裝配圖復(fù)合形法減速器優(yōu)化設(shè)計(jì)
裝配圖復(fù)合形法減速器優(yōu)化設(shè)計(jì),裝配,復(fù)合,減速器,優(yōu)化,設(shè)計(jì)
畢業(yè)設(shè)計(jì)（論文）任務(wù)書
I、畢業(yè)設(shè)計(jì)(論文)題目：
復(fù)合形法減速器優(yōu)化設(shè)計(jì)
II、畢 業(yè)設(shè)計(jì)(論文)使用的原始資料(數(shù)據(jù))及設(shè)計(jì)技術(shù)要求：
1、原始數(shù)據(jù)：
單級(jí)圓柱齒輪減速器，已知輸入功率P=22kW，輸入轉(zhuǎn)速n1=960r/min，傳動(dòng)比i=4.5，
工作壽命10年，每年工作300天。
2、設(shè)計(jì)技術(shù)要求：
1）采用復(fù)合形法，以體積最小為目標(biāo)進(jìn)行減速器優(yōu)化設(shè)計(jì)；
2）與常規(guī)設(shè)計(jì)結(jié)果進(jìn)行比較分析；
3）繪制減速器裝配圖及主要零件圖。
III、畢 業(yè)設(shè)計(jì)(論文)工作內(nèi)容及完成時(shí)間：
1. 收集資料、開題報(bào)告、外文翻譯（6000字符以上） 3.01-3.21（3周）
2. 建立優(yōu)化設(shè)計(jì)的數(shù)學(xué)模型 3.22-4.04 (2周)
3．編寫優(yōu)化設(shè)計(jì)程序、計(jì)算 4.05-5.09 (5周)
4. 減速器常規(guī)設(shè)計(jì)計(jì)算、結(jié)果分析 5.09-5.23 (2周)
5. 繪制減速器裝配圖及主要零件圖 5.24-6.13 (3周)
6. 撰寫畢業(yè)設(shè)計(jì)論文 6.14-6.27 (2周)
7．答辯準(zhǔn)備及論文答辯 6.28-7.02（1周)
Ⅳ 、主 要參考資料：
[1] 璞良貴，紀(jì)名剛主編.機(jī)械設(shè)計(jì).第八版.北京：高等教育出版社，2007
[2] 孫靖民主編.機(jī)械優(yōu)化設(shè)計(jì).第三版.北京：機(jī)械工業(yè)出版社，2005
[3] 方世杰，綦耀光主編.機(jī)械優(yōu)化設(shè)計(jì).北京：機(jī)械工業(yè)出版社，1997.2
[4] 王昆等主編. 機(jī)械設(shè)計(jì)課程設(shè)計(jì)手冊(cè).北京：機(jī)械工業(yè)出版社，2004
[5] Carrol, R., and Johnson, G.,“Optimal design of compact spur gear sets”, ASME Journal of mechanisms, transmissions and automation in design. Vol.106, No.1, March 1984, pp.95-101
航空工程 系 機(jī)械設(shè)計(jì)制造及其自動(dòng)化 專業(yè) 0781052 班
學(xué)生（簽名）：
日期：自 2010 年 3 月 1 日至 2010 年 7 月 2日
指導(dǎo)教師（簽名）：
助理指導(dǎo)教師(并指出所負(fù)責(zé)的部分)：
機(jī)械設(shè)計(jì) 系（室） 主任（簽名）： 賀紅林
附注:任務(wù)書應(yīng)該附在已完成的畢業(yè)設(shè)計(jì)說明書首頁。
畢業(yè)設(shè)計(jì)（論文）
題目： 復(fù)合形法減速器的優(yōu)化設(shè)計(jì)
系 別 航空工程系
專業(yè)名稱 機(jī)械設(shè)計(jì)制造及其自動(dòng)化
班級(jí)學(xué)號(hào) 078105206
學(xué)生姓名 戴曉思
指導(dǎo)教師 朱保利
二O一一年 六 月
單級(jí)圓柱齒輪減速器復(fù)合形法fortran優(yōu)化源程序
C ==============
PROGRAM COMPLE
C ==============
DIMENSION X(25),GX(50),XCOM(1250)
COMMON /ONE/ ITE,IXE,ILI,NPE,NFX,NGR
READ(*,*) N,KG,K
WRITE(*,10001) N,KG,K
10001 FORMAT(25X,'========== PRIMARY DATA =========='//5X,
1 'N=',I4,5X,'KG=',I4,5X,'K=',I4)
CALL MAISUB(N,K,KG,X,GX,XCOM)
STOP
END
C ===================================
SUBROUTINE MAISUB(N,K,KG,X,GX,XCOM)
C ===================================
DIMENSION X(N),GX(KG),XCOM(N,K),FXK(50),XR(25)
DIMENSION XO(25),XH(25),XL(25),BL(25),BU(25)
COMMON /ONE/ ITE,IXE,ILI,NPE,NFX,NGR
COMMON /TWO/ ISE
READ(*,*) (X(I),I=1,N)
READ(*,*) EPS
READ(*,*) KWR,ISE
READ(*,*) (BL(I),I=1,N),(BU(I),I=1,N)
WRITE(*,1010) (BL(I),I=1,N)
WRITE(*,1015) (BU(I),I=1,N)
WRITE(*,1020) EPS
1010 FORMAT(' BL:'/(5X,5E15.6))
1015 FORMAT(' BU:'/(5X,5E15.6))
1020 FORMAT(5X,'EPS=',E10.2)
ITE=0
NFX=0
IXE=0
RM=2657863.0
1025 CALL PRICOM(N,K,KG,X,GX,XCOM,FXK,BL,BU,RM)
IF(KWR.LT.0) GOTO 1041
WRITE(*,1030)
1030 FORMAT(/25X,'========== PRIMARY COMPLEX =========='/)
WRITE(*,1080) K
DO 1031 L=1,K
WRITE(*,1085) L,(XCOM(I,L),I=1,N)
1031 CONTINUE
WRITE(*,1035) (FXK(I),I=1,K)
1035 FORMAT(4X,'FXK:'/(5X,5E15.6))
1041 WRITE(*,1042)
1042 FORMAT(/25X,'========== ITEATION COMPUTE =========='/)
1045 ITE=ITE+1
CALL FXSEGU(N,K,XCOM,FXK)
DO 1050 I=1,N
1050 XL(I)=XCOM(I,K)
FXL=FXK(K)
SDX=0.0
DO 1055 I=1,K-1
1055 SDX=SDX+(FXL-FXK(I))**2
=SQRT(SDX/FLOAT(K-1))
IF(SDX.LE.EPS) GOTO 1210
IF(KWR.GT.0) GOTO 1056
IF(ITE/10*10.NE.ITE) GOTO 1090
1056 WRITE(*,1060) ITE,FXL
IF(KWR.LT.0) GOTO 1090
WRITE(*,1065) (XL(I),I=1,N)
WRITE(*,1070) FXL
WRITE(*,1075) (GX(I),I=1,KG)
WRITE(*,1035) (FXK(I),I=1,K)
1060 FORMAT(/1X,'***** ITE=',I4,5X,'FXL=',E15.7)
1065 FORMAT(' X :'/(5X,5E15.6))
1070 FORMAT(' FX:'/(5X,5E15.6))
1075 FORMAT(' GX:'/(5X,5E15.6))
1080 FORMAT(' XCOM: (K=',I3,')')
1085 FORMAT(2X,I2/(5X,5E15.6))
1090 LH=1
1095 DO 1100 I=1,N
1100 XH(I)=XCOM(I,LH)
FXH=FXK(LH)
CALL XCENTE(N,K,K,LH,XO,XCOM)
CALL FFX(N,XO,FXO)
CALL GGX(N,KG,XO,GX)
DO 1105 J=1,KG
IF(GX(J).GE.0.0) GOTO 1170
1105 CONTINUE
1140 PHI=1.3
1145 DO 1150 I=1,N
1150 XR(I)=XO(I)+PHI*(XO(I)-XH(I))
CALL FFX(N,XR,FXR)
CALL GGX(N,KG,XR,GX)
DO 1151 J=1,KG
IF(GX(J).GE.0.0) GOTO 1152
1151 CONTINUE
GOTO 1155
1152 PHI=0.5*PHI
GOTO 1145
1155 IF(FXR.LT.FXH) GOTO 1160
IF(PHI.LE.1E-10) GOTO 1195
PHI=0.5*PHI
GOTO 1145
1160 DO 1165 I=1,N
1165 XCOM(I,LH)=XR(I)
FXK(LH)=FXR
GOTO 1045
1170 DO 1175 I=1,N
BL(I)=XL(I)
BU(I)=XO(I)
1175 CONTINUE
DO 1180 I=1,N
1180 X(I)=XL(I)
ISE=1
GOTO 1025
1195 LH=LH+1
WRITE(*,1200) LH
1200 FORMAT(1X,'****** LH=',I2,'*****')
IF(LH.LE.K/2) GOTO 1095
WRITE(*,1205)
1205 FORMAT(/25X,'********** ITERTION ABORTIVE **********'/)
