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引用

引用第4楼鱼的自行车于2007-10-31 09:56发表的“”: \n)',4mY  
努力为自己的梦想奋斗 ,大家加油

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没链接上吧

xiexie

看不到什么东西啊 )ZJvx%@i  
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(1)       The center distance separability of a pair of involute spur cylindrical gears implies that a change in center distance does not affect the     . S &op|Z)1  
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A. radii of the pitch circles     B. transmission ratio     C. working pressure angle @fL ^I& ++  
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(2)       The main failure form of the closed gear drives with soft tooth surfaces is the       . Qw5nfg3T  

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A. pitting of tooth surfaces     B. breaking of gear tooth 5jdZC(q5a  
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C. wear of tooth surfaces     D. agglutination of tooth surfaces F qKJids-  
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(3)       The tooth form factor in calculation of the bending fatigue strength of tooth root is independent of the       . P:qmg"i@3  
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A. tooth number   B. modification coefficient   C. module Nd_fjB  
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D. helix angle of helical gear g;IlS*Ld  
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(4)       The contact fatigue strength of tooth surfaces can be improved by way of     . g|=_@ pL  
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A. adding module with not changing the diameter of reference circle W+XWS ,(  
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B. increasing the diameter of reference circle <Ox[![SR
 
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C. adding tooth number with not changing the diameter of reference circle .J#'k+>  
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D. decreasing the diameter of reference circle &[.5@sv  
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(5)       In design of cylindrical gear drives, b1 = b2 +(5~10)mm is recommended on purpose to       . (Where b1, b2 are the face widths of tooth of the smaller gear and the large gear respectively.) h\m35'v!  

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A. equalize strengths of the two gears         B. smooth the gear drive TFVQfj$r  
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C. improve the contact strength of the smaller gear ~PQ.l\C  
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D. compensate possible mounting error and ensure the length of contact line WxdQ^#AE  
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(6)       For a pair of involute spur cylindrical gears, if z1 < z2 , b1 > b2 , then     . St=nf\P&F  
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A.     B.     C.     D. !+
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(7)       In a worm gear drive, the helix directions of the teeth of worm and worm gear are     the same. ia6 jiW x  
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A. certainly       B. not always       C. certainly not .^YxhUH,G  
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(8)       Because of       , the general worm gear drives are not suitable for large power transmission. npP C;KD  
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A. the larger transmission ratios   B. the lower efficiency and the greater friction loss _ %s#Cb  
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C. the lower strength of worm gear   D. the slower rotating velocity of worm gear *k$[/{S1-  
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(9)       In a belt drive, if v1, v2 are the pitch circle velocities of the driving pulley and the driven pulley respectively, v is the belt velocity, then       . jzvK;*N  
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A.   B.   C.   D. rOIb9:  
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(10)   In a belt drive, if the smaller sheave is a driver, then the maximum stress of belt is located at the position of going     . j*=!M# D  
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A. into the driving sheave       B. into the driven sheave gqaM<!]  
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C. out of the driving sheave       D. out of the driven sheave GT>'|~e  
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(11)   In a V-belt drive, if the wedge angle of V-belt is 40°，then the groove angle of V-belt sheaves should be     40°. .5JIQWE(  
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A. greater than     B. equal to     C. less than     D. not less than $`pf!b2Z  
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(12)   When the centerline of the two sheaves for a belt drive is horizontal, in order to increase the loading capacity, the preferred arrangement is with the       on top. ulR yt^bx|  
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A. slack side   B. tight side VPN 9 Ql=  
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(13)   In order to     , the larger sprocket should normally have no more than 120 teeth. K'OG-fn;  
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A. reduce moving nonuniformity of a chain drive j/v>,MM  
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B. ensure the strength of the sprocket teeth     C. limit the transmission ratio 'r' =%u$1C  
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D. reduce the possibility that the chain falls off from the sprockets due to wear out of the =lNW1J\SW  
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(14)   In order to reduce velocity nonuniformity of a chain drive, we should take       . ,#a4P`q'iC  
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A. the less z1 and the larger p     B. the more z1 and the larger p H UJqB0D ?  
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C. the less z1 and the smaller p     D. the more z1 and the smaller p QW..=}pL  
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(Where z1 is the tooth number of the smaller sprocket, p is the chain pitch) =i~ = |K!  
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(15)   In design of a chain drive, the pitch number of the chain should be     . J~x]~}V&  
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A. even number   B. odd number   C. prime number /
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D. integral multiple of the tooth number of the smaller sprocket _ $PeFE2  
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2. (6 points) Shown in the figure is the simplified fatigue limit stress diagram of an element. hC-uz _/3  
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If the maximum working stress of the element is 180MPa, the minimum working stress is -80MPa. Find the angle q between the abscissa and the line connecting the working stress point to the origin. N\|B06X  
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3. (9 points) Shown in the figure is the translating follower velocity curve of a plate cam mechanism. o.$48h (  
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(1)   Draw acceleration curve of the follower schematically. #h ud_  
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(2)   Indicate the positions where the impulses exist, and determine the types of the impulses (rigid impulse or soft impulse). %g*nd#wG  
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(3)   For the position F, determine whether the inertia force exists on the follower and whether the impulse exists. fe\'N4  
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4. (8 points) Shown in the figure is a pair of external spur involute gears. ~#EXb?#uS  
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  The driving gear 1 rotates clockwise with angular velocity while the driven gear 2 rotates counterclockwise with angular velocity . , are the radii of the base circles. , are the radii of the addendum circles. , are the radii of the pitch circles. Label the theoretical line of action , the actual line of action , the working pressure angle and the pressure angles on the addendum circles , . K[SzE{5=P  
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5. (10 points) For the elastic sliding and the slipping of belt drives, state briefly: -vT$UP  
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(1)   the causes of producing the elastic sliding and the slipping. i(u zb<  
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(2)   influence of the elastic sliding and the slipping on belt drives. ,g P;XRe1  
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(3)   Can the elastic sliding and the slipping be avoided? Why? HDo=WqG  

