转等)提供动力，发动机的输出扭矩随转速升高的变化趋势为先升高后降低，最大扭矩点往往在中间转速段，而在低转速下输出扭矩很低，比如800rpm时，输出扭矩在800Nm，在1400rpm下达到1600Nm。
起重机液压系统常用到一种负载敏感泵系统，采用液控手柄控制负载敏感多路阀，其阀上有负载敏感油路连接到一种负载敏感泵上，通过控制多路阀的开度大小，实现系统调速的效果，另外，也可通过控制发动机的转速，改变液压泵的转速提高系统输出流量。
由液压泵的输入扭矩公式T＝P*V/2π可知，负载压力P越大，其泵的排量则有个最大限值Vmax，否则扭矩T就超过当前发动机的输出扭矩，会导致发动机熄火，为此，起重机产品在选用负载敏感泵时，通常都带恒功率控制功能(LA)，根据动力单元在最低转速下的输入扭矩而定，其设置值固定之后，即使发动机转速升高，能提供的扭矩增大，在泵出口压力达到一定值后泵的排量依然会降低，最终使得液压系统的输出功率降低，发动机的功率利用率降低，相比而言，系统能耗大，不节能。
发明内容
本公开的目的在于提供一种负载敏感泵系统、液压控制系统和工程机械，能够有效提升驱动机构的利用率。
本公开的一些实施例提供了一种负载敏感泵系统，包括：
变量泵；
定量泵，与变量泵由同一驱动机构驱动；
变量控制机构，用于控制变量泵；
控制油路；以及
取压阀，被配置为通过控制油路将定量泵的部分输出压力作用于变量控制机构的控制端，以在驱动机构的驱动转速升高时增大变量泵的最大排量。
在一些实施例中，取压阀为定比例取压阀，作用于变量控制机构的控制端的部分输出压力被配置为随着定量泵的工作油压的增大而增大。
在一些实施例中，取压阀具有第一进油口，第一出油口和第二出油口，取压阀包括阻尼和液控比例阀，定量泵的定量工作油口与第一进油口相通，阻尼设置在第一进油口和第一出油口的通路上，液控比例阀设置在第一进油口和第二出油口的通路上，液控比例阀的第一控制端与第一进油口相通，液控比例阀的第二控制端与第一出油口和第二出油口均相通，第二出油口与变量控制机构的控制端相通。
在一些实施例中，变量控制机构包括功率控制阀和用于控制变量泵的斜盘摆角的变量缸，功率控制阀能够改变控制油路对变量缸的供油量来实现变量泵的排量可调，变量泵的变量工作油口通过控制油路与功率控制阀的第一控制端相通，取压阀通过控制油路将定量泵的部分输出压力作用于功率控制阀的第二控制端。
在一些实施例中，控制油路向变量缸的无杆腔供油，变量缸的活塞杆用于控制变量泵的斜盘摆角，功率控制阀为液控比例阀，在功率控制阀的阀芯处于第一控制位状态下，变量泵通过功率控制阀向变量缸的无杆腔供油，在功率控制阀的阀芯处于第二控制位状态下，变量缸的无杆腔通过功率控制阀泄油。
在一些实施例中，活塞杆设有斜盘摆角反馈件，斜盘摆角反馈件和功率控制阀的第二控制端之间设有处于预压紧状态的斜盘摆角反馈弹簧。
在一些实施例中，变量控制机构还包括设置在控制油路上的流量控制阀和压力控制阀，流量控制阀的负载反馈端与负载反馈口相通，控制油路的控制油液由变量泵的工作油路提供。
本公开的一些实施例提供了一种液压控制系统，包括前述负载敏感泵系统。
本公开的一些实施例提供了一种工程机械，包括前述负载敏感泵系统。
在一些实施例中，工程机械为起重机。
基于本公开提供的技术方案，通过设置取压阀，取压阀将定量泵的部分压力变化信号引入变量控制机构的控制端，使得驱动机构的驱动转速升高时变量控制机构能够增大变量泵的最大排量，本公开负载敏感泵系统无需额外增加电气控制器或线束之类，通过自身液控油路，实现了功率随转速可变控制的效果，具有较高的可实施性。
附图说明
为了更清楚地说明本公开实施例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，下面描述中的附图仅仅是本公开中记载的一些实施例，对于本领域普通技术人员来讲，还可以根据这些附图获得其他的附图。
图1是本公开负载敏感泵系统的一些实施例的结构原理示意图。
附图标记说明：
1、变量泵；2、定量泵；3、取压阀；4、压力控制阀；5、流量控制阀；6、功率控制阀；7、变量缸；8、斜盘摆角反馈件；9、斜盘摆角反馈弹簧；31、阻尼；32、液控比例阀；P1、第一进油口；P2、第一出油口；P3、第二出油口；B1、变量工作油口；B2、定量工作油口；X、负载反馈口；Y、控制端口。
具体实施方式