GOTO 1220
1210 WRITE(*,1215)
1215 FORMAT(/25X,'========== OPTIMUM SOLUTION =========='/)
1220 WRITE(*,1225) ITE,NFX,IXE
1225 FORMAT(' ITE=',I5,' NFX=',I5' IXE=',I5)
WRITE(*,1065) (XL(I),I=1,N)
WRITE(*,1070) FXL
WRITE(*,1075) (GX(I),I=1,KG)
RETURN
END
C ================================================
SUBROUTINE PRICOM(N,K,KG,X,GX,XCOM,FXK,BL,BU,RM)
C ================================================
DIMENSION X(N),XO(25),BL(N),BU(N),GX(KG),XCOM(N,K),FXK(K)
COMMON /TWO/ ISE
2020 IF(ISE) 2025,2050,2075
2025 WRITE(*,2019)
2019 FORMAT(5X,'READ XCOM (FORMAT: * )')
READ(*,*) ((XCOM(I,J),I=1,N),J=1,K)
DO 2045 L=1,K
DO 2030 I=1,N
2030 X(I)=XCOM(I,L)
CALL FFX(N,X,FXK(L))
CALL GGX(N,KG,X,GX)
DO 2031 J=1,KG
IF(GX(J).GE.0.0) GOTO 2075
2031 CONTINUE
2045 CONTINUE
RETURN
2050 CALL FFX(N,X,FXK(1))
CALL GGX(N,KG,X,GX)
DO 2051 L=1,KG
IF(GX(L).GE.0.0) GOTO 2075
2051 CONTINUE
GOTO 2095
2075 DO 2080 I=1,N
CALL RANDOM(RM,Q)
2080 X(I)=BL(I)+Q*(BU(I)-BL(I))
CALL FFX(N,X,FXK(1))
CALL GGX(N,KG,X,GX)
DO 2081 L=1,KG
IF(GX(L).GE.0.0) GOTO 2075
2081 CONTINUE
2095 DO 2100 I=1,N
2100 XCOM(I,1)=X(I)
DO 2110 L=2,K
DO 2105 I=1,N
CALL RANDOM(RM,Q)
XCOM(I,L)=BL(I)+Q*(BU(I)-BL(I))
2105 CONTINUE
2110 CONTINUE
LH=0
DO 2155 LL=1,K-1
LL2=LL
CALL XCENTE(N,K,LL2,LH,XO,XCOM)
CALL FFX(N,XO,FXO)
CALL GGX(N,KG,X,GX)
DO 2111 L=1,KG
IF(GX(L).GE.0.0) GOTO 2075
2111 CONTINUE
2115 CONTINUE
LL1=LL+1
DO 2120 I=1,N
2120 X(I)=XCOM(I,LL1)
2125 CALL FFX(N,X,FXK(LL1))
CALL GGX(N,KG,X,GX)
DO 2126 L=1,KG
IF(GX(L).GE.0.0) GOTO 2145
2126 CONTINUE
DO 2140 I=1,N
2140 XCOM(I,LL1)=X(I)
GOTO 2155
2145 DO 2150 I=1,N
2150 X(I)=XO(I)+0.5*(X(I)-XO(I))
GOTO 2125
2155 CONTINUE
RETURN
END
C ===============================
SUBROUTINE FXSEGU(N,K,XCOM,FXK)
C ===============================
DIMENSION X(25),XCOM(N,K),FXK(K)
DO 3010 L=1,K-1
KL=K-L
DO 3005 LP=1,KL
LP1=LP+1
IF(FXK(LP).GT.FXK(LP1)) GOTO 3005
W=FXK(LP)
FXK(LP)=FXK(LP1)
FXK(LP1)=W
DO 3000 I=1,N
X(I)=XCOM(I,LP)
XCOM(I,LP)=XCOM(I,LP1)
3000 XCOM(I,LP1)=X(I)
3005 CONTINUE
3010 CONTINUE
RETURN
END
C ====================================
SUBROUTINE XCENTE(N,K,LL,LH,XO,XCOM)
C ====================================
DIMENSION XO(N),XCOM(N,K)
COMMON /ONE/ ITE,IXE,ILI,NPE,NFX,NGR
IXE=IXE+1
DO 4015 I=1,N
XS=0.0
DO 4000 L=1,LL
IF(L.EQ.LH) GOTO 4000
XS=XS+XCOM(I,L)
4000 CONTINUE
IF(LH) 4010,4010,4005
4005 XO(I)=XS/FLOAT(LL-1)
GOTO 4015
4010 XO(I)=XS/FLOAT(LL)
4015 CONTINUE
RETURN
END
SUBROUTINE RANDOM(RM,Q)
C =======================
C =======================
RM35=2.0**35
RM36=2.0*RM35
RM37=2.0*RM36
RM =5.0*RM
IF(RM.GE.RM37) RM=RM-RM37
IF(RM.GE.RM36) RM=RM-RM36
IF(RM.GE.RM35) RM=RM-RM35
Q=RM/RM35
RETURN
END
一、選題的依據(jù)及意義：
隨著社會(huì)的發(fā)展和人民生活水平的提高，人們對(duì)產(chǎn)品的需求是多樣化的，這就決定了未來的生產(chǎn)方式趨向多品種、小批量。在各行各業(yè)中十分廣泛地使用著齒輪減速器，它是一種不可缺少的機(jī)械傳動(dòng)裝置. 它是機(jī)械設(shè)備的重要組成部分和核心部件。目前，國(guó)內(nèi)各類通用減速器的標(biāo)準(zhǔn)系列已達(dá)數(shù)百個(gè)，基本可滿足各行業(yè)對(duì)通用減速器的需求。國(guó)內(nèi)減速器行業(yè)重點(diǎn)骨干企業(yè)的產(chǎn)品品種、規(guī)格及參數(shù)覆蓋范圍近幾年都在不斷擴(kuò)展，產(chǎn)品質(zhì)量已達(dá)到國(guó)外先進(jìn)工業(yè)國(guó)家同類產(chǎn)品水平，承擔(dān)起為國(guó)民經(jīng)濟(jì)各行業(yè)提供傳動(dòng)裝置配套的重任，部分產(chǎn)品還出口至歐美及東南亞地區(qū)，推動(dòng)了中國(guó)裝配制造業(yè)發(fā)展。
圓柱齒輪減速器是一種使用非常廣泛的機(jī)械傳動(dòng)裝置。減速器是用于原動(dòng)機(jī)與工作機(jī)之間的獨(dú)立的傳動(dòng)裝置，用來降低轉(zhuǎn)速和增大轉(zhuǎn)矩，以滿足工作需要。在現(xiàn)代機(jī)械中應(yīng)用極為廣泛，具有品種多、批量小、更新?lián)Q代快的特點(diǎn)。目前生產(chǎn)的各種類型的減速器還存在著體積大、重量重、承載能力低、成本高和使用壽命短等問題，與國(guó)外先進(jìn)產(chǎn)品相比還有較大的差距。對(duì)減速器進(jìn)行優(yōu)化設(shè)計(jì)，選擇最佳參數(shù)是提高承載能力、減輕重量和降低成本等各項(xiàng)指標(biāo)的一種重要途徑。
目的： 通過設(shè)計(jì)熟悉機(jī)器的具體操作，增強(qiáng)感性認(rèn)識(shí)和社會(huì)適應(yīng)能力，進(jìn)一步鞏固、 深化已學(xué)過的理論知識(shí)，提高綜合運(yùn)用所學(xué)知識(shí)發(fā)現(xiàn)問題、解決問題的能力。學(xué)習(xí)機(jī)械設(shè)計(jì)的一般方法，掌握通用機(jī)械零件、機(jī)械傳動(dòng)裝置或簡(jiǎn)單機(jī)械的設(shè)計(jì)原理和過程。對(duì)所學(xué)技能的訓(xùn)練，例如：計(jì)算、繪圖、查閱設(shè)計(jì)資料和手冊(cè)，運(yùn)用標(biāo)準(zhǔn)和規(guī)范等。學(xué)會(huì)利用多種手段(工具)解決問題，如：在本設(shè)計(jì)中可選擇CAD等制圖工具。了解減速器內(nèi)部齒輪間的傳動(dòng)關(guān)系。
意義： 通過設(shè)計(jì)，培養(yǎng)學(xué)生理論聯(lián)系實(shí)際的工作作風(fēng)，提高分析問題、解決問題的獨(dú)立工作能力；通過實(shí)習(xí)，加深學(xué)生對(duì)專業(yè)的理解和認(rèn)識(shí)，為進(jìn)一步開拓專業(yè)知識(shí)創(chuàng)造條件，鍛煉動(dòng)手動(dòng)腦能力，通過實(shí)踐運(yùn)用鞏固了所學(xué)知識(shí)，加深了解其基本原理
二、國(guó)內(nèi)外研究概況及發(fā)展趨勢(shì)（含文獻(xiàn)綜述）：
1、國(guó)外減速器技術(shù)發(fā)展簡(jiǎn)況
齒輪減速器在各行各業(yè)中十分廣泛地使用著，是一種不可缺少的機(jī)械傳動(dòng)裝置。當(dāng)前減速器普遍存在著體積大、重量大，或者傳動(dòng)比大而機(jī)械效率過低的問題。
