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汽车变速箱三维设计与仿真

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【摘要】

　　　变速器用来改变发动机传到驱动轮上的转矩和转速，目的是在原地起步，爬坡，转弯，加速等各种行驶工况下，使汽车获得不同的牵引力和速度，同时使发动机在最有利工况范围内工作。变速器设有空挡和倒挡。需要时变速器还有动力输出功能。

　　　因为变速箱在低档工作时作用有较大的力，所以一般变速箱的低档都布置靠近轴的后支承处，然后按照从低档到高档顺序布置各档位齿轮。这样做既能使轴有足够大的刚性，又能保证装配容易。变速箱整体结构刚性与轴和壳体的结构有关系。一般通过控制轴的长度即控制档数，来保证变速箱有足够的刚性。

　　　本文设计研究了三轴式五挡手动变速器，对变速器的工作原理做了阐述，变速器的各挡齿轮和轴做了详细的设计计算，并进行了强度校核，对一些标准件进行了选型。变速器的传动方案设计。简单讲述了变速器中各部件材料的选择。

　　【关键词】挡数；传动比；齿数；轴

　　【Abstract】

　　　Transmission to change the engine reached on the driving wheel torque and speed, is aimed at marking start, climbing, turning, accelerate various driving conditions, the car was different traction and speed Meanwhile engine in the most favorable working conditions within the scope of the work. And the trans mission in neutral gear with reverse gear. Transmission also need power output function.

　　　Gearbox because of the low-grade work at a larger role, In general, the low-grade gearbox layout are close to the axis after support, Following from low-grade to high-grade order of the layout of stalls gear. This will not only allow axis are large enough for a rigid, but also ensures easy assembly. Gear box overall structure and rigid axle and the shell structure of relations. Generally through the control shaft length control over several stalls to ensure that adequate gear box rigid.

　　　This paper describes the design of three-axis five block manual trans mission, the transmission principle of work elaborated, Transmission of the gear shaft and do a detailed design, and the intensity of a school. For some standard parts for the selection. Transmission Trans mission program design. A brief description of the trans mission of all components of the material choice.

