CN109441905B - 一种变压差负载敏感多路阀 - Google Patents

一种变压差负载敏感多路阀 Download PDF

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CN109441905B
CN109441905B CN201811601431.8A CN201811601431A CN109441905B CN 109441905 B CN109441905 B CN 109441905B CN 201811601431 A CN201811601431 A CN 201811601431A CN 109441905 B CN109441905 B CN 109441905B
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oil
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权龙�
王波
郝云晓
王鹤
李泽鹏
夏连鹏
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Taiyuan University of Technology
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Abstract

本发明公开了一种变压差负载敏感多路阀，各联阀组采用新型元件电液压力补偿阀，实现了补偿压差实时连续调控和补偿阀芯实时位置反馈监测，克服了流量饱和工况下传统LS***流量失配和LUDV***分流比例固定、执行器运动协调性差的问题。本发明公开的一种变压差负载敏感多路阀具有工况适用性强、流量分配精度高、技术性强等优点。

Description

一种变压差负载敏感多路阀
技术领域
本发明属于液压技术领域，涉及一种负载敏感多路阀，具体涉及一种补偿压差可变的负载敏感多路阀。
背景技术
多路换向阀作为工程机械的核心元件，应用于工程机械目前主要有正流量、负流量和负载敏感三种控制方式。正、负流量控制技术是目前国内挖掘机采用的主流技术，采用开中心多路阀，存在较大的中位和旁路节流损失，且未采用压差补偿技术，受负载压力和油源压力变化影响，多个执行器复合动作时，存在操控性差的问题。而负载敏感技术在每一联执行器的换向阀前增设了压力补偿阀，保持控制阀口前后压差Δp恒定，由公式
Figure GDA0002259376380000011
看出，流向执行器流量Q只与换向阀开口大小A有关，不受负载压力变化影响，改善了多个执行器复合动作时***的操控性。
但现有负载敏感技术压力补偿阀依靠负载压力和油源压力控制，工作过程中补偿阀芯不可控、不可测，不利于负载敏感多路阀智能化发展。而且，如图1所示，传统补偿阀补偿压差Δp恒定不变，不能实时匹配***工况，对于精确定位和微动操作工况，过大的补偿压差Δp将造成大的阀口流量增益和节流损失，增加了***操控难度；对于大载荷快速变化工况，过小的补偿压差Δp将造成执行器响应过慢，降低***工作效率。进一步，在流量饱和工况下，传统负载敏感(LS)技术存在压力补偿阀失效造成的***流量失配问题；负载独立分配(LUDV)技术各执行器运行速度将按相同比例减小，分流比例固定、分流精度低，各执行器运行协调性差。
发明内容
为了解决上述问题，本发明旨在提供一种补偿压差可控的智能化负载敏感多路阀，实时连续调控补偿压差匹配不同工况，解决传统负载敏感技术流量饱和工况下的流量失配难题，提高负载敏感***的流量分配精度。
为实现上述目的，本发明采用以下技术方案：一种变压差负载敏感多路阀，包括至少一联阀组，其中每联阀组包括进油路1，先导控制进油路2，先导控制回油路3，负载敏感油路4，回油路5，换向阀6，单向阀7，梭阀8，第Ⅰ单向溢流阀9，第Ⅱ单向溢流阀10，其特征在于，还包括电液压力补偿阀11和第Ⅰ先导减压阀12；
