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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 . 3ximNQ} S
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A. radii of the pitch circles B. transmission ratio C. working pressure angle dd<:#c9
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(2) The main failure form of the closed gear drives with soft tooth surfaces is the . q]eFd6
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A. pitting of tooth surfaces B. breaking of gear tooth N-2([v
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C. wear of tooth surfaces D. agglutination of tooth surfaces i iX\it$s
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(3) The tooth form factor in calculation of the bending fatigue strength of tooth root is independent of the . (#6AKr9 K
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(4) The contact fatigue strength of tooth surfaces can be improved by way of . ~:>AR` 9G
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A. adding module with not changing the diameter of reference circle KD% TxK
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B. increasing the diameter of reference circle 0K<x=-cCB
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C. adding tooth number with not changing the diameter of reference circle 0 "EoC
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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.) vUNisVA
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A. equalize strengths of the two gears B. smooth the gear drive ?c!:81+\
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C. improve the contact strength of the smaller gear xXX/]x>
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D. compensate possible mounting error and ensure the length of contact line v "Me {+
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(6) For a pair of involute spur cylindrical gears, if z1 < z2 , b1 > b2 , then . 9UwLF`XM
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(7) In a worm gear drive, the helix directions of the teeth of worm and worm gear are the same. #~^btL'dHF
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A. certainly B. not always C. certainly not
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(8) Because of , the general worm gear drives are not suitable for large power transmission. xCWz\-;
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A. the larger transmission ratios B. the lower efficiency and the greater friction loss t9F DU
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C. the lower strength of worm gear D. the slower rotating velocity of worm gear A>= E {
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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 . J8?2R^;{
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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 . s~^}F +n
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C. out of the driving sheave D. out of the driven sheave ,:)`
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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°. dRW$T5dac
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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. B4h5[fPX
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(13) In order to , the larger sprocket should normally have no more than 120 teeth. 5'KA'>@
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B. ensure the strength of the sprocket teeth C. limit the transmission ratio ]fBUT6
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D. reduce the possibility that the chain falls off from the sprockets due to wear out of the L\%orLEmK
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(14) In order to reduce velocity nonuniformity of a chain drive, we should take . 1oiRW Re
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(15) In design of a chain drive, the pitch number of the chain should be . >J9oH=S6
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2. (6 points) Shown in the figure is the simplified fatigue limit stress diagram of an element. vM:cWat
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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. 1 zw*/dp
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3. (9 points) Shown in the figure is the translating follower velocity curve of a plate cam mechanism. (x/k.&
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(1) Draw acceleration curve of the follower schematically. `tP 7ncky
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(2) Indicate the positions where the impulses exist, and determine the types of the impulses (rigid impulse or soft impulse). jv&*uYm
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(3) For the position F, determine whether the inertia force exists on the follower and whether the impulse exists. *S2ypzwRZ,
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4. (8 points) Shown in the figure is a pair of external spur involute gears. ;qm
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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 , . Evedc*z~P
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5. (10 points) For the elastic sliding and the slipping of belt drives, state briefly: ee^{hQi
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(1) the causes of producing the elastic sliding and the slipping. fTK3,s1=
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(2) influence of the elastic sliding and the slipping on belt drives. C$XU%5qi
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(3) Can the elastic sliding and the slipping be avoided? Why? H"
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6. (10 points) A transmission system is as shown in the figure. !/'t5~x[
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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. x kx^%3dV
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(1) Label the rotating direction of the worm 1. D=j-!{zB
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(2) Label the helix directions of the teeth of the helical gears 3, 4 and the worm gears 2, 6. cOmw?kA*G
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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. Z3"%`*Tmq-
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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. n,vct<&z@
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(1) Label the action lines of the resultant forces of all the pairs for the position shown. sXL q*b?
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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. N]>=p.#j
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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. Lu?C-
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(1) Calculate the DOF of the mechanism and give the detailed calculating process. -$pzl,^ h
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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 . !EvAB+`jLI
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(3) Replace the higher pair with lower pairs for the position shown. \o z#l'z
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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. I,E?h? 6Y
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9. (15 points) An offset crank-slider mechanism is as shown in the figure. ]RZ|u*l= x
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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. ~Z -Vs
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(1) Find a, b, e (the offset). [ZN tCnv
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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. = h-U
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(3) Find the minimum transmission angle gmin of the mechanism, and indicate the corresponding position of the crank 1.