　　[Keywords]: block; Transmission ratio; Teeth; Axis

引言1

1 总体方案设计3

1.1 汽车参数的选择3

1．2变速器设计应满足的基本要求3

2 变速器传动机构布置方案4

2.1 传动机构布置方案分析4

2.1.1 固定轴式变速器4

2.1.2 倒挡布置方案6

2.1.3 其他问题7

3 零部件结构方案分析9

3.1 齿轮形式9

3.2 换挡机构形式9

3.3 变速器轴承11

4变速器设计和计算12

4.1 挡数12

4.2 传动比范围12

4.3 中心距A12

4.4 外形尺寸13

4.5 轴的直径13

4.6 齿轮参数13

4.6.1 模数的选取13

4.6.2 压力角14

4.6.3 螺旋角14

4.6.4 齿宽b16

4.6.5 变位系数的选择原则16

4.7 各挡齿轮齿数的分配17

4.7.1 确定一挡齿轮的齿数17

4.7.2 对中心距进行修正18

4.7.3 确定常啮合传动齿轮副的齿数18

4.7.4 确定其他各挡的齿数19

4.7.5 确定倒挡齿轮齿数20

5 变速器的校核21

5.1 齿轮的损坏形式21

5.2 齿轮强度计算21

5.2.1 齿轮弯曲强度计算21

5.2.2 轮齿接触应力计算22

6 同步器的选型24

6.1 锁销式同步器24

6.1.1 锁销式同步器结构24

6.1.2 锁销式同步器工作原理25

6.2 锁环式同步器26

6.2.1 锁环式同步器结构26

6.2.2 锁环式同步器工作原理26

6.2.3 锁环式同步器主要尺寸的确定27

7 变速器操纵机构30

7.1 直接操纵手动换挡变速器30

7.2 远距离操纵手动换挡变速器31

8 三维建模32

8.1各档位齿轮的建模32

8.2箱体和箱体上盖的建模见下图9.11和9.1237

8.3汽车变速箱整体模型和爆炸图见下图9.13和9.1438

9 变速箱的仿真40

9.1 方针的的第一步，完成三维变速箱的装配40

9.1.1新建装配环境40

9.1.2装配倒档轴组件40

9.1.3装配中间轴组件41

9.1.4装配一二轴组件41

9.1.5完成变速箱的全部装配42

9.2进行仿真42

9.2.1定义齿轮副43

9.2.2定义伺服电动机43

9.2.3机构分析43

9.3保存仿真动画43

10 结论44

致谢45

参考文献46

附录47

　　　现在汽车变速器的发展趋势是向着可调自动变速箱或无级变速器方向发展。无级变速机构由两组锥形轮组成，包括一对主动锥形轮（锥形轮组1）和一对被动锥形轮（锥形轮组2）同时有一根链条运行在两对锥形轮V形沟槽中间，链条的运动如同动力传递单元。锥形轮组1由发动机的辅助减速机构驱动，发动机的动力通过链条传递给锥形轮组2直至终端驱动。在每组锥形轮中有一个锥形轮可以在轴向移动，调整链条在锥形轮的工作直径并传递速比。两组锥形轮必须保持相同的调整，以保证链条始终处与涨紧状态，使传递扭矩时锥形轮接触充分的压力。采用无级变速器可以节约燃料，使汽车单位油耗的行驶里程提高30%。通过选择最佳传动比，获得最有利的功率输出，它的传动比比传统的变速器轻，结构更简单而紧凑。世界各大汽车制造商正竞相开发无级变速器。专家预计2003至2005年间无级变速器将成为世界各大汽车制造商的技术开发重点。目前一些著名汽车制造商（如福特、通用、本田、克莱斯勒等）正致力于无级变速器的开发工作。现在全球CVT的产量约为50万台，而普通型自动变速器的产量约为2,500万台，双向通讯和线控技术的应用，无级变速器有无比的优势，预计不久将来中国各大汽车制造商也将生产自己的CVT无级变速器，并广泛应用于国产轿车。

　　　在此次设计中对变速器作了总体设计，对变速器的传动方案进行了选择，变速器的齿轮和轴做了详细的设计计算，对同步器和一些标准件做了选型设计。

　　 1 总体方案设计

1.1 汽车参数的选择

根据变速器设计所选择的汽车基本参数如下表

表1.1 设计基本参数

Tablet 1-1 able basic design parameters

项目参数值

发动机：5.5L V12

挡数:5

最大功率(kW/n)：380/5000

最大扭矩(N·m/n)：830/1900_3500

1．2变速器设计应满足的基本要求

　对变速器如下基本要求.

　　　 1）保证汽车有必要的动力性和经济性。

　　　 2）设置空挡，用来切断发动机动力向驱动轮的传输。

　　　 3）设置倒档，使汽车能倒退行驶。

　　　 4）设置动力输出装置，需要时能进行功率输出。

　　　 5）换挡迅速，省力，方便。

　　　 6）工作可靠。汽车行驶过程中，变速器不得有跳挡，乱挡以及换挡冲击等现象发生。

　　　 7）变速器应当有高的工作效率。

　　　除此以外，变速器还应当满足轮廓尺寸和质量小，制造成本低，维修方便等要求。满足汽车有必要的动力性和经济性指标，这与变速器的档数，传动比范围和各挡传动比有关。汽车工作的道路条件越复杂，比功率越小，变速器的传动比范围越大。