现在将参照附图来详细描述本公开的各种示例性实施例。对示例性实施例的描述仅仅是说明性的，决不作为对本公开及其应用或使用的任何限制。本公开可以以许多不同的形式实现，不限于这里的实施例。提供这些实施例是为了使本公开透彻且完整，并且向本领域技术人员充分表达本公开的范围。应注意到：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、材料的组分、数字表达式和数值应被解释为仅仅是示例性的，而不是作为限制。
本公开中使用的“第一”、“第二”以及类似的词语并不表示任何顺序、数量或者重要性，而只是用来区分不同的部分。“包括”或者“包含”等类似的词语意指在该词前的要素涵盖在该词后列举的要素，并不排除也涵盖其他要素的可能。“上”、“下”、“左”、“右”等仅用于表示相对位置关系，当被描述对象的绝对位置改变后，则该相对位置关系也可能相应地改变。
在本公开中，当描述到特定器件位于第一器件和第二器件之间时，在该特定器件与第一器件或第二器件之间可以存在居间器件，也可以不存在居间器件。当描述到特定器件连接其它器件时，该特定器件可以与其它器件直接连接而不具有居间器件，也可以不与其它器件直接连接而具有居间器件。
本公开使用的所有术语与本公开所属领域的普通技术人员理解的含义相同，除非另外特别定义。还应当理解，在诸如通用字典中定义的术语应当被解释为具有与它们 在相关技术的上下文中的含义相一致的含义，而不应用理想化或极度形式化的意义来解释，除非这里明确地这样定义。
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，技术、方法和设备应当被视为说明书的一部分。
在负载敏感液压系统中，对变量泵的变量控制方式包括压力控制、流量控制和功率控制，其中压力控制是将变量泵出口的最大压力限制在变量泵的控制范围内，变量泵仅提供执行元件所需的液压油流量，如果工作压力超过压力阀处设置的压力设定值，则变量泵将调节至更小的排量以减少控制偏差；流量控制是通过使用可变节流孔(例如方向阀)来调节节流孔上游和下游压差，由这个压差来控制变量泵的流量，无论压力等级如何变化，变量泵的输出流量将等于执行机构实际所需的流量；功率控制是为了在工作压力不断变化的情况下保持恒定的传动扭矩，需要改变变量泵的斜盘角度(对应变量泵的排量)，在固定输入转速下，变量泵的输出流量和压力保持不变，从而达到恒功率控制的目的。
如图1所示，本公开的一些实施例提供了一种负载敏感泵系统，包括：变量泵1；定量泵2，与变量泵1由同一驱动机构驱动；变量控制机构，用于控制变量泵1；控制油路；以及取压阀3，被配置为通过控制油路将定量泵2的部分输出压力作用于变量控制机构的控制端，以在驱动机构的驱动转速升高时增大变量泵1的最大排量。
如图1所示，变量泵1与定量泵2均由同一驱动机构驱动，例如通过发动机驱动，变量泵1与定量泵2的转速变化相通，当定量泵2的转速升高时，变量泵1的转速也相应地升高，通过设置取压阀3，取压阀3将定量泵的部分压力变化信号引入变量控制机构的控制端，使得驱动机构的驱动转速升高时变量控制机构能够增大变量泵1的最大排量，实现不同输入转速下，变量泵的功率可变控制，使得液压泵的功率利用率提高，从而可以有效降低驱动机构的最大工作转速，实现液压系统的节能效果。本公开负载敏感泵系统无需额外增加电气控制器或线束之类，通过自身液控油路，实现了功率随转速可变控制的效果，具有较高的可实施性。
在一些实施例中，取压阀3为定比例取压阀，作用于变量控制机构的控制端的部分输出压力被配置为随着定量泵2的工作油压的增大而增大，从而能够准确获得驱动机构的转速变化信号，有效提升控制准确性。
对于取压阀的结构，在一些实施例中，如图1所示，取压阀3具有第一进油口P1，第一出油口P2和第二出油口P3，取压阀3包括阻尼31和液控比例阀32，定量泵2的定量工作油口B2与第一进油口P1相通，阻尼31设置在第一进油口P1和第一出油 口P2的通路上，液控比例阀32设置在第一进油口P1和第二出油口P3的通路上，液控比例阀32的第一控制端与第一进油口P1相通，液控比例阀32的第二控制端与第一出油口P2和第二出油口P3均相通，第二出油口P3与变量控制机构的控制端相通。