所述的电液压力补偿阀包括位移传感器13、补偿阀体14、补偿阀芯15、弹簧16、进油口A、出油口B、第Ⅰ控制腔PF、第Ⅱ控制腔PE和第Ⅲ控制腔PG；补偿阀芯布置在补偿阀体之中，且包括第Ⅰ台肩17、第Ⅱ台肩18和第Ⅲ台肩19三个台肩，弹簧一端作用在补偿阀芯左端面C上，另一端作用在补偿阀体上、并与补偿阀芯第Ⅰ台肩形成第Ⅰ控制腔PF，位移传感器通过补偿阀体安设在补偿阀芯上，直接检测阀芯的位置X和速度XV，补偿阀芯第Ⅱ台肩和第Ⅲ台肩则分别与补偿阀体形成第Ⅲ控制腔PG和第Ⅱ控制腔PE；
电液压力补偿阀与***采用两种连接方式：
连接方式1：电液压力补偿阀布置在换向阀之前，电液压力补偿阀的进油口A与进油路连通，电液压力补偿阀的出油口B与单向阀的进油口、电液压力补偿阀的第Ⅱ控制腔PE连通，电液压力补偿阀的第Ⅲ控制腔PG与第Ⅰ先导减压阀的工作油口连通，第Ⅰ先导减压阀的进出油口分别与先导控制进油路和先导控制回油路连通，负载敏感油路通过梭阀与换向阀的检测油口F、电液压力补偿阀的第Ⅰ控制腔PF连通；
连接方式2：电液压力补偿阀布置在换向阀之后，单向阀的出油口与电液压力补偿阀的进油口A、电液压力补偿阀的第Ⅱ控制腔PE连通，电液压力补偿阀的第Ⅰ控制腔PF与负载敏感油路连通，电液压力补偿阀的第Ⅲ控制腔PG与第Ⅰ先导减压阀的工作油口连通，第Ⅰ先导减压阀的进、出油口分别与先导控制进油路、先导控制回油路连通。
所述的电液压力补偿阀是常开式和常闭式中的一种。
所述的补偿阀芯第Ⅰ台肩外径d1与第Ⅲ台肩外径d3相等，且均小于第Ⅱ台肩外径d2。
所述的换向阀是电子比例换向阀、液压控制换向阀和电液比例换向阀中的一种。
当所述的换向阀是电液比例换向阀时，所述的一种变压差负载敏感多路阀还包括第Ⅱ先导减压阀20和第Ⅲ先导减压阀21；第Ⅱ先导减压阀和第Ⅲ先导减压阀的进、出油口分别与先导控制进油路、先导控制回油路连通，第Ⅱ先导减压阀和第Ⅲ先导减压阀的工作油口分别与换向阀的两端连通，并依据不同的控制信号输出不同的压力控制换向阀的方向和位移。
本发明的多路阀可以是单联阀，也可以是多联阀，当作为多联阀与多个执行器连通时，各连共用统一的进油路、先导控制进油路、先导控制回油路、负载敏感油路和回油路，且各联具有相同的元件和结构连接关系。
***变补偿压差工作原理及过程：
根据上述的补偿阀芯外径尺寸可得补偿阀芯的力平衡方程：
Figure GDA0002259376380000041
从上式可以看出，补偿阀芯受力主要包括弹簧力F弹、换向阀前压力p2、换向阀后压力p1和第Ⅰ先导减压阀输出压力p3四部分，其中换向阀前后压差即为补偿阀工作压差Δp，因此，可推出补偿阀补偿压差Δp为
Figure GDA0002259376380000042
假设弹簧力F弹不变，从上式可以看出，补偿阀补偿压差Δp与第Ⅰ先导减压阀输出压力p3有关，当第Ⅰ先导减压阀控制信号Isignal为零时，第Ⅰ先导减压阀输出压力p3为零，补偿阀补偿压差最大，其工作方式与传统压力补偿阀相同；当第Ⅰ先导减压阀输出压力p3时，补偿阀补偿压差开始减小，并与减压阀控制信号Isignal呈线性关系，从而实现补偿阀补偿压差的连续变化可控。
与现有技术相比，本发明具有以下有益效果：
本发明设计了新型电液压力补偿阀，实现了补偿阀补偿压差实时连续调控和补偿阀芯实时位置反馈监测，促进了负载敏感多路阀的智能化发展，为进一步实施先进控制技术打下基础。
本发明设计了新型电液压力补偿阀，增大了补偿压差调控范围，可实现***任意比例分流和抗流量饱和控制，克服了流量饱和工况下传统LS***流量失配和LUDV***分流比例固定、执行器运动协调性差的问题。
本发明应用范围广，可适用不同机型和工况，基于工况需求匹配补偿压差，精细操作时，减小补偿压差，降低阀口流量增益，提高操控稳定性；快速动作时，提高补偿阀补偿压差，增大阀口流量增益，实现执行器快速响应和高效工作。
附图说明
图1为传统压力补偿阀补偿压差控制曲线；
图2为本发明实施例1的***原理图；
图3为本发明电液压力补偿阀的结构原理图；
图4为本发明电液压力补偿阀的阀芯结构图；
图5为本发明电液压力补偿阀的补偿压差控制曲线；
图6为本发明实施例2的***原理图。