QQ截图20130728194234.gif

汽车变速箱三维设计与仿真.jpg

图片11.jpg

内容简介：: An analytical design for three circular-arc camsChiara Lanni, Marco Ceccarelli*, Giorgio FiglioliniDipartimento di Meccanica, Strutture, Ambiente e Territorio, Universit? a a di Cassino, Via Di Biasio 43,03043 Cassino (Fr), ItalyReceived 10 July 2000; accepted 22 January 2002AbstractIn this paper we have presented an analytical description for three circular-arc cam profiles. An ana-lytical formulation for cam profiles has been proposed and discussed as a function of size parameters fordesign purposes. Numerical examples have been reported to prove the soundness of the analytical designprocedure and show the engineering feasibility of suitable three circular-arc cams.? 2002 Elsevier Science Ltd. All rights reserved.1. IntroductionA cam is a mechanical element, which is used to transmit a desired motion to another me-chanical element by direct surface contact.Generally, a cam is a mechanism, which is composed of three different fundamental parts froma kinematic viewpoint 1,2: a cam, which is a driving element; a follower, which is a driven el-ement and a fixed frame. Cam mechanisms are usually implemented in most modern applicationsand in particular in automatic machines and instruments, internal combustion engines andcontrol systems 3.Cam and follower mechanisms can be very cheap, and simple. They have few moving parts andcan be built with very small size.The design of cam profile has been based on simply geometric curves, 4, such as: parabolic,harmonic, cycloidal and trapezoidal curves 2,5 and their combinations 1,2,6,7.In this paper we have addressed attention to cam profiles, which are designed as a collection ofcircular arcs. Therefore they are called circular-arc cams 5,8.*Corresponding author.E-mail address: ceccarelliing.unicas.it (M. Ceccarelli).0094-114X/02/$ - see front matter ? 2002 Elsevier Science Ltd. All rights reserved.PII: S0094-114X(02)00032-0Mechanism and Machine Theory 37 (2002) 915924/locate/mechmtCircular-arc cams can be easily machined and can be used in low-speed applications 9. Inaddition, circular-arc cams could be used for micro-mechanisms and nano-mechanisms since verysmall manufacturing can be properly obtained by using elementary geometry.An undesirable characteristic of this type of cam is the sudden change in the acceleration at theprofile points where arcs of different radii are joined 5.A limited number of circular-arcs is usually advisable so that the design, construction andoperation of cam transmission can be not very complicated and they can become a compromisefor simplicity and economic characteristics that are the basic advantages of circular-arc cams 8.Recently new attention has been addressed to circular-arc cams by using descriptive viewpoint10, and for design purposes 11,12.In this paper we have described three circular-arc cams by taking into consideration the geo-metrical design parameters. An analytical formulation has been proposed for three circular-arccams as an extension of a formulation for two circular-arc cams that has been presented in aprevious paper 12.2. An analytical model for three circular-arc camsAn analytical formulation can be proposed for three circular-arc cams in agreement with designparameters of the model shown in Figs. 1 and 2.Significant parameters for a mechanical design of a three circular-arc cam are: Fig. 1 8; the riseangle as, the dwell angle ar, the return angle ad, the action angle aa as ar ad, the maximumlift h1.Fig. 1. Design parameters for general three circular-arc cams.916C. Lanni et al. / Mechanism and Machine Theory 37 (2002) 915924The characteristic loci of a three circular-arc cams are shown in Fig. 2 as: the first circle C1ofthe cam profile with q1radius and centre C1; the second circle C2of the cam profile with q2radiusand centre C2; the third circle C3of the cam profile with q3radius and centre C3; the base circle C4with radius r and the centre is O; the lift circle C5of the cam profile with (r h1) radius and centreO; the roller circle with radius q centred on the follower axis. In addition significant points are:D ? xD;yD which is the point joining C1with C5; F ? xF;yF which is the point joining C1withC3; G ? xG;yG which is the point joining C3with C2; A ? xA;yA) which is the point joining C2with C4. x and y are Cartesian co-ordinates of points with respect to the fixed frame OXY, whoseorigin O is a point of the cam rotation axis. Additional significant loci are: t13which is the co-incident tangential vector between C1and C3; t15which is the coincident tangential vector betweenC1and C5; t23which is the coincident tangential vector between C2and C3; t24which is the co-incident tangential vector between C2and C4.The model shown in Figs. 1 and 2 can be used to deduce a formulation, which can be usefulboth for characterizing and designing three circular-arc cams. Analytical description can beproposed when the circles are formulated in the suitable form: circle C1with radius q21 x1? xF2 y1? yF2passing through point F asx2 y2? 2xx1? 2yy1? x2F? y2F 2x1xF 2y1yF 01 circle C2with radius q22 x2? xA2 y2? yA2passing through point A asx2 y2? 2xx2? 2yy2? x2A? y2A 2x2xA 2y2yA 02 circle C2with radius q22 x2? xG2 y2? yG2passing through point G asx2 y2? 2xx2? 2yy2? x2G? y2G 2x2xG 2y2yG 03Fig. 2. Characteristic loci for three circular-arc cams.C. Lanni et al. / Mechanism and Machine Theory 37 (2002) 915924917 circle C3with radius q23 x3? xF2 y3? yF2passing through point F asx2 y2? 2xx3? 2yy3? x2F? y2F 2x3xF 2y3yF 04 circle C3with radius q23 x3? xG2 y3? yG2passing through point G asx2 y2? 2xx3? 2yy3? x2G? y2G 2x3xG 2y3yG 05 circle C4with radius r asx2 y2 r26 circle C5with radius (r h1) asx2 y2 r h127Additional characteristic conditions can be expressed in the form as thefirstcircleC1andliftcircleC5musthavethesametangentialvectort15atpointDexpressedasxx1 yy1? x1xD? y1yD 08 the base circle C4and second circle C2must have the same tangential vector t24at point A ex-pressed asxx2 yy2? x2xA? y2yA 09 the second circle C2and third circle C3must have the same tangential vector t23at point G ex-pressed asxx3? x2 yy3? y2 x3xG y3yG? x1xG? y1yG 010 the first circle C1and the second circle C2must have the same tangential vector t12at point Fexpressed asxx1? x3 yy1? y3 x3xF y3yF? x1xF? y1yF 011Eqs. (1)(11) may describe a general model for three circular-arc cams and can be used to drawthe mechanical design as shown in Fig. 2.3. An analytical design procedureEqs. (1)(11) can be used to deduce a suitable system of equations, which allows solving the co-ordinates of the points C1, C2, C3, F and G when suitable data are assumed.It is possible to distinguish four different design cases by using the proposed analytical de-scription.In a first case we can consider that the numeric value of the parameters h1, r, as, ar, ad, q1, q2,and co-ordinates of the points A, C1, C2, D and G are given, and the co-ordinates of points C3, Fare the unknowns. When the action angle aais equal to 180?, the co-ordinate xAof point A is equalto zero. Since A is the point joining C2and C4then the centre C2of the second circle C2lies on theY axis and therefore the co-ordinate x2of the centre C2is equal to zero. By using Eqs. (1)(11) it is918C. Lanni et al. / Mechanism and Machine Theory 37 (2002) 915924possible to deduce a suitable system of equations which allows to solve the co-ordinates of thepoints C3and F. Analytical formulation can be expressed by means of the following conditions: the first circle C1passing across points F and D in the formxF? x12 yF? y12 xD? x12 yD? y1212 the third circle C3passing across points F and G in the formxF? x32 yF? y32 xG? x32 yG? y3213 coincident tangents to C1and C3at the point F in the formx3? x1y3? y1xF? x3yF? y314 coincident tangents to C2and C3at the point G in the formx2? x3y2? y3xG? x2yG? y215When x2 xA 0 are assumed, Eqs. (12)(15) can be expressed asx2F y2F? 2x1xF? 2y1yF? x2D? y2D 2x1xD 2y1yD 0x2F y2F? 2x3xF? 2y3yF? x2G? y2G 2x3xG 2y3yG 0xF? x3y3? y1 ? x3? x1yF? y3 0xGy2? y3 ? x3yG? y2 016If the position of the centre C2is unknown and the direction of the centre C1lies on the ODstraight line, we can approach referring to Fig. 2 a second problem: namely the value of theparameters h1, r, as, ar, ad, q1, and the co-ordinates of the points C2, A, D and G are known andthe co-ordinates of