國(guó)外的減速器，以德國(guó)、丹麥和日本處于領(lǐng)先地位，特別在材料和制造工藝方面占據(jù)優(yōu)勢(shì)，減速器工作可靠性好，使用壽命長(zhǎng)。但其傳動(dòng)形式仍以定軸齒輪傳動(dòng)為主，體積和重量問題，也未解決好。最近報(bào)導(dǎo)，日本住友重工研制的FA型高精度減速器，美國(guó)Alan-Newton公司研制的X-Y式減速器，在傳動(dòng)原理和結(jié)構(gòu)上與本項(xiàng)目類似或相近，都為目前先進(jìn)的齒輪減速器。當(dāng)今的減速器是向著大功率、大傳動(dòng)比、小體積、高機(jī)械效率以及使用壽命長(zhǎng)的方向發(fā)展。因此，除了不斷改進(jìn)材料品質(zhì)、提高工藝水平外，還在傳動(dòng)原理和傳動(dòng)結(jié)構(gòu)上深入探討和創(chuàng)新，平動(dòng)齒輪傳動(dòng)原理的出現(xiàn)就是一例。減速器與電動(dòng)機(jī)的連體結(jié)構(gòu)，也是大力開拓的形式，并已生產(chǎn)多種結(jié)構(gòu)形式和多種功率型號(hào)的產(chǎn)品。
目前，超小型的減速器的研究成果尚不明顯。在醫(yī)療、生物工程、機(jī)器人等領(lǐng)域中，微型發(fā)動(dòng)機(jī)已基本研制成功，美國(guó)和荷蘭近期研制的分子發(fā)動(dòng)機(jī)的尺寸在納米級(jí)范圍，如能輔以納米級(jí)的減速器，則應(yīng)用前景遠(yuǎn)大。
2、國(guó)內(nèi)減速器技術(shù)發(fā)展簡(jiǎn)況
國(guó)內(nèi)的減速器多以齒輪傳動(dòng)、蝸桿傳動(dòng)為主，但普遍存在著功率與重量比小，或者傳動(dòng)比大而機(jī)械效率過低的問題。另外，材料品質(zhì)和工藝水平上還有許多弱點(diǎn)，特別是大型的減速器問題更突出，使用壽命不長(zhǎng)。國(guó)內(nèi)使用的大型減速器(500kw以上)，多從國(guó)外(如丹麥、德國(guó)等)進(jìn)口，花去不少的外匯。60年代開始生產(chǎn)的少齒差傳動(dòng)、擺線針輪傳動(dòng)、諧波傳動(dòng)等減速器具有傳動(dòng)比大，體積小、機(jī)械效率高等優(yōu)點(diǎn)?。但受其傳動(dòng)的理論的限制，不能傳遞過大的功率，功率一般都要小于40kw。由于在傳動(dòng)的理論上、工藝水平和材料品質(zhì)方面沒有突破，因此，沒能從根本上解決傳遞功率大、傳動(dòng)比大、體積小、重量輕、機(jī)械效率高等這些基本要求。90年代初期，國(guó)內(nèi)出現(xiàn)的三環(huán)(齒輪)減速器，是一種外平動(dòng)齒輪傳動(dòng)的減速器，它可實(shí)現(xiàn)較大的傳動(dòng)比，傳遞載荷的能力也大。它的體積和重量都比定軸齒輪減速器輕，結(jié)構(gòu)簡(jiǎn)單，效率亦高。由于該減速器的三軸平行結(jié)構(gòu)，故使功率/體積(或重量)比值仍小。且其輸入軸與輸出軸不在同一軸線上，這在使用上有許多不便。北京理工大學(xué)研制成功的"內(nèi)平動(dòng)齒輪減速器"不僅具有三環(huán)減速器的優(yōu)點(diǎn)外，還有著大的功率/重量(或體積)比值，以及輸入軸和輸出軸在同一軸線上的優(yōu)點(diǎn)，處于國(guó)內(nèi)領(lǐng)先地位。國(guó)內(nèi)有少數(shù)高等學(xué)校和廠礦企業(yè)對(duì)平動(dòng)齒輪傳動(dòng)中的某些原理做些研究工作，發(fā)表過一些研究論文，在利用擺線齒輪作平動(dòng)減速器開展了一些工作。二、平動(dòng)齒輪減速器工作原理簡(jiǎn)介,平動(dòng)齒輪減速器是指一對(duì)齒輪傳動(dòng)中，一個(gè)齒輪在平動(dòng)發(fā)生器的驅(qū)動(dòng)下作平面平行運(yùn)動(dòng)，通過齒廓間的嚙合，驅(qū)動(dòng)另一個(gè)齒輪作定軸減速轉(zhuǎn)動(dòng)，實(shí)現(xiàn)減速傳動(dòng)的作用。平動(dòng)發(fā)生器可采用平行四邊形機(jī)構(gòu)，或正弦機(jī)構(gòu)或十字滑塊機(jī)構(gòu)。本成果采用平行四邊形機(jī)構(gòu)作為平動(dòng)發(fā)生器。平動(dòng)發(fā)生器可以是虛擬的采用平行四邊形機(jī)構(gòu)，也可以是實(shí)體的采用平行四邊形機(jī)構(gòu)。有實(shí)用價(jià)值的平動(dòng)齒輪機(jī)構(gòu)為內(nèi)嚙合齒輪機(jī)構(gòu)，因此又可以分為內(nèi)齒輪作平動(dòng)運(yùn)動(dòng)和外齒輪作平動(dòng)運(yùn)動(dòng)兩種情況。外平動(dòng)齒輪減速機(jī)構(gòu)，其內(nèi)齒輪作平動(dòng)運(yùn)動(dòng)，驅(qū)動(dòng)外齒輪并作減速轉(zhuǎn)動(dòng)輸出。該機(jī)構(gòu)亦稱三環(huán)(齒輪)減速器。由于內(nèi)齒輪作平動(dòng)，兩曲柄中心設(shè)置在內(nèi)齒輪的齒圈外部，故其尺寸不緊湊，不能解決體積較大的問題。?內(nèi)平動(dòng)齒輪減速，其外齒輪作平動(dòng)運(yùn)動(dòng)，驅(qū)動(dòng)內(nèi)齒輪作減速轉(zhuǎn)動(dòng)輸出。由于外齒輪作平動(dòng)，兩曲柄中心能設(shè)置在外齒輪的齒圈內(nèi)部，大大減少了機(jī)構(gòu)整體尺寸。由于內(nèi)平動(dòng)齒輪機(jī)構(gòu)傳動(dòng)效率高、體積小、輸入輸出同軸線，故由廣泛的應(yīng)用前景。? 三、本項(xiàng)目的技術(shù)特點(diǎn)與關(guān)鍵技術(shù)? 1.本項(xiàng)目的技術(shù)特點(diǎn),本新型的"內(nèi)平動(dòng)齒輪減速器"與國(guó)內(nèi)外已有的齒輪減速器相比較，有如下特點(diǎn)：(1)傳動(dòng)比范圍大，自I=10起，最大可達(dá)幾千。若制作成大傳動(dòng)比的減速器，則更顯示出本減速器的優(yōu)點(diǎn)。(2)傳遞功率范圍大：并可與電動(dòng)機(jī)聯(lián)成一體制造。(3)結(jié)構(gòu)簡(jiǎn)單、體積小、重量輕。比現(xiàn)有的齒輪減速器減少1/3左右。(4)機(jī)械效率高。嚙合效率大于95%，整機(jī)效率在85%以上，且減速器的效率將不隨傳動(dòng)比的增大而降低，這是別的許多減速器所不及的。 (5)本減速器的輸入軸和輸出軸是在同一軸線上
三、研究?jī)?nèi)容及實(shí)驗(yàn)方案：
研究?jī)?nèi)容：
1.采用復(fù)合形法，以體積最小為目標(biāo)進(jìn)行減速器優(yōu)化設(shè)計(jì)；
2.與常規(guī)設(shè)計(jì)結(jié)果進(jìn)行比較分析，
3.繪制減速器裝配圖及主要零件圖。
實(shí)驗(yàn)方案：
1. 收集有關(guān)資料寫開題報(bào)告
2. 以減速器體積最小為目標(biāo)函數(shù)建立優(yōu)化設(shè)計(jì)的數(shù)學(xué)模型
3．采用復(fù)合型法編寫優(yōu)化設(shè)計(jì)程序、計(jì)算
4. 計(jì)算減速器各項(xiàng)尺寸，并進(jìn)行結(jié)果分析
5. 運(yùn)用UG繪制減速器裝配圖及主要零件圖
6. 翻譯外文資料
7.撰寫畢業(yè)設(shè)計(jì)論文
四、目標(biāo)、主要特色及工作進(jìn)度
目標(biāo)：本課題以減速器體積最小為目標(biāo)函數(shù)，設(shè)計(jì)減速器的最優(yōu)參數(shù)，
繪制減速器裝配圖及主要零件圖。
主要特色：減速器體積小，重量輕，承載能力提高，降低成本
工作進(jìn)度：
1. 收集資料、開題報(bào)告、外文翻譯 3，01-3.21
2. 建立優(yōu)化設(shè)計(jì)的數(shù)學(xué)模型 3.22-4.04
3．編寫優(yōu)化設(shè)計(jì)程序、計(jì)算 4.05-5.09
4. 減速器常規(guī)設(shè)計(jì)計(jì)算、結(jié)果分析 5.09-5.23
5. 繪制減速器裝配圖及主要零件圖 5.24-6.13
6. 撰寫畢業(yè)設(shè)計(jì)論文 6.14-6.27
7. 答辯準(zhǔn)備及論文答辯 6.28-7.02
五、參考文獻(xiàn)
【1】璞良貴，紀(jì)名剛主編.機(jī)械設(shè)計(jì).第八版.北京：高等教育出版社，2007
【2】孫靖民主編.機(jī)械優(yōu)化設(shè)計(jì).第三版.北京：機(jī)械工業(yè)出版社，2005
【3】方世杰，綦耀光主編.機(jī)械優(yōu)化設(shè)計(jì).北京：機(jī)械工業(yè)出版社，1997.2
【4】王昆等主編. 機(jī)械設(shè)計(jì)課程設(shè)計(jì)手冊(cè).北京：機(jī)械工業(yè)出版社，2004
【5】劉瑞新，洪遠(yuǎn)征等編著.Visual Basic 程序設(shè)計(jì)教程.第二版. 北京：機(jī)械工業(yè)出版社，2006
【6】楊黎明主編.機(jī)械零件設(shè)計(jì)手冊(cè).北京：國(guó)防工業(yè)出版社，1996
【7】劉瑞新，洪遠(yuǎn)征等編著.Visual Basic 程序設(shè)計(jì)教程上機(jī)指導(dǎo)及習(xí)題解答.第二版. 北京：機(jī)械工業(yè)出版社，2006
【8】鄭貞平，喻德主編.UG NX5中文版三維設(shè)計(jì)與NC加工實(shí)例精解. 北京：機(jī)械工業(yè)出版社，2008
