曲柄滑块机构 slider-crank (or crank-slider) mechanism6 _/ i* f# l" g( @9 Q) l2 e7 v X
曲柄摇杆机构 crank-rocker mechanism
9 I* z0 q$ B- m( C: n曲齿锥齿轮 spiral bevel gear
: f6 u7 T* D( a; C曲率 curvature
6 }" ^; \, ~4 h* t) L曲率半径 radius of curvature! n6 h4 X* w* b6 ]
曲面从动件 curved-shoe follower
) ? t" @4 J$ W; ]5 N曲线拼接 curve matching
" X6 D8 s) d! [曲线运动 curvilinear motion
- |% h% e' p k4 H4 ~曲轴 crank shaft+ F( }" J. H; n9 V
驱动力 driving force+ z3 R0 v C Y- w6 ` }
驱动力矩 driving moment (torque)
0 C/ x0 P- h2 Q5 G9 Y全齿高 whole depth
3 T% e! J7 B8 h3 |6 u权重集 weight sets1 X% \9 t0 l5 p* L
球 ball3 l8 W# Z Y& p
球面滚子 convex roller
7 g" T2 f" `0 f" K球轴承 ball bearing, O0 A1 w" N7 x2 N8 e# n
球面副 spheric pair# n& }+ D" R9 M8 s( M& o
球面渐开线 spherical involute
6 L! }2 v+ b: F# M# I球面运动 spherical motion
8 T" e; D4 T. q- x( k* w, L. M, T球销副 sphere-pin pair6 o$ d; p: D0 f. W6 [9 h. i* P. t& M
球坐标操作器 polar coordinate manipulator
% c) E8 ^1 o3 G8 ~; y3 w5 b. k燃点 spontaneous ignition
8 D) j9 F0 d6 G* Z/ S; c5 `热平衡 heat balance; thermal equilibrium
! w! w: ]) k9 r6 Y6 [3 w人字齿轮 herringbone gear
) G1 ^1 M& Z, ]5 O- K; @9 ]& `冗余自由度 redundant degree of freedom1 K5 o) w& \) n- N1 B( D6 e4 l
柔轮 flexspline
5 R! b# Y% j O0 w t$ W柔性冲击 flexible impulse; soft shock
@5 t1 ~/ s1 V8 y5 T柔性制造系统 flexible manufacturing system; FMS
3 s& q& @3 i) Y柔性自动化 flexible automation' E" ~; I( N. }" g( ]
润滑油膜 lubricant film
0 s9 `' M, c. y# O. p; ^润滑装置 lubrication device9 y: H% J7 S; [5 ?$ n
润滑 lubrication
4 w v" N3 g' @- H润滑剂 lubricant; y6 a0 C9 h$ A4 U, i
三角形花键 serration spline
- e' X1 ]9 I& \/ l+ ?8 h! Q三角形螺纹 V thread screw
" j9 f" T h* U f% r1 v5 }+ R三维凸轮 three-dimensional cam
?* o8 f$ Z9 W三心定理 Kennedy`s theorem
( m" X" }- Q O砂轮越程槽 grinding wheel groove. c3 D+ n, @1 s L9 N
砂漏 hour-glass
4 N! ?; I; s* ]/ ]2 x少齿差行星传动 planetary drive with small teeth difference; j {- e. P. ?3 w& ^! n* s
设计方法学 design methodology
" g q3 j U x# Q" v h# K% e) |设计变量 design variable
6 h. b& P7 L) s5 m设计约束 design constraints
1 ^ v& _: ~& `' B) J深沟球轴承 deep groove ball bearing
" F; T* c7 B& f9 T/ e9 W生产阻力 productive resistance9 @( X5 Y+ i# ]9 y
升程 rise' F* Y" V$ x* N
升距 lift
- a7 @; x0 e$ R9 l, H. R" s实际廓线 cam profile
7 i3 R! k" _& ^$ ]6 O1 O十字滑块联轴器 double slider coupling; Oldham‘s coupling
T0 d7 }% m& t4 D* F2 p0 X2 \矢量 vector/ Q4 w( P* U& m' y
