【正文】 流量時(shí)間圖 根據(jù)流量時(shí)間圖求得平均流量為 根據(jù)教材《液壓傳動(dòng)系統(tǒng)》第三版第五章“蓄能器回路分析”提到‘經(jīng)上輥快開缸 Φ 300/180X20 3 127 上輥 平衡 缸 Φ 65/36X150 6 2 15 下輥 鎖緊 缸 Φ 65/36X60 6 2 6 下中輥快開缸 Φ 250/180X20 1 .入，出輥道升降液壓 缸 CD250A80/56150A10/02CGDMA 各 4 夾送輥擺動(dòng)液壓缸 CD250B40/2850A10/02CGDMA 2 10 大量的例證可以得出，蓄能器的工作容積應(yīng) 該等于負(fù)的 △ Vi 中絕對值最大的與正的△ Vi 中絕對值最大的二者之和，表現(xiàn)為 Vw=∣ △ Vi∣ max+∣ +△ Vi∣ max 式中 Vw— 蓄能器工作容積； ∣ △ Vi∣ max— 負(fù)的 △ Vi中絕對值最大值； ∣ +△ Vi∣ max— 正的△ Vi中絕對值最大值； 由流量時(shí)間圖可以求出△ Vi1=()x6= △ Vi2=() x9+△ Vi1= =327 △ Vi3=() +△ Vi2= =338 △ Vi4=()+△ Vi3== △ Vi5=() +△ Vi4== △ Vi6=() +△ Vi5== △ Vi7=() +△ Vi6== △ Vi8=() +△ Vi7== △ Vi9=()+Vi8== 由上式可以看出 ∣ △ Vi∣ max=338；∣ +△ Vi∣ max= 則 Vw=∣ △ Vi∣ max+∣ +△ Vi∣ max=338+93=431L 因?yàn)橐陨蟿?dòng)作順序可能不完全對，導(dǎo)致計(jì)算數(shù)據(jù)偏大，現(xiàn)在假設(shè)全部靠蓄能器來保壓， Σ △ VK=(+++++)= 11 計(jì)算方法二： △ V=Σ △ VK1Σ qmt 式中 △ V有效排油量（ L） Σ △ V系統(tǒng)中各個(gè)工作點(diǎn)耗 油量總和（ L） K系統(tǒng)泄漏系數(shù)，一般可以選 K1= Σ qmt泵總供油量（一個(gè)工作 循環(huán)內(nèi)系統(tǒng)所需的平均流量 ） ，可按下式計(jì)算： Σ qm=K2Σ Vi/T 或 Σ qm=K2(QmaxQmin)/2 式中Ｋ２－－－系統(tǒng)泄漏系數(shù)，Ｋ＝１ .３－１ .１ Σ Vi系統(tǒng) 中一個(gè)工作 循環(huán)內(nèi)各個(gè)執(zhí)行機(jī)構(gòu) 耗油量總和（ L） Qmax系統(tǒng)中最大流量 Qmin系統(tǒng)中最小流量 T機(jī)組工作周期時(shí)間 (s) t最大耗油量時(shí)泵的工作時(shí)間 (s) T=21,t=。==63mm 液壓系統(tǒng)壓油管道推薦流速 36，壓力高，管道短，粘度小取大值； 液壓系統(tǒng)回油管道推薦流速 ； ② 給 快 開 缸 供 油 的 管 子 ， 取 速 度 值 為 ，則d2=(4x127/1000/60/)189。==7mm ⑥ 給下中輥高度調(diào)整液壓馬達(dá)供油的管子，取速度值為 3，因?yàn)轳R達(dá)轉(zhuǎn)速不同，所需流量不同，經(jīng)過計(jì)算它的流量范圍是,則 d6=()189。 本液壓機(jī)執(zhí)行部件的最大工作壓力 P1=14MPA，進(jìn)油路中的壓力損失，取 P?? =。 此外，為了延長設(shè)備的使用壽命，設(shè)備在設(shè)計(jì)時(shí)必須有一定的壓力儲備量，并確保泵的壽命，因此在選取泵的額定工作壓力 Pn 時(shí)，應(yīng)滿足pPPn )~(? ，取 Pp=。 將參數(shù)代入公式中，即： m in/1 4 01 2 Lq P ??? 但是有蓄能器補(bǔ)油，可以選擇 A10VS0100DR 1500r/min 時(shí)，流量 150L/min,功率 62 千瓦，尺寸 206X電動(dòng)機(jī)額定功率的確定必須根據(jù)消耗功率最大的工況來確定，因此要分別計(jì)算主缸、頂出缸各工況消耗的功率。 式中 l管道的長度（ m） d管道的內(nèi)徑（ m） v 液流平均速度 (m/s) ρ 液壓油密度 (kg/m3) λ 沿程阻力系數(shù) ξ 局部阻力系數(shù) △ p3=△ pn(Q/Qn)^2 式中 Qn閥的額定流量 (m3/s) Q通過閥的實(shí)際流量 (m3/s) △ pn閥的額定壓力損失 (Pa), 矯直 機(jī)執(zhí)行部件有主缸和 平衡缸，夾送輥擺動(dòng)缸，輥道升降缸，換輥馬達(dá)，下中輥高度調(diào)整液壓馬達(dá) ，供油管子管徑如下 名稱 D1 D2 D3 D4 D5 D6 D7 內(nèi)徑 60.3 25.4 15.9 8 19 28.6 19 最后根據(jù)標(biāo)準(zhǔn) 軟管 取值如下 液壓油選用 LHL32 液 壓 油 ， 15 ℃時(shí)該油液的運(yùn)動(dòng)粘度scmcst / 2??? ,油液密度 3/920 mkg?? 。進(jìn)油管長度為 10m，沿程 壓力損失 1P? 為： PaPavdlP 6222111 ?????????? ??? 閥的壓力損失 PaP ??? 閥 ；那么進(jìn)油路總的壓力損失 進(jìn)P?為： 進(jìn)P? = 1P? + 閥P? = PaPa 666 )( ????? 由于進(jìn)出口管徑相同，要求工作速度相同，所以估算壓力損失也相同，那么回油壓力損失 也為 兆帕； △ p=+= 要求工作壓力 14 兆帕，而設(shè)計(jì)的是 18 兆帕，所以這點(diǎn)壓力損失對系統(tǒng)的工作幾乎沒有影響！ 通過對主缸、 入出口輥道升降 缸各工況的壓力損失驗(yàn)算可知，液壓系統(tǒng)的油路構(gòu)及元件參數(shù)選擇滿足要求 。后來問老師才知道不要求做三維制圖，也不用管缸，馬達(dá)等實(shí)體如何空間布置，只做系統(tǒng)圖和泵站圖，這才明白，所想與所要求的背道而馳。第二次選擇，全部選擇力氏樂的電磁換向閥，液控單向閥，單向節(jié)流閥，可是，還是組合不到一起來，除非管式連接，可 是老師要求的是疊加閥，怎么就疊不起來呢？問同學(xué)，又問老師，還是不明白，明明他們都可以疊加起來，為什么我的就不行？思來想去，突然大笑，原來我是一個(gè)很爛的月老，非要把普通閥當(dāng)作疊加閥用，能疊起來嗎？第三次，經(jīng)歷元件選型就比較順利。在老師的指導(dǎo)下，我順利的完成了畢業(yè)設(shè)計(jì)。 