##封閉行星齒輪傳動系統(tǒng)的功率流分析及效率計算(可參考建立功率分流方程)

1、第31巻第5期封閉行星齒輪傳動不統(tǒng)的功率流分析及效率計算#© 1994-2010 China Academic Journal Electronic Publishing House. All rights resened. 第31巻第5期封閉行星齒輪傳動不統(tǒng)的功率流分析及效率計算95:1004- 2539(2007)05- 0094- 03(華南湮工大學(xué)機械工程學(xué)院.廣東廣州510W0)張木青胡青春朱新軍段福海通過對封閉行星齒輪傳動系統(tǒng)內(nèi)部功率流的分析研究了功率分配系數(shù)與系統(tǒng)內(nèi)部功率流 的關(guān)系建立了功率分配系數(shù)與單元傳動比的關(guān)系表達式以及效率計算公式確定了無功率循環(huán)的必要 條件。結(jié)

2、合具體實例繪制了功率流圖譜及效率曲線通過有功率循環(huán)系統(tǒng)與無功率循環(huán)系統(tǒng)的對比. 指出臺理地選擇單元傳動比可避免系統(tǒng)內(nèi)部出現(xiàn)功率循環(huán)從而獲得高效率的傳動。為封閉行星齒輪 傳動系統(tǒng)的設(shè)計提供一種有效簡潔的分析方法。封閉行星齒輪傳動功率流效率引言封閉行星齒輪傳動系統(tǒng)通過雙路徑傳動減小了各 構(gòu)件上的負載.因而，在傳遞相同栽荷條件下,其結(jié)構(gòu) 更加緊湊。由于封閉行星齒輪傳動的上述優(yōu)點，廣泛 地應(yīng)用于工業(yè)機械、起重機械、建筑機械、冶金機械以 及航空機械等現(xiàn)代機械傳動領(lǐng)域。然而如果封閉行 星齒輪傳動系統(tǒng)各支路的傳動比選擇不當.將會使其 內(nèi)部存在較大的循環(huán)功率封閉功率丿。循環(huán)功 率的存在加大了構(gòu)件上的栽荷加劇了

3、磨損.產(chǎn)生較大 的振動和噪聲.嚴重降低了傳動系統(tǒng)的性能。本文通 過對封閉行星齒輪傳動系統(tǒng)內(nèi)部的功率流分析說明 臺理地選擇單元傳動比可獲得高效率的傳動，介紹一 種避免功率循環(huán)的單元傳動比配直方法。1封閉行星齒輪傳動系統(tǒng)如表Ka) (b)所示若將一個簡單的單級行星齒 輪傳動系統(tǒng)與一個差動行星齒輪傳動系統(tǒng)進行封閉式 連接.就形成了封閉行星齒輪傳動系統(tǒng).其中只有一個 固定構(gòu)件.單元間通過構(gòu)件剛性連接(構(gòu)件4、B、d、e 分別為輸入、輸出、連接、制動構(gòu)件丿。很明顯，a)中輸 入功率旳在八利用雙路徑傳遞其中一部分功率Pi 通過2傳遞給輸出軸，另一部分功率P2繞過r2傳遞 給輸出軸，(b丿中輸入功率加在n利

4、用兩條路徑傳 遞，其中一部分功率P1通過ri傳遞給儀另一部分功 率力直接傳遞給亠然后在H處匯流輸出。所有的 封閉行星齒輪傳動系統(tǒng)的連接都可簡化為表1結(jié)構(gòu)簡 圖的形式。2 系統(tǒng)內(nèi)部功率流及運動學(xué)關(guān)系表1(a)中轉(zhuǎn)矩和功率由兩條路徑輸出稱為功率 分流輸出型兩級封閉行星齒輪傳動系統(tǒng)'表I (b)中轉(zhuǎn)矩和功率由兩條路徑輸入，稱為功率分流輸入型兩級 封閉行星齒輪傳動系統(tǒng)。二者廣泛地應(yīng)用于動力傳 動系統(tǒng)中，文中主要以二者為研究對象。傳動系統(tǒng)內(nèi) 將給定方向上功率流定義為正方向若實際功率流方 向與定義的方向相同，則為正.反之.則為負。因此.需 要通過計算來判定實際功率流的正負號。定義傳動比/為傳動系統(tǒng)

