?液壓泵的輸出功率 PP=pPqP=常數(shù) 液壓缸的輸出功率 P1=Fv=Fq1/A=p1q1 回路的功率損失 △p=pP-p1=pPqP-p1q1=pP（q1+△q）-(pP-△p)q1=pP△q+△pq1 △q=qP-q1 溢流損失 △pY=pP△q 節(jié)流損失 △pT=△pq1 回路的效率 η=p1/p,P=Fv/pPqP=p1q1/pPqP ∵存在兩部分功率損失 ∴這種調(diào)速回路效率較低 節(jié)流閥出口節(jié)流調(diào)速回路特征：將節(jié)流閥串聯(lián)在液壓缸的回油路上，即串聯(lián)在缸和油箱之間，調(diào)節(jié)AT，可調(diào)節(jié)q2以改變速度，仍應(yīng)和溢流閥聯(lián)合使用，pP=pS。
與進(jìn)口節(jié)流調(diào)速回路相同處 ∵v—F特性基本與進(jìn)口節(jié)流相似 ∴上述結(jié)論都適用于此? 不同于進(jìn)口節(jié)流調(diào)速回路 1）承受負(fù)值負(fù)載能力 2）實(shí)現(xiàn)壓力控制的方便性 3）最低穩(wěn)定速度? 承受負(fù)值負(fù)載能力 ∵回油路節(jié)流閥使缸有一定背壓 ∴能承受負(fù)值負(fù)載，并↑v穩(wěn)定性，而進(jìn)油路則需在回油路上增加背壓閥方可承受，△P↑。
實(shí)現(xiàn)壓力控制的方便性 ∵進(jìn)油路調(diào)速中工作臺(tái)碰到死擋鐵后，活塞停止，缸進(jìn)油腔油壓上升至pS? ∴便于實(shí)現(xiàn)壓力（升壓）控制而回油路調(diào)?速在上述工況時(shí)，進(jìn)油腔壓力變化很小，無法控壓，而回油腔p↓0，可降壓發(fā)訊，但電路復(fù)雜。
最低穩(wěn)定速度 ∴在缸徑、缸速相同情況下，進(jìn)油節(jié)流調(diào)速回路流量閥開?口較大，低速時(shí)不易堵塞 ∵若回路使用單桿缸，無桿腔進(jìn)油量大于有桿腔回油流量? 節(jié)流閥旁路節(jié)流調(diào)速回路特征：將節(jié)流閥裝在與執(zhí)行元件并聯(lián)的支路上，即與缸并聯(lián)，溢流閥做安全閥，pP取決于負(fù)載，pP=p1=△p=F/A 缸（q1） q< 節(jié)流閥→T 節(jié)流閥旁節(jié)流調(diào)速回路工作特點(diǎn)分析 （1）速度負(fù)載特性 （2）最大承載能力 （3）功率和效率 q1=qP-qT=(qtP-△qP)-qT φ =(qtP-kLpP)-CAT△p φ =qtp-kL(F/A)-CAT(F/A) 故液壓缸的工作速度為： φ v=q1/A=[qtp-kL(F?/A)-CAT(F/A)]/A 結(jié)論：①AT=C，F(xiàn)↑，v↓,F↓，v↑，即v—F特性更軟 ②F=C,↑AT，v↓;↓AT↑v，即速度隨AT而變化 節(jié)流閥旁路節(jié)流調(diào)速回路最大承載力 AT↑，阻力↓，F(xiàn)max↓，即低速承載能力小，AT至一定值時(shí)，即使F很小，qp→節(jié)→T,V=0，所以Fmax既與AT有關(guān)，又受安全閥調(diào)定壓力的限制。
節(jié)流閥旁路節(jié)流調(diào)速回路功率和效率? ∵pP隨F變化而變化，只有△P節(jié)，而無△P溢 ∴η高，發(fā)熱少 節(jié)流閥旁節(jié)流調(diào)速回路應(yīng)用 ∵v—F特性較軟，低速承載能力差 ∴一般用于高速、重載、對(duì)速度平?穩(wěn)性要求很低的較大功率場合，如：牛頭刨床主運(yùn)動(dòng)系統(tǒng)、輸送機(jī)械液壓系統(tǒng)、大型拉床液壓系統(tǒng)、龍門刨床液壓系統(tǒng)等。
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