【9】Carrol, R., and Johnson, G.,“Optimal design of compact spur gear sets”, ASME Journal of mechanisms, transmissions and automation in design. Vol.106, No.1, March 1984, pp.95-101
復(fù)合形法減速器優(yōu)化設(shè)計(jì)
學(xué)生姓名: 戴曉思 班級(jí): 078105206
指導(dǎo)老師: 朱保利
摘要：圓柱齒輪減速器是一種使用非常廣泛的機(jī)械傳動(dòng)裝置。減速器是用于原動(dòng)機(jī)與工作機(jī)之間的獨(dú)立的傳動(dòng)裝置，用來降低轉(zhuǎn)速和增大轉(zhuǎn)矩，以滿足工作需要。在現(xiàn)代機(jī)械中應(yīng)用極為廣泛，具有品種多、批量小、更新?lián)Q代快的特點(diǎn)。目前生產(chǎn)的各種類型的減速器還存在著體積大、重量重、承載能力低、成本高和使用壽命短等問題，與國(guó)外先進(jìn)產(chǎn)品相比還有較大的差距。對(duì)減速器進(jìn)行優(yōu)化設(shè)計(jì)，選擇最佳參數(shù)是提高承載能力、減輕重量和降低成本等各項(xiàng)指標(biāo)的一種重要途徑。
單級(jí)圓柱齒輪減速器優(yōu)化設(shè)計(jì)主要是通過計(jì)算機(jī)輔助設(shè)計(jì)，利用fortran語言進(jìn)行編程優(yōu)化。本課題以減速器最大尺寸最小或重量最輕為目標(biāo)函數(shù)，設(shè)計(jì)減速器的最優(yōu)參數(shù)，研究?jī)?nèi)容：采用復(fù)合形法，以體積最小為目標(biāo)進(jìn)行減速器優(yōu)化設(shè)計(jì)，與常規(guī)設(shè)計(jì)結(jié)果進(jìn)行比較分析，繪制減速器3d裝配圖及主要零件圖
此次設(shè)計(jì)的減速器與常規(guī)設(shè)計(jì)比較具有體積小，重量輕，結(jié)構(gòu)緊湊，成本低等問題。編程方法簡(jiǎn)單，能夠很好的達(dá)到優(yōu)化效果，能夠運(yùn)用到工程實(shí)際中去。
關(guān)鍵字： 單級(jí)圓柱齒輪減速器、優(yōu)化設(shè)計(jì)、fortran、復(fù)合型法、體積、 3d設(shè)計(jì)
指導(dǎo)教師簽名：
optimal design of reliability for the single-stage helical cylinder gear reducer
Student name: Dai Xiaosi Class：0781052
Supervisor: Professor Zhu Baoli
Abstract: The wheels gear is a very extensive use of automatic transmission. gear is used for the original motion and the work of the independence of the transmission that is used to reduce speed and torques increase in turn, need to work. in modern machinery used in a wide variety and quantity of small and fast. the upgrading of the production of various kinds of gear have a great volume and weight bearing ability, heavy and low cost and high and use a shorter life span, And advanced product compare there is a large gap. the gear design and optimize the choice of the parameter is to improve the bearing ability, lighten the weight and reduce costs for all the way.
This column with the main gear design is a computer-aided design and optimize the use of fortran programming language. this subject in order to gear the maximum size to the weight or the light of objective function, the design of gear and study the contents of a composite image ：, to save the goal of gear design and optimize the conventional design a comparative analysis, gear and main parts of the assembly drawing
The design of gear and conventional design are a small volume, light weight, compact structure, low cost etc. a programming method is simple to very good to achieve the effect can be applied to the actual.
Keyword: A homopolar bevel gear speed reducer optimizing design fortran complex method volume 3d design
Signature of conductor:
ELEMENTS OF CAM DESIGN
How to plan and produce simple but efficient cams for petrol engines and other mechanisms
Cams are among the most versatile mechanisms available．A cam is a simple two-member device．The input member is the cam itself，while the output member is called the follower．Through the use of cams，a simple input motion can be modified into almost any conceivable output motion that is desired．Some of the common applications of cams are
——Camshaft and distributor shaft of automotive engine
——Production machine tools
——Automatic record players
——Printing machines
——Automatic washing machines
——Automatic dishwashers
The contour of high-speed cams (cam speed in excess of 1000 rpm) must be determined mathematically．However，the vast majority of cams operate at low speeds(less than 500 rpm) or medium-speed cams can be determined graphically using a large-scale layout．In general，the greater the cam speed and output load，the greater must be the precision with which the cam contour is machined．
Cams in some form or other are essential to the operation of many kinds of mechanical devices. Their best-known application is in the valve-operating gear of internal combustion engines, but they play an equally important part in industrial machinery, from printing presses to reaping machines.
In general, a cam can be defined as a projection on the face of a disc or the surface of a cylinder for the purpose of producing intermittent reciprocating motion of a contacting member or follower. Most cams operate by rotary motion, but this is not an essential condition and in special cases the motion may be semi-rotary， oscillatory or swinging. Even straight-line motion of the operating member is possible, though the term cam may not be considered properly applicable in such circumstances.