输出功 output work; t" m& G& u' ~% e! r
输出构件 output link
5 o( [" ^2 [, s- g输出机构 output mechanism! M% P1 {3 F. }$ h$ P, E. V
输出力矩 output torque o4 Q4 j! K; l; G& c
输出轴 output shaft
2 ~+ q/ f5 x( E输入构件 input link
# }+ d& H& f/ v& R! P6 z4 Q数学模型 mathematic model' { W4 ^( H4 Y; | B
实际啮合线 actual line of action' V% W$ Z7 x+ h+ T
双滑块机构 double-slider mechanism, ellipsograph
/ F$ l, z/ l! A9 b, _5 f4 i. D双曲柄机构 double crank mechanism
9 W, n% W# r" b& I) j8 H4 |双曲面齿轮 hyperboloid gear2 r6 j6 a" I& D- [% T! m
双头螺柱 studs3 _& D2 a0 z N% \( x( P& R
双万向联轴节 constant-velocity (or double) universal joint
4 [* A& q. E. P, g9 _双摇杆机构 double rocker mechanism' @% w* `6 f4 o! `' i1 V
双转块机构 Oldham coupling% T/ L- F" M6 Q5 g& y3 i8 K+ \
双列轴承 double row bearing5 Y0 S! [0 q! p, p: o: B
双向推力轴承 double-direction thrust bearing
1 E/ l% U$ j) C" E* C4 l( T松边 slack-side p' o' a* L6 N: ~9 [8 g! W- s, K
顺时针 clockwise
; n3 E% q3 K; D0 j瞬心 instantaneous center
8 \, Z3 D# ~9 ~1 {. c1 p死点 dead point
( D$ U. T. Q% S- j1 u四杆机构 four-bar linkage8 C+ a# T; E" B/ X5 o3 _
速度 velocity
]7 L+ ?# T0 W, V( A0 C+ V: e9 V速度不均匀 ( 波动 ) 系数 coefficient of speed fluctuation
. G4 l; i, L4 L% _8 Y+ S速度波动 speed fluctuation" K, g6 a0 @ W7 y, O% f* x1 x
速度曲线 velocity diagram
# y( {% O, `( m* q8 R速度瞬心 instantaneous center of velocity
0 L5 s! L0 V/ j: c' N# m8 X塔轮 step pulley
$ l, n X0 g9 _+ p: E6 B踏板 pedal
! \4 t1 }/ `; k! S0 H" e& p _# B台钳、虎钳 vice
* H7 }3 e! i6 _1 |; W9 [( M9 ]太阳轮 sun gear; G/ L2 S2 W. T6 m# p2 d
弹性滑动 elasticity sliding motion
% {% M# r0 `3 x弹性联轴器 elastic coupling flexible coupling
1 j# r- ]" `0 R, L/ n' q1 i# j% T弹性套柱销联轴器 rubber-cushioned sleeve bearing coupling$ @6 }, D6 R. ?1 o
套筒 sleeve
$ |$ z0 O) |8 z梯形螺纹 acme thread form! J6 o2 a! \5 Z! a
特殊运动链 special kinematic chain
. e G) d. i" b* w5 B/ `& I5 ]特性 characteristics# t8 m. @( x r% C1 c
替代机构 equivalent mechanism2 q5 }+ z% l6 `7 i, W2 W
调节 modulation, regulation
8 R! x2 l6 ]5 I0 ^/ O调心滚子轴承 self-aligning roller bearing
) K- C/ m# c0 K. C. r调心球轴承 self-aligning ball bearing
9 H9 I" P3 b8 ?6 ?) Z# ^调心轴承 self-aligning bearing9 Z+ I. m% o# F. N' T- [
调速 speed governing
( Z* E) D1 c! g" x; f- d. V调速电动机 adjustable speed motors% \8 \8 C( D- f' }
调速系统 speed control system0 x: U; {5 r7 P) N6 m; V
调压调速 variable voltage control+ v7 h/ x& c+ Q( I& u F! ?