5、的輸出轉(zhuǎn)速與輸入轉(zhuǎn) 速之比單元傳動比6為制動連接構(gòu)件d時.輸出轉(zhuǎn) 速與輸入轉(zhuǎn)速之比.單元傳動比為固定構(gòu)件e時, 連接構(gòu)件d轉(zhuǎn)速與輸入轉(zhuǎn)速之比(功率分流輸入型) 或輸出轉(zhuǎn)速與連接構(gòu)件d轉(zhuǎn)速之比(功率分流輸出 型)O類型傳動簡圖結(jié)構(gòu)簡圖傳動比創(chuàng)分流輸出傳動分流輸入傳動(b)n(I).&)(&-1)封閉行星齒輪傳動系統(tǒng)內(nèi)環(huán)路的功率流方向取決 于連接構(gòu)件d.如表2。從表2中.可清楚地看到根據(jù) 的取值范圍表1(a)、(b)中的輸入功率存在三種傳 遞方式當0v <1時，表2中的功率流P1-P2方向 為同向稱為無功率循環(huán)當>1時，表2中的功率流P5 方向為順時針方向稱為正功率循環(huán)

6、，當V 0時表2的功率流pi>p2方向為逆時針方向稱為 負功率循環(huán)。本文只對功率分流輸入型的封閉行星齒輪傳動系© 1994-2010 China Academic Journal Electronic Publishing House. All rights resened. 第31巻第5期封閉行星齒輪傳動不統(tǒng)的功率流分析及效率計算#© 1994-2010 China Academic Journal Electronic Publishing House. All rights resened. 第31巻第5期封閉行星齒輪傳動不統(tǒng)的功率流分析及效率計算97統(tǒng)進行分析

7、即表Hb) o2類星來潦入 功分輸a>lPla<0系統(tǒng)輸入功率與各支路傳遞功率的關(guān)系Pm= T,n n,a = P + P,()支路傳遞功率為P = Tdnd(2)式中 m nd分別為連接構(gòu)件d的轉(zhuǎn)矩和轉(zhuǎn)速。、 是輸入功率在各支路上的分配系數(shù).二者滿足+ = 1 表1(b)中傳動比和功率分配系數(shù)與單元傳動比 的關(guān)系式為單元傳動比丄丄仃»2= “ABlAd將式(4丿代入表1( U)中得傳動比表達式i = ,r = / + 12 - ilii AB根據(jù)廳星齒輪運動學(xué)關(guān)系，則構(gòu)件"的轉(zhuǎn)矩和轉(zhuǎn) 速為仏1 J - ii. 如Td =e .d in = '丿&quo

8、t;d =g = °2 刃in'6丿AB 9IAB1'Ad由式(1八式(2八式(6丿得功率分配系數(shù)表達式Pm il + 12 6/2封閉行星齒輪傳動系統(tǒng)內(nèi)環(huán)路出現(xiàn)功率循環(huán)將會 増加輪齒和軸承上栽荷.加劇磨損.從而使其傳動效率 降低。通過以上分析可知功率分配系數(shù)、是單 元傳動比的函數(shù).單元傳動比決定著輸入功率在支路 上的分配和有無功率循環(huán).因此通過合理地選擇單元 傳動比便可實現(xiàn)傳動系統(tǒng)無功率循環(huán)傳動，其 必要條件為表l(b丿功率分流輸入“ 11 11Ov 一 < 1n + /2 - h >23 系統(tǒng)效率分析文獻/4/對傳動比與效率的關(guān)系定義如下如果運 動傳動

9、比(忽略功率損失)與功率流方向相同那么動 力傳動比(考慮功率損失丿為運動傳動比乘以效率； 如果運動傳動比與功率流方向相反.則動力傳動比為 運動傳動比乘以效率倒數(shù)，這種理論對于復(fù)殺傳 動也正確°從表2中可以看出.功率Px流經(jīng)兩個行星 齒輪傳動單元.功率P2流經(jīng)一個行星齒輪傳動單元c 設(shè)每個傳動單元轉(zhuǎn)醫(yī)固定時的效率分別為I、2,只 考慮由輪齒間摩擦引起的損失.一般取值為1=2 = 0.96。則兩級封閉行星齒輪傳動系統(tǒng)傳動效率 紬的 計算公式AB=2+2'V(9)其中JC = 11 V = 1»> 1 x = 1 F v = - 1.0 <<0. 5(1

10、0) x = 1, y = 0,0. 5 v < 1乂 x = 1=1.<0由式、式(1()丿可得12+/ 2 >1+ 2rO< <0.5AB =1(11丿1 + ,0. 5 << 1./ I 2 +2»<04實例分析3齒輪序號123456國126B5?ISIS4502261352261352圖1 .圖2為功率分流輸入型傳動結(jié)構(gòu)其各齒輪 齒數(shù)如表3中所示運動學(xué)計算如下圖1單元傳動比兒=傳動比/=0. 555功率分配系數(shù)=1.602,0. 602 傳動效率ab = 0. 849圖2 單元傳動比幾=0. 3333 ,f2 =0. 3333傳