Most text books on mechanics give some information on the design of cams and show examples of cam forms plotted to produce various orders of motion. Where neither the operating speed nor the mechanical duty is very high, there is a good deal of latitude in the nermissible design of the cam and it is only necessary to avoid excessively steep contours or abrupt changes which would result in noise, impact shock, and side pressure on the follower. But, with increase of either speed or load, much more exacting demands are made on the cam, calling for the most careful design and, at very high speed, the effect of inertia on the moving parts is most pronounced, so that the further factors of acceleration and rate of lift have to be taken into account and these are rarely dealt with in any detail in the standard text books.
The design of the cam follower is also of great importance and bears a definite relation to the shape of the cam itself. This is because the cam cannot make contact with the follower at a single fixed point. Surface contact is necessary to distribute load and avoid excess wear, thus the cam transmits its motion through various points of location on the follower, depending on the shape of the two complementary members. The cams for operating i.c. engine valves present specially difficult problems in design. In the case of racing engines, both the load and speed may be regarded as extreme, because in many engines the rate at which the valves can be effectively controlled is the limiting factor in engine performance. In some respects, cam design of miniature engines is simplified by reason of their lighter working parts (and consequent less inertia) but on the other hand, working friction is usually greater and rotational speeds are generally considerably higher than in full-size practice.
In the many designs for small four-stroke engines which I have published, I have sought to simplify valve operation and to provide designs for cams which can be simply and accurately produced with the facilities of the amateur workshop. Numerous engine designs which have been submitted to me by readers have contained errors in the valve gear and particularly in the cams and in view of prevalent misconceptions in the fundamental principles of these items, I am giving some advice on the matter which I trust will help individual designers to obtain the best results from their engines. There have been many engines built with cams of thoroughly bad design but which, in spite of this, have produced results more or less satisfactory to their constructors. It may be said that within certain limits of speed one can get away with murder but in no case can an engine perform efficiently with badly designed cams, or indeed errors in any of its working details. This article is concerned mainly with the design of cams for operating the valves of i.c. engines and, in order to avoid any confusion of terms, Fig. 1 shows the various parts of a cam of this type and explains their functions. The circular, concentric portion of the cam, which has no operative effect, is known as the base circle: the humy of the cam (shown shaded) is known as the lobe, and the flanks on either side rise from the base circle to the nose, which is usually rounded.Lift may be defined as the difference between the radius of the base circle and that of the nose. the anele enclosed between the points where the flanks join the base circle is termed the angular ‘period, representing the proportion of the full cycle during which the cam operates the valve gear. In Fig. 2, typical examples of cams used in i.c. engines are illustrated. The tangent cam, A, has dead straight flanks-which as the name implies form tangents to the base circle. This type of cam is easy to design and produce, the simplest method of machining being by a circular milling process forming a concentric surface on the base circle and running straight out tangentially where the flanks start and finish. It can also be produced by filing and I have in the past described how to make it with the aid of a roller filing rest in the lathe, in conjunction with indexing gear to locate the flank angles.