阻尼31起到减压的作用，通过设置液控比例阀32，第一进油口P1的油压作用在液控比例阀32的第一控制端，第一出油口P2和第二出油口P3的油压作用在液控比例阀32的第二控制端，由于阀芯的第一控制端和第二控制端的面积相等，当液控比例阀32平衡时，第一进油口P1的油压等于第一出油口P2和第二出油口P3的油压之和，亦即第二出油口P3的油压等于第一进油口P1的油压减去第一出油口P2的油压，第二出油口P3的油压为阻尼31所产生的压降，由于阻尼31成比例地减压，因此当第一进油口P1的油压增大时，第一出油口P2的油压和第二出油口P3的油压均增大，将第二出油口P3的油压作用到变量控制机构的控制端，使得驱动机构的驱动转速升高时变量控制机构能够增大变量泵1的最大排量。
需要说明的是，第二出油口P3的油压仅仅是第一出油口P2的油压的一小部分，第一出油口P2的油压占大部分，因此取压阀3的设置并不会影响第一出油口P2为工作动力输出油口的动力输出。
对于变量控制机构的结构，在一些实施例中，如图1所示，变量控制机构包括功率控制阀6和用于控制变量泵1的斜盘摆角的变量缸7，功率控制阀6能够改变控制油路对变量缸7的供油量来实现变量泵1的排量可调，变量泵1的变量工作油口B1通过控制油路与功率控制阀6的第一控制端(图1中左控制端)相通，取压阀3通过控制油路连通控制端口Y将第二出油口P3的油压作用于功率控制阀6的第二控制端(图1中右控制端)，有利于改变功率控制阀6的阀芯位置，继而改变控制油路对变量缸7的供油量，从而实现变量泵1的排量可调，具有较高的可实施性。
如图1所示，在一些实施例中，控制油路向变量缸7的无杆腔供油，变量缸7的活塞杆用于控制变量泵1的斜盘摆角，功率控制阀6为液控比例阀，在功率控制阀6的阀芯处于第一控制位(图1所示的左位)状态下，变量泵1通过功率控制阀6向变量缸7的无杆腔供油，在功率控制阀6的阀芯处于第二控制位(图1所示的右位)状态下，变量缸7的无杆腔通过功率控制阀6泄油。通过这样的配置方式，在第二出油口P3的油压作用于功率控制阀6的第二控制端下，有利于功率控制阀6维持在第二控制位(图1所示的右位)，相较于没有第二出油口P3的油压作用来说，控制变量泵1的斜盘摆角增大，从而提高了变量泵1的排量。
在一些实施例中，如图1所示，活塞杆设有斜盘摆角反馈件8，斜盘摆角反馈件 8和功率控制阀6的第二控制端之间设有处于预压紧状态的斜盘摆角反馈弹簧9。通过设置处于预压紧状态的斜盘摆角反馈弹簧9，第二出油口P3的油压和斜盘摆角反馈弹簧9共同作用于功率控制阀6的第二控制端，与作用于功率控制阀6的第一控制端的变量泵1的变量工作油口B1的油压达到平衡。
对于如何实现负载敏感压差控制，在一些实施例中，如图1所示，变量控制机构还包括设置在控制油路上的流量控制阀5和压力控制阀4，流量控制阀5的负载反馈端与负载反馈口X相通，控制油路的控制油液由变量泵1的工作油路提供，流量控制阀5和压力控制阀4是本领域所知晓的技术手段，在此不再赘述。
下面以图1所示的实施例为例应用于起重机，驱动机构为发动机为例，来说明本公开负载敏感泵系统的控制原理如下：
起重机在上车作业时，发动机转速通常工作在低转速状态，发动机最大输出扭矩值较低，为防止负载过大将发动机鳖熄火，变量泵1需要限制其最大排量输出。
当负载敏感泵系统正常工作时，其流量控制阀5起作用，变量泵1提供系统需要的流量，当转速升高，泵排量逐渐增加。
若没有设置取压阀3来进行压力引入，功率控制阀6在变量泵1的变量工作油口B1的油压的作用下使得阀芯向右移动工作至左位，继而带动斜盘摆角反馈件8和活塞杆向右移动，而变量泵1通过功率控制阀6向变量缸7的无杆腔供油，使得活塞杆向左移动，最终达到平衡使得泵排量稳定在Vmax1不变；
而在设置取压阀3来进行压力引入后，取压阀3输出的第二出油口P3的油压随着转速也相应升高，输出给变量泵1的控制端口Y压力也增大，这样功率控制阀6能够向左移动工作至右位，变量缸7的无杆腔通过功率控制阀6泄油，使得活塞杆向左移动，当达到新的平衡时，泵排量稳定在Vmax2，相比同转速下变量泵的最大排量Vmax1，其排量是增大的，系统输出扭矩也是相应升高的，这样在同样的大转速下，变量泵1的排量增大，液压系统的功率利用率更高；
压力控制阀4用于变量泵1的最大压力限制，当变量泵1的出口压力超过该值时，变量泵1的出口压力直接作用于变量缸7的无杆腔，使得变量泵1的排量降低。
本公开的一些实施例提供了一种液压控制系统，包括前述负载敏感泵系统。
本公开的一些实施例提供了一种工程机械，包括前述负载敏感泵系统。本公开负载敏感泵系统尤其适用于起重机，因此，在一些实施例中，工程机械为起重机。
至此，已经详细描述了本公开的各实施例。为了避免遮蔽本公开的构思，没有描述本领域所公知的一些细节。本领域技术人员根据上面的描述，完全可以明白如何实 施这里公开的技术方案。