调速器 regulator, governor, P- q ^; s. Q& W% `2 h, g# t
铁磁流体密封 ferrofluid seal
* y/ O0 h7 z7 d2 }9 y- j6 U停车阶段 stopping phase$ X* j5 u$ O5 X3 ?4 a
停歇 dwell
9 H. U* Q5 ?) W8 _1 w" j8 ^同步带 synchronous belt9 x- g" |( k( s3 Y7 B1 l: }
同步带传动 synchronous belt drive* ~# j6 o2 b) N6 [, e
凸的，凸面体 convex
6 H+ | q* C8 M$ M- {% o5 }凸轮 cam5 W7 l! f( P( c; N1 ^- Y
凸轮倒置机构 inverse cam mechanism
+ o( i* F) w1 A凸轮机构 cam , cam mechanism4 I: T* |: c% T4 K) z/ F+ h
凸轮廓线 cam profile
5 T% I) ?3 L, n V( Z. ]4 B凸轮廓线绘制 layout of cam profile; f& v3 ?2 X, N2 Q1 t7 g
凸轮理论廓线 pitch curve1 n# S' d0 V" [; C' I
凸缘联轴器 flange coupling
, A+ D2 O( y l) W" k: t- a/ w图册、图谱 atlas
3 G6 ?- |5 f. r$ c+ B图解法 graphical method
$ i0 R. t$ R! t推程 rise8 m* X, A) m2 W/ w
推力球轴承 thrust ball bearing; t6 W+ h; v4 j0 A8 x6 x9 d" Z |
推力轴承 thrust bearing
% b7 U4 j1 u" a9 D% z退刀槽 tool withdrawal groove: f" m5 ?* a4 J- a& f' x. \
退火 anneal
% V; B% }* m* s7 U陀螺仪 gyroscope& Y& H, `$ T0 Q/ U
V 带 V belt
! [3 I$ m7 x( s3 q s+ `外力 external force / Q6 ?5 _- i. v5 M5 i" C
外圈 outer ring ; D: ~; \, b! @9 W( W7 B; \
外形尺寸 boundary dimension
$ k ]" I; [# B+ y# l2 X万向联轴器 Hooks coupling universal coupling
" ~: k+ ^/ t3 t* J% z* d外齿轮 external gear5 s, W( U1 o3 {; g9 I7 n5 S
弯曲应力 beading stress
, H' T2 A4 b' _) B弯矩 bending moment
& P9 P e# z+ W) ]- u腕部 wrist
7 H. V) a. G4 [ _* x e往复移动 reciprocating motion
1 N$ j) A1 l$ K+ f3 j6 Z往复式密封 reciprocating seal0 j! q" [5 b( _
网上设计 on-net design, OND) G, c/ x X& \$ P% J, p; J3 c
微动螺旋机构 differential screw mechanism* f" f3 ]3 R* P7 n3 {; X2 C
位移 displacement
7 d5 c! G0 h n+ L# L2 S位移曲线 displacement diagram
6 E; R, L, S5 F! E8 B& `7 v7 m位姿 pose , position and orientation
: a) @6 x* i- K9 s' I" p稳定运转阶段 steady motion period% ?# Y E9 z# {! W' [* p0 `$ e
稳健设计 robust design& z2 T6 M& ?* y& V, G
蜗杆 worm, n# L) Y( f3 i7 t3 e; M9 @
蜗杆传动机构 worm gearing$ P1 F! g# [" V! C
蜗杆头数 number of threads
# a |% A9 T/ l$ C* o2 [7 u蜗杆直径系数 diametral quotient
7 ^8 K2 _5 U2 |蜗杆蜗轮机构 worm and worm gear* Q& j% s. x3 k, B- e. g% [
蜗杆形凸轮步进机构 worm cam interval mechanism
5 o5 b/ b9 K! [' b% G6 D, f* B% }蜗杆旋向 hands of worm" {5 P; B* m; i