operating machinery engineering machinery, construction machinery, agricultural machinery, automobiles, etc.。 ship from the deck heavy machinery (winch), the bow doors, bulkhead valve, stern thruster, etc.。 directional control valve includes a oneway valve , oneway fluid control valve, shuttle valve, valve and so on. Under the control of different ways, can be divided into the hydraulic valve control switch valve, control valve and set the value of the ratio control valve. Auxiliary ponents, including fuel tanks, oil filters, tubing and pipe joints, seals, pressure gauge, oil level, such as oil dollars. Hydraulic oil in the hydraulic system is the work of the energy transfer medium, there are a variety of mineral oil, emulsion oil hydraulic molding Hop categories. The role of the hydraulic system is to help humanity work. Mainly by the implementation of ponents to rotate or pressure into a reciprocating motion. Hydraulic system and hydraulic power control signal is posed of two parts, the signal control of some parts of the hydraulic power used to drive the control valve movement. Part of the hydraulic power means that the circuit diagram used to show the different functions of the interrelationship between ponents. Containing the source of hydraulic pump, hydraulic motor and auxiliary ponents。 the use and maintenance requirements for a higher level of technology. In the hydraulic system and its system, the sealing device to prevent leakage of the work of media within and outside the dust and the intrusion of foreign bodies. Seals played the role of ponents, namely seals. Medium will result in leakage of waste, pollution and environmental machinery and even give rise to malfunctioning machinery and equipment for personal accident. Leakage within the hydraulic system will cause a sharp drop in volumetric efficiency, amounting to less than the required pressure, can not even work. Microinvasive system of dust particles, can cause or exacerbate friction hydraulic ponent wear, and further lead to leakage. Therefore, seals and sealing device is an important hydraulic equipment ponents. The reliability of its work and life, is a measure of the hydraulic system an important indicator of good or bad. In addition to the closed space, are the use of seals, so that two adjacent coupling surface of the gap between the need to control the liquid can be sealed following the smallest gap. In the contact seal, pressed into selfsealstyle and selfstyled selftight seal (ie, sealed lips) two. The three hydraulic system diseases 1, as a result of heat transmission medium (hydraulic oil) in the flow velocity in various parts of the existence of different, resulting in the existence of a liquid within the internal friction of liquids and pipelines at the sam e time there is friction 29 between the inner wall, which are a result of hydraulic the reasons for the oil tempera ture. Temperature will lead to i