图中：1-进油路，2-先导控制进油路，3-先导控制回油路，4-负载敏感油路，5-回油路，6-换向阀，7-单向阀，8-梭阀，9-第Ⅰ单向溢流阀，10-第Ⅱ单向溢流阀，11-电液压力补偿阀，12-第Ⅰ先导减压阀，13-位移传感器，14-补偿阀体，15-补偿阀芯，16-弹簧，17-第Ⅰ台肩，18-第Ⅱ台肩，19-第Ⅲ台肩，20-第Ⅱ先导减压阀，21-第Ⅲ先导减压阀。
具体实施方式
下面结合附图1～6对本发明做进一步详细说明。
实施例1
一种变压差负载敏感多路阀，包括至少一联阀组，其中每联阀组包括进油路1，先导控制进油路2，先导控制回油路3，负载敏感油路4，回油路5，换向阀6，单向阀7，梭阀8，第Ⅰ单向溢流阀9，第Ⅱ单向溢流阀10，其特征在于，还包括电液压力补偿阀11和第Ⅰ先导减压阀12；
如图2所示，电液压力补偿阀11布置在换向阀6之前，电液压力补偿阀11的进油口A与进油路1连通，电液压力补偿阀11的出油口B与单向阀7的进油口、电液压力补偿阀11的第Ⅱ控制腔PE连通，电液压力补偿阀11的第Ⅲ控制腔PG与第Ⅰ先导减压阀12的工作油口连通，第Ⅰ先导减压阀12的进出油口分别与先导控制进油路2和先导控制回油路3连通，负载敏感油路4通过梭阀8与换向阀6的检测油口F、电液压力补偿阀的第Ⅰ控制腔PF连通；
如图3和图4所示，所述的电液压力补偿阀11包括位移传感器13、补偿阀体14、补偿阀芯15、弹簧16、进油口A、出油口B、第Ⅰ控制腔PF、第Ⅱ控制腔PE和第Ⅲ控制腔PG；补偿阀芯15布置在补偿阀体14之中，且包括第Ⅰ台肩17、第Ⅱ台肩18和第Ⅲ台肩19，弹簧16一端作用在补偿阀芯15左端面C上，另一端作用在补偿阀体14上、并与补偿阀芯15第Ⅰ台肩17形成第Ⅰ控制腔PF，位移传感器13通过补偿阀体14安设在补偿阀芯15上，直接检测阀芯的位置X和速度XV，补偿阀芯15第Ⅱ台肩18和第Ⅲ台肩19则分别与补偿阀体14形成第Ⅲ控制腔PG和第Ⅱ控制腔PE；
所述的电液压力补偿阀11是常开式和常闭式中的一种。
所述的补偿阀芯15第Ⅰ台肩17外径d1与第Ⅲ台肩19外径d3相等，且均小于第Ⅱ台肩18外径d2。
所述的换向阀6是电子比例换向阀、液压控制换向阀和电液比例换向阀中的一种。
本发明的多路阀可以是单联阀，也可以是多联阀，当作为多联阀与多个执行器连通时，各连共用统一的进油路1、先导控制进油路2、先导控制回油路3、负载敏感油路4和回油路5，且各联具有相同的元件和结构连接关系。
***变补偿压差工作原理及过程：
根据上述的补偿阀芯15外径尺寸可得补偿阀芯15的力平衡方程：
Figure GDA0002259376380000071
从上式可以看出，补偿阀芯15受力主要包括弹簧力F弹、换向阀前压力p2、换向阀后压力p1和第Ⅰ先导减压阀输出压力p3四部分，其中换向阀前后压差即为补偿阀工作压差Δp，因此，可推出补偿阀补偿压差Δp为
Figure GDA0002259376380000072
假设弹簧力F弹不变，从上式可以看出，补偿阀补偿压差Δp与第Ⅰ先导减压阀输出压力p3有关，当第Ⅰ先导减压阀控制信号Isignal为零时，第Ⅰ先导减压阀输出压力p3为零，补偿阀补偿压差最大，其工作方式与传统压力补偿阀相同；当第Ⅰ先导减压阀输出压力p3时，补偿阀补偿压差开始减小，并与减压阀控制信号Isignal呈线性关系，从而实现补偿阀补偿压差的连续变化可控，其控制曲线如图5所示。
实施例2
如图6所示，本发明一种变压差负载敏感多路阀的第二种实施方式，在结构组成上与实施例1相同，区别是电液压力补偿阀11与***的连接方式有所改变，并且所述的换向阀6是电液比例换向阀。
电液压力补偿阀11布置在换向阀6之后，单向阀7的出油口与电液压力补偿阀11的进油口A、电液压力补偿阀11的第Ⅱ控制腔PE连通，电液压力补偿阀11的第Ⅰ控制腔PF与负载敏感油路4连通，电液压力补偿阀11的第Ⅲ控制腔PG与第Ⅰ先导减压阀12的工作油口连通，第Ⅰ先导减压阀12的进、出油口分别与先导控制进油路2、先导控制回油路3连通。
当所述的换向阀6是电液比例换向阀时，***还包括第Ⅱ先导减压阀20和第Ⅲ先导减压阀21；第Ⅱ先导减压阀20和第Ⅲ先导减压阀21的进、出油口分别与先导控制进油路2、先导控制回油路3连通，第Ⅱ先导减压阀20和第Ⅲ先导减压阀21的工作油口分别与换向阀6的两端连通，并依据不同的控制信号输出不同的压力控制换向阀6的方向和位移。