the points C1, F and C3are unknown. Again we may assume aa 180? andconsequently xA x2 0. Two additional conditions are necessary to have a solvable systemtogether with Eq. (9). They are the second circle C2passing across points G and A in the formxG? x22 yG? y22 xA? x22 yA? y2217 straight-line containing points O, A and C2in the formx2yA? xAy2 018Thus, the second case can be solved by Eqs. (16)(18).If the position of the centre C1is unknown but we know that it lies on the OD straight line, wecan approach a third design problem: namely the value of the parameters h1, r, as, ar, ad, q1, andthe co-ordinates of the points A, D and G are known and the co-ordinates of the points C1, C2, Fand C3are unknown. Again we may assume aa 180? and consequently xA x2 0. Two ad-ditional conditions are necessary to have a solvable system together with Eqs. (16)(18). They areC. Lanni et al. / Mechanism and Machine Theory 37 (2002) 915924919 the first circle C1passing across point D in the formxD? x12 yD? y12 q2119 straight-line containing points O, D and C1in the formxDy1? x1yD 020Finally we may approach the fourth case when aa 180? and xA6 0 and also x26 0. Referringto Fig. 1, in which aais the angle between the general position of the point A and the Y axis, thevalue of the parameters h1, r, as, ar, ad, q1, and the co-ordinates of the points A, D and G areknown and the co-ordinates of the points C1, C2, C3and F are unknown. The fourth of Eq. (16)can be expressed asx2? x3yG? y2 ? y2? y3xG? x2 021Thus, the general design case can be solved by using Eqs. (12)(14) and Eqs. (17)(21).A design procedure can be obtained by using the above-mentioned formulation in order tocompute the design parameters. In particular, the proposed formulation has been useful for adesign procedure which makes use of MAPLE to solve for the design unknowns.4. Numerical examplesSeveral numeric examples have been successfully computed in order to prove the soundness andnumerical efficiency of the proposed design formulation. It has been found that only one solutioncan represent a significant circular-arc cam design for any of the formulated design cases.In the Example 1 of Fig. 3 referring to the first design case, the data are given as h1 15 mm,r 40 mm, ar 40?, as ad 70?, q1 17 mm, A ? 0;40 mm, D ? 51:68 mm; 18:81 mmC1? 35:71 mm; 13:00 mm, C2? 0 mm; ?75:64 mm and G ? 22:24 mm; 37:84 mm. Fig.3 shows results for the design case, which has been formulated by Eq. (16). In particular, Fig. 3(a)shows the first solution of the analytical formulation. We can note that points F, C1and C3arealigned in the order F, C1and C3and points G, C3and C2in the order G, C3and C2respectively tothe first and second arcs cam profile. Fig. 3(b) shows the second solution of the analytical for-mulation. A cam profile cannot be identified since F point does not lie also on circle C1. Significantpoints F, C1and C3are aligned in the same order with respect to the case in Fig. 3(a); points G, C2and C3are aligned in the C2, G and C3sequential order which is different respect to the case in Fig.3(a) and do not give a cam profile. Fig. 3(c) shows the third solution of analytical formulation thatis similar to the case of Fig. 3(b). Fig. 3(d) shows the fourth solution of analytical formulation. Wecan note that in correspondence of point D there is a cusp. In addition, points F and G are verynear to centre C3so that a sudden change of curvature is obtained in the cam profile as shown inFig. 3(d). Thus a practical feasible design is represented only by Fig. 3(a) that can be characterisedby the proper order F, C1and C3and G, C3and C2of the meaningful points.The feasible numerical solution in Fig. 3(a) is characterised by the values: xF 46:78 mm,yF 25:91 mm, x3 11:99 mm, y3 ?14:47 mm.920C. Lanni et al. / Mechanism and Machine Theory 37 (2002) 915924In the Example 2 of Fig. 3 the data are given as h1 15 mm, r 40 mm, ar 40?,as ad 70?, q1 17 mm, A ? 0; 40 mm, D ? 51:68 mm; 18:81 mm, C1? 35:71 mm;13:00 mm and G ? 22:24 mm; 37:84 mm.In this case Fig. 3 represents also the design solution which has been obtained by using Eqs.