Tangent cams can only work efficiently in conjunction with a convex curved follower, as this is the only way in which the flank can be brought progressively and smoothly into action. Some time ago an engine was described having tangent cams in conjunction with flat followers. This was not intended for extremely high speed and very likely produced all the power required of it, but it is quite clear that the flat face of the tangent cam. On engaging the flat tappet-over the full length of the flank all at once, must produce an abrupt slapping action which is noisy, inefficient and destructive in the long run. Rollers are often used as followers with tangent cams and are satisfactory in respect of their shape, but the idea of introducing rolling motion at this point is not as good as it seems at first sight, because it merely transfers the sliding friction to a much smaller area--that of the pivot pin. It is possible in some cases, however, to use a ball or roller race for the follower and this, at any rate, has the merit of distributing and equalizing the wearing surface.
Tangent cams have been used with a certain degree of success for high-performance-engines and were at one time popular on racing motorcycle engines, though usually with some slight modification of shape-often “ designed ” by the tuner with the aid of .a Carborundum slip! Their more common application, however, has been on gas and oil engines running at relatively slow speeds, where they work well in contact with rollers attached to the ends of the valve rockers. Cams with convex flanks are extensively used in motor cars and other mass-produced engines. One important advantage in this respect is that they are suited to manufacture in quantity by a copying process from accurately formed master cams. The fact that hat-based tappets can be used also favours quantity production and they can be designed to work fairly silently. The contour of the flank can be plotted so that violent changes in the acceleration of the cam are avoided and, more important still, the tappet will follow the cam on the return motion without any tendency to bounce or float at quite high speeds. In such cases, it may be necessary to introduce compound curves which are extremely difficult to copy on a small scale, but cams made with flanks formmg true circular arcs will give reasonably efficient results, and are very easily produced in any scale: Concave-flanked cams.
Comparatively few examples of concave-flanked cams (Fig. 2c) are to be seen nowadays, though they have been used extensively in the past with the idea of obtaining the most rapid opening and closing of the valves. Theoretically, they can be designed to produce consant-acceleration, but in practice they render valve control very difficult at high speed and their fierce angle of attack produces heavy side pressure on the tappet. The concave flank must always have a substantially greater radius than the follower, or a slapping action like that of a tangent cam on a flat follower is produced.
The shape of the nose in most types of cams is dictated mainly by the need to decelerate the follower as smoothly as possible. It is one thing to design it in such a way that ideal conditions are obtained, and quite another to ensure in practice that the follower retains close contact with the cam. If the radius of the nose is too small, the follower will bounce and come down heavily on the return flank of the cam and,. if too great, valve opening efficiency will be reduced.
Of the three types of cams, A, B and C, which all have identically equal lift and angular period, the lobe of B encloses the smallest area, and on first sight it might appear that it is the least efficient in producing adequate valve opening, or mean lift area, but owing to the use of a flat based tappet, its lift characteristics are not very different from those of a tangent cam with round-based tappet, and not necessarily inferior to those of a concave-flank cam.
Unsymmetrical cams
It is not common to make the two flanks of a cam of different contours to produce some particular result which the designer may consider desirable. In some cases, the object is to produce rapid opening and gradual closing, but sometimes the opposite effect is preferred. When all things are considered, however, most attempts to monkey about with cam forms lead to complications which may actually defeat their own object, at least at really high speeds.
In many engines, particularly those of motorcycles, the cams operate the valves through levers or rockers which move in an arc instead of in a straight line, as in the orthodox motor car tappet. This may be mechanically efficient, but it modifies the lift characteristic of the cam, as the point at which the latter transmits motion to the follower varies in relation to the radius of the lever arm, (Fig. 3).
With the cam rotating in a clockwise direction, the effective length of the lever will be greater in the position.
A during valve opening than in position B during closing, as indicated by dimensions X and Y. This amounts to the same as using an unsymmetrical cam, and in the example shown, would result in slow opening and rapid closing of the valve, or vice versa if either the direction of rotation of the cam, or the relative “ hand ” of the lever, is reversed. The shorter the lever, the greater the discrepancy in the rate of movement, Neither the unsymmetrical cam form nor the pivoted lever is condemned as bad design, but I have sought to avoid them in most of the engines I have designed because they are a complicating factor in what is already a very involved problem, and by keeping to fairly simple cams and straight-line tappets, one can be assured that there are not too many snags.
The employment of cams with flanks of true circular arc has enabled me to devise means of producing them on the lathe without elaborate attachments and, what is more important still, to produce an entire set of cams for a multi-cylinder engine in correct angular relation to each other by equally simple means. There is no doubt whatever that these methods have enabled many engine constructors (some without previous experience) to tackle successfully a problem which would otherwise have been formidable, to say the least.
Many designers have attempted to improve valve efficiency by designing cams which hold the valve at maximum opening for as long a period as possible. This is done by providing dwell or, in other words, making the top of the lobe concentric with the cam axis over a certain angular distance in the centre of its lift. To do this, however, it is necessary to make the flanks excessively steep, thus producing heavy side thrust on the tappet, and making control at high speed more difficult, (Fig. 4A).
A little consideration, however, will show that the same result can be achieved, with much less mechanical difficulty, by lifting the valve somewhat higher at an easier rate, as shown at B. This avoids the need for sudden acceleration and deceleration of the tappet and promotes flow efficiency of the valve. The shaded portions of the two cams show the differences in the area of the lobe, showing that nothing is really gained by the dwell. Factors in efficiency High valve lift is a desirable feature, but only if it can be obtained without making extra dificulties in controlling the valve. The maximum port area of a valve is obtained when the lift is equal to one-fourth of the seat diameter, but owing to the baffling effect on the valve head, a higher lift is better for flow efficiency-if it is practicable.
Large diameter valves will obviously release and admit gas efficiently but they are more difficult to control and keep cool at high speed than smaller valves. Another point is that the exhaust valve is required to open against a high cylinder pressure, and the larger it is the more the load imposed on the cam, quite apart from the spring load.