Claims (6)

1.一种变压差负载敏感多路阀，包括至少一联阀组，其中每联阀组包括进油路(1)，先导控制进油路(2)，先导控制回油路(3)，负载敏感油路(4)，回油路(5)，换向阀(6)，单向阀(7)，梭阀(8)，第Ⅰ单向溢流阀(9)，第Ⅱ单向溢流阀(10)，其特征在于增设有电液压力补偿阀(11)和第Ⅰ先导减压阀(12)；
所述的电液压力补偿阀包括位移传感器(13)、补偿阀体(14)、补偿阀芯(15)、弹簧(16)、进油口(A)、出油口(B)、第Ⅰ控制腔(PF)、第Ⅱ控制腔(PE)和第Ⅲ控制腔(PG)；补偿阀芯布置在补偿阀体之中，且包括第Ⅰ台肩(17)、第Ⅱ台肩(18)和第Ⅲ台肩(19)三个台肩，弹簧一端作用在补偿阀芯左端面(C)上，另一端作用在补偿阀体上、并与补偿阀芯第Ⅰ台肩形成第Ⅰ控制腔(PF)，位移传感器通过补偿阀体安设在补偿阀芯上，直接检测阀芯的位置(X)和速度(XV)，补偿阀芯第Ⅱ台肩和第Ⅲ台肩则分别与补偿阀体形成第Ⅲ控制腔(PG)和第Ⅱ控制腔(PE)；
电液压力补偿阀与***连接方式有以下两种：
连接方式1：电液压力补偿阀布置在换向阀之前，电液压力补偿阀的进油口(A)与进油路连通，电液压力补偿阀的出油口(B)与单向阀的进油口、电液压力补偿阀的第Ⅰ控制腔(PF)连通，电液压力补偿阀的第Ⅲ控制腔(PG)与第Ⅰ先导减压阀的工作油口连通，第Ⅰ先导减压阀的进出油口分别与先导控制进油路和先导控制回油路连通，负载敏感油路通过梭阀与换向阀的检测油口(F)、电液压力补偿阀的第Ⅱ控制腔(PE)连通；
连接方式2：电液压力补偿阀布置在换向阀之后，单向阀的出油口与电液压力补偿阀的进油口A、电液压力补偿阀的第Ⅰ控制腔(PF)连通，电液压力补偿阀的第Ⅱ控制腔(PE)与负载敏感油路连通，电液压力补偿阀的第Ⅲ控制腔(PG)与第Ⅰ先导减压阀的工作油口连通，第Ⅰ先导减压阀的进、出油口分别与先导控制进油路、先导控制回油路连通。
2.根据权利要求1所述的一种变压差负载敏感多路阀，其特征在于：所述的电液压力补偿阀是常开式和常闭式中的一种。
3.根据权利要求1所述的一种变压差负载敏感多路阀，其特征在于：所述的补偿阀芯第Ⅰ台肩外径d1与第Ⅲ台肩外径d3相等，且均小于第Ⅱ台肩外径d2。
4.根据权利要求1所述的一种变压差负载敏感多路阀，其特征在于：所述的换向阀是电子比例换向阀、液压控制换向阀和电液比例换向阀中的一种。
5.根据权利要求1所述的一种变压差负载敏感多路阀，其特征在于：当所述的换向阀是电液比例换向阀时，所述的一种变压差负载敏感多路阀还包括第Ⅱ先导减压阀(20)和第Ⅲ先导减压阀(21)；第Ⅱ先导减压阀和第Ⅲ先导减压阀的进、出油口分别与先导控制进油路、先导控制回油路连通，第Ⅱ先导减压阀和第Ⅲ先导减压阀的工作油口分别与换向阀的两端连通，并依据不同的控制信号输出不同的压力控制换向阀的方向和位移。
6.根据权利要求1所述的一种变压差负载敏感多路阀，其特征在于：本发明的多路阀可以是单联阀，也可以是多联阀，当作为多联阀与多个执行器连通时，各联共用统一的进油路、先导控制进油路、先导控制回油路、负载敏感油路和回油路，且各联具有相同的元件和结构连接关系。
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