11、動比/ = 0. 555功率分配系數(shù) =0.400,0. 600 傳動效率肋=0.976結(jié)合上述實例.以單元傳動比/1為橫坐標,2為 縱坐標通過給定的傳動比匚根據(jù)式心丿建立h與“ 的函數(shù)關(guān)系式.并繪出其函數(shù)圖像，在圖中以細實線表 示，根據(jù)式仃丿建立 與的函數(shù)關(guān)系式，繪出函 數(shù)圖像，在圖中以點劃線表示.這些點劃線將坐標系劃 分為無功率循環(huán)區(qū)、正功率循環(huán)區(qū)和負功率循環(huán)區(qū).在 上述基礎(chǔ)上根據(jù)式(11丿建立了系統(tǒng)傳動效率 佔與 功率分配系數(shù)、的函數(shù)關(guān)系式.繪出函數(shù)圖像，在圖 中以短劃線表示。S3功率分流輸入型傳勸比及效率曲線圖從圖3中可以看出傳動比/=0, 555的曲線只有 一支，該曲線分布在正功率循

12、環(huán)、無功率循環(huán)和負功率 循環(huán)三個區(qū)域。同樣曲線上的每一點對應(yīng)的八、“ 都滿足20.555。結(jié)合效率曲線可以看出由于該曲 線不存在正負功率循環(huán)的轉(zhuǎn)變區(qū)域'其效率曲線變化 比較平緩。實例圖1對應(yīng)的點為該點位于正功率循環(huán)區(qū), 傳動效率0=0.849。為獲得較髙效率的傳動，通過 調(diào)整溝件連接和齒輪齒數(shù)，即實例圖2.得到"點，該 點位于無功率循環(huán)區(qū)，對應(yīng)的傳動效率為p = 0.976。6結(jié)論本文采用圖解分析模型對封閉行星齒輪傳動系統(tǒng) 內(nèi)部功率流進行了分析確定了功率流方向與功率分 配系數(shù)的關(guān)系通過對單元傳動比的定義推導(dǎo)出傳動 比及功率分配系數(shù)與單元傳動比的函數(shù)關(guān)系式.確定 了系統(tǒng)內(nèi)部無功

13、率循環(huán)的必要條件通過給定傳動比 幾以單元傳動比/1為橫坐標.h為縱坐標繪出傳動 比及效率函數(shù)圖像，形成功率流圖譜.通過功率流圖譜 可直觀地看出循環(huán)功率對系統(tǒng)傳動效率的影響。在封 閉行星齒輪傳動系統(tǒng)設(shè)計中，應(yīng)用本文的分析方法可 快速地驗證傳動系統(tǒng)是否存在功率循環(huán)，若存在功率 循環(huán)則可通過功率流圖譜來選擇避免功率循環(huán)的單 元傳動比.然后根據(jù)單元傳動比合理配置系統(tǒng)中的構(gòu) 件連爰和齒輪齒數(shù).獲得高效率的傳動系統(tǒng)。1 E. Itnneblris. F Freudenstein lhe Kfechanical Hliciency d 巾icydic Ce<ir Thiins. .ASMEJ. Nbc

14、h. Des. 1993.115：64565l2 Del Castillo J. NL 'lhe Analytical Expression d the Miciency d Hanelar Ce<jr Trains. Meeh. Nkch. Theory 2002 37(2) :1972I43 E. fennerfri F. Freudenstein. A Systemilic .Approach k) R)uer - How and Sialic R)rcc Analysis in 年icydic Spur - Gar Tmins. ASME J. 4xh. Des. . 1

15、993,115(3) :639 6444暉德里亞夫采夫B.H.IOH.菱爾便舍夫酋.陳啟松.張展譯.行星 齒輪傳動手冊北京:冶金工業(yè)出版社9865 While G Durixntion of Hgh HTiciency luo Stage Ipicyclic Gars Mxh. Mach. Theory. 2003 .38:149159收稿日期：20060911 收修改椅日期：2OO61O25作者簡介:張木*<1953- ) 男廣東廣州人副製授© 1994-2010 China Academic Journal Electronic Publishing House. All

16、rights resened. 英文摘耍© 1994-2010 China Academic Journal Electronic Publishing House. All rights reserved, © 1994-2010 China Academic Journal Electronic Publishing House. All rights reserved, FXpert System tf (irar's Fhiit Diagnosis hased on Neural Net wrk Li Jia, Li Bin . Wang Mengqing(

17、81) Abstract On the basis of the typical fault mechanisms and vibration chai-acters .a neural network nixlel is sei up for fault diagnosis lhe test results shnv tint the higlier accuracy of the model. An expert system of gear's fault diagnosis based on neural neluork is also constructed by apply

18、ing Windows system and Visual C+ + pwgrani. traditioiial method at signal analysis advanced analysis methods are integrated into gcars fault diagnosis such as wavelcl tranfonn. neural nebwrk and expert system technology. and a multifunction expert system. lhe ware of tliis system has been researched

