CAJ | 학술논문

为了解定量泵液压传动系统的特点，该文针对负载敏感定量泵液压回路中的负载压力变化和主控多路阀阀芯移动，深入研究了定量泵出口压力、负载压力和补偿阀口开度、主控阀芯位移之间的数学关联性，得出了补偿阀口开度变化量与主控阀芯阀口开度变化量之间的解析关系式。研究表明，随着定量泵出口压力增加，出现负载压力波动时补偿阀芯的运动幅度会变小，泵输出压力为6、9和12 MPa时，位移变化率分别为0.081、0.142和0.183（输出压力6 MPa）；0.058、0.110和0.139(输出压力9MPa)；0.042、0.079和0.112（输出压力12 MPa）；而对同一输出压力，随着负载压力变化增加，补偿阀芯位移变化率的变化减小，负载压力变化1、2和3 MPa时，补偿阀芯位移变化率依次减小为0.081、0.072和0.064（输出压力6 MPa）；0.057、0.051和0.046（输出压力9MPa）；0.043、0.038和0.034（输出压力12 MPa），与试验结果吻合。主控阀芯移动时补偿阀芯的运动分析表明，在定量泵出口压力不变时，补偿阀口开度变化和主控阀等效节流面积改变成正比。研究结果对于机械负载敏感定量泵系统的设计具有一定的借鉴意义。
위료해정량빙액압전동계통적특점，해문침대부재민감정량빙액압회로중적부재압력변화화주공다로벌벌심이동，심입연구료정량빙출구압력、부재압력화보상벌구개도、주공벌심위이지간적수학관련성，득출료보상벌구개도변화량여주공벌심벌구개도변화량지간적해석관계식。연구표명，수착정량빙출구압력증가，출현부재압력파동시보상벌심적운동폭도회변소，빙수출압력위6、9화12 MPa시，위이변화솔분별위0.081、0.142화0.183（수출압력6 MPa）；0.058、0.110화0.139(수출압력9MPa)；0.042、0.079화0.112（수출압력12 MPa）；이대동일수출압력，수착부재압력변화증가，보상벌심위이변화솔적변화감소，부재압력변화1、2화3 MPa시，보상벌심위이변화솔의차감소위0.081、0.072화0.064（수출압력6 MPa）；0.057、0.051화0.046（수출압력9MPa）；0.043、0.038화0.034（수출압력12 MPa），여시험결과문합。주공벌심이동시보상벌심적운동분석표명，재정량빙출구압력불변시，보상벌구개도변화화주공벌등효절류면적개변성정비。연구결과대우궤계부재민감정량빙계통적설계구유일정적차감의의。
A type of load pressure sensitive quantitative pump hydraulic circuit was studied, and its working principle was explained. Under the conditions, the research included two situations, which are load pressure change and main control multi-way valve spool movement. By the basic physical equations of the hydraulic units, the mathematical relationship between system outlet pressure p1, load pressure p2, fixed differential relief valve compensation spool opening xc and main control spool displacement xe was obtained;and by the analysis of above mathematical relationship, it was observed that under the situation which main control spool equivalent throttling area Ae keeps still and load pressure p2 changes, fixed differential relief valve compensation spool displacement rate Δxc/xc is inversely proportional to a pump’s system outlet pressure p1, however, it is proportional to load pressure change Δp2; and as the pump outlet pressure p1 increases, the fixed differential relief valve compensation spool displacement rateΔxc/xc becomes smaller. The experimental results showed that displacement rate Δxc/xc are 0.081, 0.142 and 0.183(output pressure is 6 MPa);0.058, 0.110 and 0.139(output pressure is 9 MPa);0.042, 0.079 and 0.112(output pressure is 12 MPa) respectively. For constant pump outlet pressure p1, the movement range of the fixed differential relief valve compensation spool becomes larger, and that the fixed differential relief valve compensation spool displacement rate slopeΔxc/xc/Δp2 has the trend to become smaller as load pressure changeΔp2 increases. The theoretical analysis and experimental results (whenΔp2 are 1, 2, 3 MPa,Δxc/xc/Δp2 are 0.081, 0.072 and 0.064(output pressure is 6 MPa);0.057, 0.051 and 0.046(output pressure is 9 MPa); 0.043, 0.038 and 0.034(output pressure is 12 MPa) respectively under p1 equals 6, 9, 12 MPa) are consistent. Others, as the fixed differential relief valve compensation spool throttling ports generally is designed as U or V partial throttling groove, thus when the main control spool moves, its moving characteristics analysis is established based on U throttling groove. By its throttling structural feature, a geometric simplified throttling area calculation mathematical expression of U throttling groove was deduced, and then based on the U throttling area calculation formula, the fixed differential relief valve compensation spool characteristic movement when main control spool moves was analyzed. Then the mathematical expression between the change of the fixed differential relief valve compensation spool throttling port opening Δxc and the throttling area change ΔAe of main control valve spool was obtained. It was then observed that the fixed differential relief valve compensation spool opening changeΔxc is proportional to the main control valve spool equivalent throttling area changeΔAe;and it was also found that the value of the ratio between the fixed differential relief valve compensation spool throttling port opening changeΔxc and the main control valve spool equivalent throttling area changeΔAe is closely relevant to the pump system outlet pressure p1 and load pressure p2; besides p1 and p2, the ratio between the fixed differential relief valve compensation spool throttling port opening change Δxc and main control valve spool equivalent throttling area change ΔAe is relevant to the ratio between main control valve spool throttling port’s flow coefficient Cqe and overflow throttling port’s flow coefficient Cqc of the fixed differential relief valve chamber, and also is relevant to the throttling area gradient wc of the fixed differential relief valve throttling port. As the fixed differential relief valve compensation throttling area gradient wc becomes larger, the compensation spool opening change Δxc largely approximates to the main control valve spool U throttling groove equivalent throttling area change ΔAe. By the simplified throttling area calculation formula of U throttling groove, the mathematical relationship between the fixed differential relief valve compensation spool opening changeΔxc and the main control valve spool openingΔxe is obtained, and it is helpful to the design of a machinery load sensitive quantitative pump system.