凸輪設(shè)計(jì)的基本內(nèi)容
如何為汽油發(fā)動(dòng)機(jī)和其他機(jī)械設(shè)計(jì)和生產(chǎn)簡(jiǎn)單而有效的凸輪
凸輪是被應(yīng)用的最廣泛的機(jī)械結(jié)構(gòu)之一。凸輪是一種僅僅有兩個(gè)組件構(gòu)成的設(shè)備。主動(dòng)件本身就是凸輪，而輸出件被稱為從動(dòng)件。通過使用凸輪，一個(gè)簡(jiǎn)單的輸入動(dòng)作可以被修改成幾乎可以想像得到的任何輸出運(yùn)動(dòng)。常見的一些關(guān)于凸輪應(yīng)用的例子有：
——凸輪軸和汽車發(fā)動(dòng)機(jī)工程的裝配
——專用機(jī)床
——自動(dòng)電唱機(jī)
——印刷機(jī)
——自動(dòng)的洗衣機(jī)
——自動(dòng)的洗碗機(jī)
高速凸輪(凸輪超過1000 rpm的速度)的輪廓必須從數(shù)學(xué)意義上來定義。無論如何，大多數(shù)凸輪以低速(少于500 rpm)運(yùn)行而中速的凸輪可以通過一個(gè)大比例的圖形表示出來。一般說來，凸輪的速度和輸出負(fù)載越大，凸輪的輪廓在被床上被加工時(shí)就一定要更加精密。
在多種機(jī)械裝置的操作中凸輪在某種形式下是必不可少。他們最有名的應(yīng)用是在內(nèi)燃機(jī)閥門操作裝置中，但在工業(yè)機(jī)器中，從印刷機(jī)到收割機(jī)械，凸輪機(jī)構(gòu)也是一個(gè)相當(dāng)重要的一部分。
一般來說，一個(gè)凸輪可以被定義為一個(gè)圓盤面或一個(gè)為產(chǎn)生接觸間歇往復(fù)運(yùn)動(dòng)的零件或從動(dòng)件。大多數(shù)凸輪的運(yùn)動(dòng)是旋轉(zhuǎn)運(yùn)動(dòng)，但這不是一個(gè)必要條件，在特殊情況下，它的運(yùn)動(dòng)是半旋轉(zhuǎn)，振動(dòng)或擺動(dòng)。即使原動(dòng)件可能是直線運(yùn)動(dòng)，但在某種情況下凸輪也可能會(huì)適當(dāng)?shù)乇豢紤]，。
在機(jī)構(gòu)學(xué)大多數(shù)文本書籍中給了關(guān)于凸輪設(shè)計(jì)和凸輪類型的實(shí)例設(shè)計(jì)的一些信息，產(chǎn)生各種規(guī)定的運(yùn)動(dòng)。在某種情況運(yùn)行速度和機(jī)械的性能不是非常高，有一個(gè)規(guī)律是凸輪機(jī)構(gòu)設(shè)計(jì)很好的協(xié)議，只需要避免過于陡峭的輪廓或從動(dòng)件產(chǎn)生噪聲，影響沖擊，并側(cè)壓力的突然改變。
然而，凸輪速度或負(fù)荷增加或具有更嚴(yán)格的要求，尋求更精細(xì)的設(shè)計(jì)，并以極高的速度，在慣性運(yùn)動(dòng)部件上的作用最明顯，因此，對(duì)舉升的加速度和速度因素都必須考慮，這些很少在任何詳細(xì)的標(biāo)準(zhǔn)教科書中得到處理。
凸輪從動(dòng)件的設(shè)計(jì)也是非常重要的，并且關(guān)系到凸輪自身的形狀。這是因?yàn)橥馆喤c從動(dòng)件不能在一個(gè)固定點(diǎn)上接觸。表面接觸需要分配負(fù)荷，避免過度磨損，凸輪傳送運(yùn)動(dòng)通過從動(dòng)件各點(diǎn)位置，這都取決于兩個(gè)互補(bǔ)零部件形狀。目前凸輪在發(fā)動(dòng)機(jī)氣門設(shè)計(jì)的問題上特別困難。在賽車引擎中，無論是負(fù)載還是速度都可能會(huì)被視為極端，因?yàn)樵诤芏喟l(fā)動(dòng)機(jī)中引擎的閥門上這些限制因素得不到有效控制。在某些方面，微型發(fā)動(dòng)機(jī)凸輪的設(shè)計(jì)的簡(jiǎn)化是由于他們的打火工作部件（以及隨之而來的慣量）的原因，但在另一方面，工作通常具有更大的摩擦和旋轉(zhuǎn)速度，一般都大大高于全尺寸的做法更高。
對(duì)于小型四沖程發(fā)動(dòng)機(jī)的許多設(shè)計(jì)已經(jīng)出版，我力求簡(jiǎn)化操作閥門，并為凸輪可以簡(jiǎn)單而準(zhǔn)確地運(yùn)用在業(yè)余設(shè)計(jì)制作車間的設(shè)施。許多發(fā)動(dòng)機(jī)的設(shè)計(jì)已提交，讀者對(duì)設(shè)計(jì)中包含有錯(cuò)誤的閥門裝置，特別是凸輪和這些項(xiàng)目上的基本原則有普遍的誤解，我給一些對(duì)此事的意見，而我的信任將有助于個(gè)別設(shè)計(jì)人員獲得其發(fā)動(dòng)機(jī)的最佳效果。
目前有許多關(guān)于發(fā)動(dòng)機(jī)的凸輪設(shè)計(jì)，盡管如此，這些設(shè)計(jì)結(jié)果或多或少令它們不滿意?？梢哉f，它的速度在一定限度內(nèi)可以滿足要求，但在某些情況下，凸輪設(shè)計(jì)不良可以與發(fā)動(dòng)機(jī)配合，但在工作細(xì)節(jié)上會(huì)出現(xiàn)錯(cuò)誤??。
本文關(guān)注的主要是集成電路的閥門發(fā)動(dòng)機(jī)凸輪設(shè)計(jì)，并且為了避免一些混淆的術(shù)語，圖1顯示了這種類型的凸輪的各個(gè)部分，并解釋它們的功能。凸輪輪廓的同心部分，它沒有操作效果，被稱為基圓；凸輪（顯示陰影）被稱為葉輪，無論是從基圓上升到頂圓，這通常是圓形的側(cè)翼。
推程可以被定義為基圓半徑和頂圓之間的差值。點(diǎn)之間的封閉在兩側(cè)加入基圓的角被稱為周期，代表整個(gè)周期運(yùn)作期間，凸輪齒輪比例閥。
在圖2中，對(duì)用于i.c.發(fā)動(dòng)機(jī)凸輪典型例子進(jìn)行了說明。切線凸輪，一個(gè)已經(jīng)固定在直線兩側(cè)，其中顧名思義形式向基圓的切線。這種凸輪式很容易設(shè)計(jì)和生產(chǎn)，是由一個(gè)圓形銑加工過程形成了一個(gè)最簡(jiǎn)單的方法，它是在表面與基圓同心連續(xù)運(yùn)行了切向那里的兩翼開始和結(jié)束。它也可以產(chǎn)生和我在過去的描述如何與一個(gè)在軋輥車床休息備案，它借助與索引齒輪側(cè)面結(jié)合的角度來定位。
切線凸輪的有效工作只能和一個(gè)凸弧形上的從動(dòng)件一起，因?yàn)檫@是唯一的方式，側(cè)面可以發(fā)揮作用，逐步平穩(wěn)。前一段時(shí)間有一種引擎與切線凸輪一起被描述。這是不適合極高的速度的，極有可能產(chǎn)生力的集中現(xiàn)象，但相當(dāng)清楚的是，它是切線凸輪的盤型平面。平面上推桿以上的側(cè)翼突然變長(zhǎng)，運(yùn)動(dòng)中突然出現(xiàn)運(yùn)動(dòng)噪音，效率低，從長(zhǎng)遠(yuǎn)來看具有破壞性。