19、 and piugranmrdKey w)rds: Gear Fault diagnosis Neural nehwrk Expert systemMethod <f (car's Eiidt Diagnosis bused on Spectral Fhtropy Hu Junhui Shao Renping. Zeng Zejun(84) Abstract In the gear is fault diagnosis. the key is how to extract the fault feature fium random signals by proper metlxx

20、is. In fact, lhe signal uv get will be polluted by noise &)nic methods are sensitive lo the noise and difficult to distinguish the faults. such as the power spec- truin. Spectral eiiiupy based on the statistics indicates lhe orderlessncss and is robust to noise In this paper. spectral entiupy is

21、 i nt induced into lhe gear Iransiiission system. the fault features of the gear uilh crack and abrasion are extracted and compared to that of wmial gear, lhe results d analysis and experiment show that the precisions of identification arc liigher than 90 % t is shown that the spectral entropy is su

22、rely an effective method for the fault diagnosis of gear transmission system. Key w>rds: Spectral cntiopy Ivaturc extraction Fault diagnosis Gear transmission systemHTicicncy Analysis and Experiment rf a New lpc d Fitcring (car Reducer Rm Jisheng JJang Xichang .Wang Guangian(88) Abstract The inch

23、ing efficiency cf the ccccnlric reducing mechanism and the filtering jpline gear mechanism of a new tjpe of filtering gear reducer (Giina patent CN1699793A) is analyzed. Each internal gear pair meshing efficiency equation uvre derived by lhe theory analysis method and the lot/ meshing efficiency equ

24、ation of filtering gear reducer wre derived by the contact power niettod Ai last the Ihoory efficiency of a exanple filtering gear reducer was calculated and the experiment was proved, some useful conclusion wre obtainedKey w>rds: filtering gear reducer Internal gear pair Bficiency Contrastivclv

25、Study(mi Mechatronic Topology rf RiniUel HEV Zhao ©gang 丄id Yutao(91) Abstract R)r fulfilling actual requirenKnts of developing RirallcI hybrid electric vehicles (PHEVs) . imthematical nndel of powertrain is designed and the powertrain is simulated by conputer in order to evalir ate vvliicle pe

26、rformance. A calculating metlxxi of equivalent oil oon- sunption has been found on SAE2711 standard Based on sinulation H/tunre . fuel mnsiinption nnd driving perfbminnee of (iifferenl meclia- tronic topology PHEVs are conpared and analyzed And its result will guide development cf trial producing pi

27、utotypc PHEV bus.Key wrds: Rirallel - Hybrid electric vehicle Mechatronic topology SimulationPowr Flow .Analysis and FTficiency Calculation for Closed Planetary (iar Systems Nang Muqing Hu Qinguhun . 2hu Xinjun Diian Fuhai(94) Abstract The relationship between partition coefficient of pouer and powe

28、r flow in system is studied by analyzing closed planetary gear sys* Icms. The expression betuven power partition coefficient and the basic jpeed ratios is developed, lhe expression of dficiency is also proposed The necessary conditions lor power non recirculation aie detemined. lhe graphic charts of

29、 jpecd ratios and efficiency are plotted based on examples given. Analyzing the grapliic charts shows that can obtain lhe high efliciency Iraiisnission by selecting the basic jpeed ratios piuperly. A effective oonpact analysis processing metlpd for design of closed planetarr geared systems is offere

30、d.Key w)r(ls: Gosed planetary gear Hficicncy R)vr flow Experiment Research on Tooth Form Factor and Stress Correction Factor cf kivolute Gfear with a Snnll Number tf Teeth Sun Fu . Zhang Jic, Chen ingshu(97) Abstract Experinrt reseach about involute gear's tooth form factor and stress correction

31、 factor by applying 30o tangeiU n»thod is carried out. laxh profile generating experiment to teeth number is carried out measur/ tooth root chord at lhe critical section S用.bending nnment ami for rxX stress “ and mot fillet radius d' tooth / are nrasuiicd and diagrams of involute gear's

32、 tooth form factor and stress correction factor are given. Ek sign resourse for involute gear's strenlh design with a snail number of teeth is sipplicdKey wirds : Tooth form factor Stress correction factor Expert ment nrthixl Tooth pidllc generatingThe Rrsairch on Experiment of Time Sequence bet

33、 wen CamsGe ng Qnqiang, 加 ng 刀 liqiang . Li Zhenjie( 100) Abstract Rotating in)vemcnt is often changed ink) linear nwvviiKiit in (he machine design and there are time sequence relations in various fbnns ct movemenl A methjd of oonwrting staling nDvement of cams into lnriA)nt;il linear irovtiwnt and vertical linear mavcmenl is proposed .and the time sequence are realize