(16)(18) for the second design case.The feasible numerical solution is characterised by the values: xF 46:78 mm, yF 25:91 mm,x3 11:99 mm, y3 ?14:47 mm, x2 0 mm, y2 ?75:64 mm.In the Example 3 of Fig. 4 referring to the third design case the data are given as h1 15 mm,r 40 mm, ar 40?, as ad 70?, q1 17 mm, A ? 0; 40 mm, D ? 51:68 mm; 18:81 mmand G ? 22:24 mm; 37.84 mm).Fig. 4 shows results for the design case, which has been formulated by Eqs. (16)(20). Fig. 4(a)shows the first solution of analytical formulation. This case is similar to the solution representedin Fig. 3(d). Fig. 4(b) shows the second solution of analytical formulation. We can note that pointF is located below point D so that points F, C1and C3are not aligned. Fig. 3(c) shows the thirdFig. 3. Examples 1 and 2: graphical representation of design solutions for Eq. (16) and design solutions for Eqs. (16)(18). Only case (a) is a practical feasible design.C. Lanni et al. / Mechanism and Machine Theory 37 (2002) 915924921solution of analytical formulation, which is the same of the case reported in Fig. 3(a). Thus apractical feasible design is represented only by Fig. 4(c).The feasible numerical solution is characterised by the values: xF 46:78 mm, yF 25:91 mm,x3 11:99 mm, y3 ?14:47 mm, x2 0 mm, y2 ?75:64 mm, x1 35:71 mm, y1 13:00 mm.In the Example 4 of Fig. 5 referring to the fourth design case, the data are given as h1 15 mm,r 40 mm, ar 40?, as ad 70?, q1 17 mm, A ? 3:48 mm; 39.84 mm), D ? 51:68 mm;18.81 mm) and G ? 22:24 mm; 37.84 mm).Fig. 5 shows results for the design case, which has been formulated by Eqs. (16)(21). Fig. 5(a)shows the first solution of the analytical formulation. This design is similar to the case reported inFig. 4(a), but the location of point C1is different. Points F, C1and C3are aligned in the C3, F andC1order. Fig. 5(b) shows the second solution of analytical formulation, which is similar to thecase in Fig. 4(a). Fig. 5(c) shows the third solution of analytical formulation. This case shows aFig. 4. Example 3: graphical representation of design solutions for Eqs. (16)(20). Only case (c) is a practical feasibledesign.922C. Lanni et al. / Mechanism and Machine Theory 37 (2002) 915924solution, which is similar to the case reported in Fig. 4(c). Thus a practical feasible design isrepresented only by Fig. 5(c).The feasible numerical solution is characterised by the values: xF 48:15 mm, yF 24:58 mm,x3 16:92 mm, y3 ?4:50 mm, x2 ?40:01 mm, y2 ?457:26 mm, x1 35:71 mm, y1 13:00mm.5. ApplicationsA novel interest can be addressed to approximate design of cam profiles for both new designpurposes and manufacturing needs.Analytical design formulation is required to obtain efficient design algorithms. In addition,closed-form formulation can be also useful to characterise cam profiles in both analysis proce-dures and synthesis criteria. The approximated profiles with circular-arcs can be of particularinterest also to obtain analytical expressions for kinematic characteristics of any profiles that canbe approximated by segments of proper circular arcs.Fig. 5. Example 4: graphical representation of design solutions for Eqs. (16)(21). Only case (c) is a practical feasibledesign.C. Lanni et al. / Mechanism and Machine Theory 37 (2002) 915924923Indeed, the circular-arc cam profiles have become of current interest because of applications inmini-mechanisms and micro-mechanisms. In fact, when the size of a mechanical design is reducedto the scale of millimeters (mini-mechanisms) and even micron (micro-mechanisms) the manu-facturing of polynomial cam profile becomes difficult and even more complicated is a way toverify it. Therefore, it can be convenient to design circular-arc cam profiles that can be also easilytested experimentally.In addition, stronger and stronger demand of low-cost automation is giving new interest toapproximate designs, which can be used only for specific tasks. This is the case of circular-arc camprofiles that can be conveniently used in low speed machinery or in low-precision applications.6. ConclusionsIn this paper we have proposed an analytical formulation which describes the basic designcharacteristics of three circular-arc cams. A design algorithm

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