虽然已经通过示例对本公开的一些特定实施例进行了详细说明，但是本领域的技术人员应该理解，以上示例仅是为了进行说明，而不是为了限制本公开的范围。本领域的技术人员应该理解，可在不脱离本公开的范围和精神的情况下，对以上实施例进行修改或者对部分技术特征进行等同替换。本公开的范围由所附权利要求来限定。

Claims (10)

  1. 一种负载敏感泵系统，包括：
    变量泵(1)；
    定量泵(2)，与所述变量泵(1)由同一驱动机构驱动；
    变量控制机构，用于控制所述变量泵(1)；
    控制油路；以及
    取压阀(3)，被配置为通过所述控制油路将所述定量泵(2)的部分输出压力作用于所述变量控制机构的控制端，以在所述驱动机构的驱动转速升高时增大所述变量泵(1)的最大排量。
  2. 根据权利要求1所述的负载敏感泵系统，其中，所述取压阀(3)为定比例取压阀，作用于所述变量控制机构的控制端的所述部分输出压力被配置为随着所述定量泵(2)的工作油压的增大而增大。
  3. 根据权利要求1所述的负载敏感泵系统，其中，所述取压阀(3)具有第一进油口(P1)，第一出油口(P2)和第二出油口(P3)，所述取压阀(3)包括阻尼(31)和液控比例阀(32)，所述定量泵(2)的定量工作油口(B2)与所述第一进油口(P1)相通，所述阻尼(31)设置在所述第一进油口(P1)和所述第一出油口(P2)的通路上，所述液控比例阀(32)设置在所述第一进油口(P1)和所述第二出油口(P3)的通路上，所述液控比例阀(32)的第一控制端与所述第一进油口(P1)相通，所述液控比例阀(32)的第二控制端与所述第一出油口(P2)和所述第二出油口(P3)均相通，所述第二出油口(P3)与所述变量控制机构的控制端相通。
  4. 根据权利要求1所述的负载敏感泵系统，其中，所述变量控制机构包括功率控制阀(6)和用于控制所述变量泵(1)的斜盘摆角的变量缸(7)，所述功率控制阀(6)能够改变所述控制油路对所述变量缸(7)的供油量来实现所述变量泵(1)的排量可调，所述变量泵(1)的变量工作油口(B1)通过所述控制油路与所述功率控制阀(6)的第一控制端相通，所述取压阀(3)通过所述控制油路将所述定量泵(2)的部分输出压力作用于所述功率控制阀(6)的第二控制端。
  5. 根据权利要求4所述的负载敏感泵系统，其中，所述控制油路向所述变量缸(7)的无杆腔供油，所述变量缸(7)的活塞杆用于控制所述变量泵(1)的斜盘摆角，所述功率控制阀(6)为液控比例阀，在所述功率控制阀(6)的阀芯处于第一控制位状态下，所述变量泵(1)通过所述功率控制阀(6)向所述变量缸(7)的无杆腔供油，在所述功率控制阀(6)的阀芯处于第二控制位状态下，所述变量缸(7)的无杆腔通过所述功率控制阀(6)泄油。
  6. 根据权利要求5所述的负载敏感泵系统，其中，所述活塞杆设有斜盘摆角反馈件(8)，所述斜盘摆角反馈件(8)和所述功率控制阀(6)的第二控制端之间设有处于预压紧状态的斜盘摆角反馈弹簧(9)。
  7. 根据权利要求4所述的负载敏感泵系统，其中，所述变量控制机构还包括设置在所述控制油路上的流量控制阀(5)和压力控制阀(4)，所述流量控制阀(5)的负载反馈端与负载反馈口(X)相通，所述控制油路的控制油液由所述变量泵(1)的工作油路提供。
  8. 一种液压控制系统，包括权利要求1所述的负载敏感泵系统。
  9. 一种工程机械，包括权利要求1所述的负载敏感泵系统。
  10. 根据权利要求9所述的工程机械，其中，所述工程机械为起重机。
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CN115110596A (zh) * 2022-07-26 2022-09-27 山河智能装备股份有限公司 一种液压控制系统
CN116044732A (zh) * 2022-12-26 2023-05-02 厦门大学 一种三级压力控制系统及方法

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CN115110596A (zh) * 2022-07-26 2022-09-27 山河智能装备股份有限公司 一种液压控制系统
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