蜗轮 worm gear: H, v8 A( M% c* l+ b. [# @4 q
涡圈形盘簧 power spring8 n3 M7 f$ |3 m( x
无级变速装置 stepless speed changes devices! C, ]) c) l- L; t; f
无穷大 infinite
& O8 L0 V b5 b" D% p$ @( a! V3 @系杆 crank arm, planet carrier
8 S: H/ j. j6 D# z现场平衡 field balancing
, u7 N0 d4 Y$ F# a! ^0 `0 l向心轴承 radial bearing
; R# L& W$ q; ^- _7 p) E( `. f1 f5 H向心力 centrifugal force
! }1 `5 v8 l4 ~( f6 I5 l, i' ?相对速度 relative velocity3 F9 n. [" m. m' A! Y
相对运动 relative motion. n0 X: L3 i0 Z4 |# a% d
相对间隙 relative gap
( U! [3 N# ]9 H0 \" z象限 quadrant
Q" Q" K+ F) D& D F5 U5 i橡皮泥 plasticine
- |! Y; D$ b; x9 M2 Z% p6 @细牙螺纹 fine threads& N( J* z3 K1 L) q8 k
销 pin" g. _$ _, Z( b. r; G' a+ ^3 x
消耗 consumption/ h7 h1 A9 B- L1 m7 T
小齿轮 pinion
+ [1 @% k. D" U* D小径 minor diameter9 O+ K0 @7 E* c- H% I* z2 Q
橡胶弹簧 balata spring
- O1 V3 V& n$ {+ l修正梯形加速度运动规律 modified trapezoidal acceleration motion% Z# C" k2 }8 O- P1 W; ^" i
修正正弦加速度运动规律 modified sine acceleration motion0 m9 r `; ?- }# q
斜齿圆柱齿轮 helical gear. [+ O' ^. ~- H9 k6 Y( j
斜键、钩头楔键 taper key: \2 l, O& C% B4 q) ~2 _
泄漏 leakage9 A. d$ ?0 z6 D( q' L
谐波齿轮 harmonic gear) {+ ~8 L% ^& Y7 c' V
谐波传动 harmonic driving
8 K/ Z: A" i* m9 B# x. `% l/ D谐波发生器 harmonic generator
# {# n% j6 Z* d2 y# U" K! Q1 R' ^斜齿轮的当量直齿轮 equivalent spur gear of the helical gear0 i# d4 U" C( z; ]% x7 W0 u$ a* W1 T
心轴 spindle2 v% J- i" k, a/ {
行程速度变化系数 coefficient of travel speed variation' r( b! H9 J- G" X% m
行程速比系数 advance-to return-time ratio
) Z: k+ q. e% I! o; `! m# r1 o行星齿轮装置 planetary transmission
" ?3 k0 T9 u9 r: ?9 b, [3 P( E: L6 J行星轮 planet gear
) ]9 A& C0 f: v: H/ W- [行星轮变速装置 planetary speed changing devices
9 v7 ^- h9 u6 |& V. M6 Q8 n$ s行星轮系 planetary gear train
+ T: t' i1 p2 K7 ]6 Y形封闭凸轮机构 positive-drive (or form-closed) cam mechanism
) P+ K: D$ K& h* A! L- x4 F虚拟现实 virtual reality" e# c- y/ y# f1 Z
虚拟现实技术 virtual reality technology, VRT" a5 z: k% X/ M& }# y
虚拟现实设计 virtual reality design, VRD
+ D& W3 s1 l. J( j虚约束 redundant (or passive) constraint
% E' _* U1 U1 }, S6 X1 h许用不平衡量 allowable amount of unbalance1 @/ P0 e3 O5 n. k1 I% w
许用压力角 allowable pressure angle, ~/ i- u; R+ Y
