(1) The center distance separability of a pair of involute spur cylindrical gears implies that a change in center distance does not affect the . 7/_ VE
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(2) The main failure form of the closed gear drives with soft tooth surfaces is the . 6BU 0hV
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(3) The tooth form factor in calculation of the bending fatigue strength of tooth root is independent of the . }&T<wm !
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(4) The contact fatigue strength of tooth surfaces can be improved by way of . G:c8` *5Q
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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.)
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C. improve the contact strength of the smaller gear 9xK4!~5V
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D. compensate possible mounting error and ensure the length of contact line S:p.W=TAB
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(6) For a pair of involute spur cylindrical gears, if z1 < z2 , b1 > b2 , then . 4>$
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(7) In a worm gear drive, the helix directions of the teeth of worm and worm gear are the same. m~Y'$3w
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(8) Because of , the general worm gear drives are not suitable for large power transmission. ~T>jBYI0
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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 . * ?
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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 . \6`v.B&v
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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°. Ey r5jXt%;
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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. 7< h.KZPc
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(13) In order to , the larger sprocket should normally have no more than 120 teeth. |n+ #1_t%
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(14) In order to reduce velocity nonuniformity of a chain drive, we should take . $9G3LgcS
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(15) In design of a chain drive, the pitch number of the chain should be . T e+^J 8
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2. (6 points) Shown in the figure is the simplified fatigue limit stress diagram of an element. Z9xR
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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. ZY)%U*jWU
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3. (9 points) Shown in the figure is the translating follower velocity curve of a plate cam mechanism. z >|)ieL
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(1) Draw acceleration curve of the follower schematically. ) \ 4
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(2) Indicate the positions where the impulses exist, and determine the types of the impulses (rigid impulse or soft impulse). /1[gn8V691
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(3) For the position F, determine whether the inertia force exists on the follower and whether the impulse exists. T /5"}P`
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4. (8 points) Shown in the figure is a pair of external spur involute gears. [4XC #OgA
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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 , . 4P%m>[
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5. (10 points) For the elastic sliding and the slipping of belt drives, state briefly: G o <'
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(2) influence of the elastic sliding and the slipping on belt drives. TJOvyz`t
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(3) Can the elastic sliding and the slipping be avoided? Why? cJ/]
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6. (10 points) A transmission system is as shown in the figure. ~V+l_
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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. PW)aLycPK
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(1) Label the rotating direction of the worm 1. KCtX $ XGL
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(2) Label the helix directions of the teeth of the helical gears 3, 4 and the worm gears 2, 6. {a "RXa
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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. NFy MY#\]
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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. )=_ycf^MC
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(1) Label the action lines of the resultant forces of all the pairs for the position shown. QLr9dnA
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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. ^v :Z o
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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. `f`T S#V
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(1) Calculate the DOF of the mechanism and give the detailed calculating process. q=5l4| 1
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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 . E
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(3) Replace the higher pair with lower pairs for the position shown. b"CA Kl
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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. l-)B ivoi
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9. (15 points) An offset crank-slider mechanism is as shown in the figure. a \5FAkI
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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. 7[#xOZT
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(1) Find a, b, e (the offset). |\9Tv N^$`
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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. E1V^}dn
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(3) Find the minimum transmission angle gmin of the mechanism, and indicate the corresponding position of the crank 1.