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6. (10 points) A transmission system is as shown in the figure. h:+>=~\  
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The links 1, 5 are worms. The links 2, 6 are worm gears. The links 3, 4 are helical gears. The links 7, 8 are bevel gears. The worm 1 is a driver. The rotation direction of the bevel gear 8 is as shown in the figure. The directions of the two axial forces acting on each middle axis are opposite. ]HP  
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(1)   Label the rotating direction of the worm 1. iyhB;s5Rgw  
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(2)   Label the helix directions of the teeth of the helical gears 3, 4 and the worm gears 2, 6. 'x10\Q65[  
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7. (12 points) A planar cam-linkage mechanism is as shown in the figure with the working resistant force Q acting on the slider 4. @,sg^KB  
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  The magnitude of friction angle j (corresponding to the sliding pair and the higher pair) and the dashed friction circles (corresponding to all the revolute pairs) are as shown in the figure. The eccentric cam 1 is a driver and rotates clockwise. The masses of all the links are neglected. 1}!f.cWV(  
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(1)   Label the action lines of the resultant forces of all the pairs for the position shown. $0K9OF9$
 
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(2)   Label the rotation angle d of the cam 1 during which the point C moves from its highest position to the position shown in the figure. Give the graphing steps and all the graphical lines. /gHRJ$2|Sx  
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8. (15 points) In the gear-linkage mechanism shown in the figure, the link 1 is a driver and rotates clockwise; the gear 4 is an output link. Q.6pmaXrb  
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(1)   Calculate the DOF of the mechanism and give the detailed calculating process. K#F~$k|
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(2)   List the calculating expressions for finding the angular velocity ratios and for the position shown, using the method of instant centers. Determine the rotating directions of and . fX} dh 9  
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(3)   Replace the higher pair with lower pairs for the position shown. tp*AA@~  
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(4)   Disconnect the Assur groups from the mechanism and draw up their outlines. Determine the grade of each Assur group and the grade of the mechanism. 0VsrAV0  
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9. (15 points) An offset crank-slider mechanism is as shown in the figure. O,]t.1V  
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If the stroke of the slider 3 is H =500mm, the coefficient of travel speed variation is K =1.4, the ratio of the length of the crank AB to the length of the coupler BC is l = a/b =1/3. m(XcPb  
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(1)   Find a, b, e (the offset). B@=+Fg DD  
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(2)   If the working stroke of the mechanism is the slower stroke during which the slider 3 moves from its left limiting position to its right limiting position, determine the rotation direction of the crank 1. b,$H!V*  
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(3)   Find the minimum transmission angle gmin of the mechanism, and indicate the corresponding position of the crank 1.

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