滾子經(jīng)常被用來作為與切線凸輪的從動(dòng)件，并在其形狀方面令人滿意，但在這一點(diǎn)上引入滾動(dòng)運(yùn)動(dòng)的想法并不好??，因?yàn)樗坪跏且幌嗲樵福驗(yàn)樗皇寝D(zhuǎn)移的滑動(dòng)摩擦要小得多，即樞軸銷。然而，在某些情況下，有可能要使用一個(gè)球或滾子的比賽，對(duì)于這一點(diǎn)，無論如何，具有分布和均衡的磨損表面的優(yōu)點(diǎn)。
切線凸輪已經(jīng)使用于高性能型發(fā)動(dòng)機(jī)的成功，在一定程度上，同一時(shí)間流行的賽車摩托車發(fā)動(dòng)機(jī)，與一些形狀往往是“設(shè)計(jì)”所具有的援助略有修改，但通常調(diào)諧器，碳化硅流失了！然而，他們更常見的應(yīng)用一直在天然氣和石油的發(fā)動(dòng)機(jī)速度相對(duì)緩慢，他們?cè)谀睦锕ぷ鹘佑|良好，附著在滾筒的兩端閥門搖動(dòng)運(yùn)行引擎。凸齒面凸輪廣泛應(yīng)用于汽車及其他大眾生產(chǎn)的發(fā)動(dòng)機(jī)。在這方面的一個(gè)重要優(yōu)勢(shì)是，它們適合于制造一個(gè)復(fù)制過程中形成的準(zhǔn)確數(shù)量從主凸輪。在這頂帽子的挺桿可以使用的事實(shí)也有利于批量生產(chǎn)，他們可以設(shè)計(jì)相當(dāng)默默工作。該側(cè)面輪廓可以繪制，使在凸輪加速度變化是避免突變，更重要的是，推桿將不能出現(xiàn)任何反彈或漂浮，在相當(dāng)高的速度出現(xiàn)回復(fù)運(yùn)動(dòng)。在這種情況下，可能有必要引入一個(gè)小規(guī)模的復(fù)合曲線，但凸輪與兩翼圓弧會(huì)作出合理有效的結(jié)合，并且在任何規(guī)模很容易的產(chǎn)生凹陷。兩側(cè)凸輪的例子現(xiàn)在是比較少看到的，雖然他們已經(jīng)在過去廣泛地使用，獲取最快速的開啟和關(guān)閉的閥門的方法。理論上，他們可以被用來產(chǎn)生永久的加速，但在實(shí)踐中非常高的速度和激烈的攻角時(shí)，閥門控制產(chǎn)生的側(cè)壓力使沉重挺桿困難。凹側(cè)面必須始終比從動(dòng)件半徑更大，或者一個(gè)平面從動(dòng)件切線凸輪產(chǎn)生左右運(yùn)動(dòng)。
??大多數(shù)類型的凸輪，形狀主要是出于減速所需要的，盡可能的作平緩運(yùn)動(dòng)。這種設(shè)計(jì)方式可以認(rèn)為理想的條件，在實(shí)踐中又是另一回事確保從動(dòng)件保持密切與凸輪接觸。如果凸起半徑過小，從動(dòng)件將會(huì)在凸輪側(cè)翼反彈和回落。如果過大，閥門開關(guān)效率會(huì)降低。
對(duì)凸輪的三種類型，A，B和C都具有相同的舉升和角度區(qū)間，B葉包圍面積最小，乍一看，它是可能出現(xiàn)的，它在產(chǎn)生足夠的閥門打開效率最低或平均升力面積，但是由于有挺桿的使用，其舉升特性并不十分明顯，不同于基圓的切線凸輪的挺桿，并不見得遜色于凹凸輪的側(cè)面。
非對(duì)稱凸輪
這是一種不常見的凸輪，利用不同的輪廓在凸輪兩側(cè)產(chǎn)生某種特定結(jié)果，這種考慮，設(shè)計(jì)者是可取的。在某些情況下，該對(duì)象產(chǎn)生迅速開放和逐步縮小現(xiàn)象，但有時(shí)相反的效果卻為最佳。然而，當(dāng)所有的因素都考慮在內(nèi)，大多數(shù)試圖與運(yùn)動(dòng)有關(guān)凸輪形式會(huì)引起并發(fā)癥，實(shí)際上可能失敗，至少在非常高的速度。
在很多引擎中，特別是摩托車，凸輪通過杠桿或在一個(gè)搖滾的操作，用一條直線代替圓弧運(yùn)動(dòng)，如正統(tǒng)汽車挺桿。這可能是改善機(jī)械效率，但它修改了凸輪的升降特征，當(dāng)在某點(diǎn)上，后者傳遞運(yùn)動(dòng)給從動(dòng)件和杠桿臂的半徑有關(guān)，（圖3）不同的凸輪升程的特性。隨著凸輪順時(shí)針方向旋轉(zhuǎn)，杠桿的有效長(zhǎng)度將會(huì)更大。
A位置開啟和B位置關(guān)閉閥門，用X和Y的尺寸來表示。與使用非對(duì)稱凸輪是相對(duì)等的，如這個(gè)例子所示，會(huì)產(chǎn)生緩慢開啟和迅速關(guān)閉的閥門的情況，或者相反，如果不論是凸輪的旋轉(zhuǎn)方向，或相同于“手”的杠桿的方向?qū)?huì)產(chǎn)生相反的效果。桿越短，運(yùn)動(dòng)速率的差異就越大，無論是凸輪機(jī)構(gòu)的形式還是非對(duì)稱凸輪樞軸桿不好的設(shè)計(jì)，但我一直在努力避免在我所設(shè)計(jì)的引擎產(chǎn)生這種情況，因?yàn)樗麄兪且粋€(gè)非常復(fù)雜的問題，并保持相對(duì)簡(jiǎn)單的凸輪和直線挺桿因素，人們可以放心，不會(huì)有太多的障礙。
對(duì)于具有圓弧面的凸輪的運(yùn)用，使沒有詳細(xì)說明的情況下，車床生產(chǎn)它們的手段和方法，更重要的是，用正確的關(guān)系來生產(chǎn)多汽缸引擎的關(guān)系具有同樣簡(jiǎn)單的方式。這些方法已使許多發(fā)動(dòng)機(jī)構(gòu)造（不含以前的一些經(jīng)驗(yàn)）成功地解決一個(gè)疑問，至少可以這樣說。
很多設(shè)計(jì)師都試圖改善凸輪的設(shè)計(jì)，以最大時(shí)間來提高閥門的工作效率。換句話說，使得耳垂超過一定在其升力中心的角距離凸輪軸同心的頂部。但是要做到這一點(diǎn)，有必要作出過度陡峭的側(cè)面，從而產(chǎn)生大量的挺桿側(cè)向推力，在高轉(zhuǎn)速時(shí)，使控制更加困難。
然而幾乎沒有考慮，同樣的結(jié)果表明，這種方法是可以實(shí)現(xiàn)的，出現(xiàn)很少的機(jī)械問題，解除閥也更容易效率也更高，如B所示。這避免了推桿突然加速和減速，并促進(jìn)流動(dòng)閥門的工作效率。兩個(gè)凸輪的陰影部分顯示了葉面積的差異，顯示出真正的高效性。只有在不進(jìn)行額外的控制時(shí)，氣門的高效升程是非常理想的，閥門的最大開口區(qū)，等于閥座直徑的四分之一，但是由于對(duì)閥頭莫名其妙的影響，如果它是可行的，較高的升程流動(dòng)效率將會(huì)更好。
大口徑閥門能夠很明顯釋放和有效得承載，在高速運(yùn)動(dòng)下比小閥門更難控制但他們更難以控制。另一點(diǎn)是，排氣閥對(duì)高壓缸做出反抗，凸輪上的外加荷載越大反抗就越大，完全不同于彈簧負(fù)載。
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