许用应力 allowable stress; permissible stress- C) ?& e' I% ?" e1 l* f
悬臂结构 cantilever structure
, E; E, i4 L- @悬臂梁 cantilever beam
8 f+ q. C8 w) f- x$ C循环功率流 circulating power load ?& [# W! \2 v. m
旋转力矩 running torque
, l/ a+ Q. K# M* d旋转式密封 rotating seal
7 ]2 v+ \' t4 x+ E5 t旋转运动 rotary motion+ d! W2 [9 v# f# E/ m
选型 type selection" D' J: ?3 T* a1 \+ p
压力 pressure 0 k1 B. e% J# |5 S6 F6 z
压力中心 center of pressure
( a$ E( b2 i& H- \; O) O压缩机 compressor
8 M2 `0 a7 R; P: M- |压应力 compressive stress% m7 ?7 j7 j7 H Y6 b
压力角 pressure angle
; D2 A2 O7 x$ ]2 a$ I3 {( _牙嵌式联轴器 jaw (teeth) positive-contact coupling
6 i4 v' a3 Q$ u雅可比矩阵 Jacobi matrix. s8 Y' K) E% ^2 w' Y
摇杆 rocker
- o/ f. ^0 o- {: _' }1 T# x液力传动 hydrodynamic drive3 q. a' T- E8 I+ p( \/ s% J K
液力耦合器 hydraulic couplers
1 _2 p; a/ R1 a( U液体弹簧 liquid spring
4 s7 f% W; ]5 `8 x' `* q h+ [液压无级变速 hydraulic stepless speed changes
7 m4 n2 x# V) B+ e. l液压机构 hydraulic mechanism
$ l: u& I- T) H: y一般化运动链 generalized kinematic chain. ?( C2 s5 Z4 k' y, ~
移动从动件 reciprocating follower. p! ~2 r7 [: f. w5 o K
移动副 prismatic pair, sliding pair
, N# \. e! n: O0 p" a' s, W移动关节 prismatic joint
0 b7 [ @8 D2 p2 U/ D) W; l. b移动凸轮 wedge cam/ F: j- i* E' w8 Z! P. W" M
盈亏功 increment or decrement work
; x: N( L' p- Y" b! m2 X$ p* _应力幅 stress amplitude
: N# R3 c' k) Y- O应力集中 stress concentration3 \) B* [. R0 |9 F5 R
应力集中系数 factor of stress concentration. j) M, `& j8 i* s. b$ w
应力图 stress diagram
/ f6 S8 S& o7 }/ D/ Q% Y应力 — 应变图 stress-strain diagram7 x9 w4 q1 K1 H; W p+ K
优化设计 optimal design
7 J X( o( h; t. G! x& m* W' f/ {2 C油杯 oil bottle) i3 H5 C7 [% C
油壶 oil can9 k) g1 H3 ?7 c! `9 Q) O8 ?; l
油沟密封 oily ditch seal+ ]3 O$ f+ R- H! p6 V
有害阻力 useless resistance
- h7 A/ r: U0 M: E: q有益阻力 useful resistance' }3 E1 q1 M: i5 s, V: n
有效拉力 effective tension
9 b1 K% @* P6 L- \7 H) d2 |6 Q! C% r有效圆周力 effective circle force
" |! C( w( _8 l& \& J) }" ?; B. x有害阻力 detrimental resistance1 p( x, \0 \, }) C# H
余弦加速度运动 cosine acceleration (or simple harmonic) motion- m6 b; z8 l% k' Y4 {$ G7 x
预紧力 preload
! H+ J0 a6 t% t3 e! z原动机 primer mover |
发表于 2008-2-21 11:42:15