曲柄滑块机构 slider-crank (or crank-slider) mechanism, n. p# O2 k! Q' m9 F9 d8 \& k
曲柄摇杆机构 crank-rocker mechanism
1 x# Q& J6 i2 @, O曲齿锥齿轮 spiral bevel gear
3 W9 J& n8 n) D/ d曲率 curvature
. x& L) O" @+ h- n6 K1 |. Y: x6 C曲率半径 radius of curvature6 w# H- B6 @+ l' M/ x
曲面从动件 curved-shoe follower
1 |% I- N' u! u3 T$ M曲线拼接 curve matching
7 Q( ?' s5 a: Y- c; p" W! a曲线运动 curvilinear motion: y: Y B# |3 L% p0 y& M7 _
曲轴 crank shaft
9 d% e3 F; R; ?: C; ]) w7 |驱动力 driving force2 U7 Y( z, ^: v+ `4 \
驱动力矩 driving moment (torque) J( d% N. J( V' i6 {
全齿高 whole depth
; V4 c! ?/ Y* R4 J权重集 weight sets9 Z7 N8 k4 F3 ^6 ]$ w4 e
球 ball$ ?6 J, {# P3 I
球面滚子 convex roller8 p1 X9 U7 P5 s# c0 ?
球轴承 ball bearing
" E9 L6 ]$ b/ u | {6 T& V: e5 W球面副 spheric pair
! ]7 o& A* i3 f球面渐开线 spherical involute3 u/ C% h. M9 u7 v1 R
球面运动 spherical motion
`" m0 p. d" R球销副 sphere-pin pair/ {, g \* ?0 ?2 o( y6 R
球坐标操作器 polar coordinate manipulator: ^& q9 z' l b2 v8 h2 g+ ?
燃点 spontaneous ignition
4 N: K& T9 |! u) w) D# T' u/ E- d热平衡 heat balance; thermal equilibrium 4 E" R7 d; `+ V% Q. S; R* j6 F
人字齿轮 herringbone gear3 \* z5 I. F$ M) `) ~& A1 o% s# I+ @
冗余自由度 redundant degree of freedom* T" M8 C0 N0 |7 {7 O% X; @
柔轮 flexspline5 q8 {- g6 v( ?9 J h/ U/ C; X; @
柔性冲击 flexible impulse; soft shock7 z" }. t8 r$ T8 U8 j: M! |+ s
柔性制造系统 flexible manufacturing system; FMS; N$ `: x1 J6 J, ]4 C. m
柔性自动化 flexible automation
1 E9 g" i5 r4 K8 m: F润滑油膜 lubricant film% l9 a% x4 i- p9 }, O
润滑装置 lubrication device7 t6 P; b0 x9 ?9 A5 |
润滑 lubrication! `/ N3 a: s2 D! Y
润滑剂 lubricant
5 _6 d1 \! C" a# D z/ ^7 e三角形花键 serration spline / M8 f3 ?! h% u( m E9 X
三角形螺纹 V thread screw
) F$ O- Z( }/ N3 _3 C三维凸轮 three-dimensional cam
7 y# P9 c$ L/ P4 r3 y* i0 I三心定理 Kennedy`s theorem/ j; T0 _$ E% t, }+ n' ` D1 x- x
砂轮越程槽 grinding wheel groove
. _4 ?$ ~6 p% L4 C" D3 @4 u: z砂漏 hour-glass
, B# T3 y" u% \" c少齿差行星传动 planetary drive with small teeth difference7 ]# t- e* _- J
设计方法学 design methodology. i- Q, @% J) b/ h. R' y( ^5 z
设计变量 design variable% M: k+ C7 R# G( D0 ] E
设计约束 design constraints
, j9 a5 A+ m( V$ z- h+ F6 Y2 Y) s' Q深沟球轴承 deep groove ball bearing: e6 T4 }6 t$ o8 S
生产阻力 productive resistance
' @4 ^; [/ X" h0 y! X升程 rise
) `3 w! i; v$ l& ~2 e升距 lift2 v0 G" Y: v5 G2 L; |: `# `
实际廓线 cam profile
5 X4 b k) ^8 q十字滑块联轴器 double slider coupling; Oldham‘s coupling* Z# ^8 Q6 O$ @+ r( I% n( u) U( o
矢量 vector& I/ X$ U2 l: @- U) D
输出功 output work8 a' y9 W( p7 E0 X
输出构件 output link
u* }4 N, `4 o输出机构 output mechanism
2 J8 U9 g% \( k0 I4 I% S% s输出力矩 output torque
5 w: ?' x" t' h w4 t s输出轴 output shaft
+ x. n- i8 ^( K' a2 X. c' S输入构件 input link
: b2 h6 g) v- y/ _8 |& b# y数学模型 mathematic model5 e l/ Z: U, C: a8 p+ H
实际啮合线 actual line of action
* B4 l( d, p7 U4 b" ]/ s) m. a双滑块机构 double-slider mechanism, ellipsograph
4 f+ b. _/ t4 c3 C- f双曲柄机构 double crank mechanism
$ J% J& `. j) E# z# ^7 W双曲面齿轮 hyperboloid gear
0 w) J9 @3 _- K6 F, k双头螺柱 studs9 Z& v l$ o+ l( g
双万向联轴节 constant-velocity (or double) universal joint5 {, t2 |7 @% K7 G
双摇杆机构 double rocker mechanism
0 R/ l5 G" P6 |& `$ O& ~1 S双转块机构 Oldham coupling
. d7 K. u6 {- l( b! G, c双列轴承 double row bearing
& Q0 r( s1 k- |# t! p" K6 W2 v6 @# b双向推力轴承 double-direction thrust bearing( K4 J9 X0 h& _) {3 e% T" |; ?
松边 slack-side
3 Q- i7 ]% G& b顺时针 clockwise
" n# ?; _ C4 _6 r" V F* U) p瞬心 instantaneous center6 _0 K3 i, T: ^) F- b- T
死点 dead point; B6 n; P) y' f t" ^
四杆机构 four-bar linkage' r! |% }4 ^# e1 s0 r
速度 velocity
& o( O( M7 y3 h7 O& k速度不均匀 ( 波动 ) 系数 coefficient of speed fluctuation
1 l8 k5 K! }& N& q" [, G速度波动 speed fluctuation
7 V) C- M7 `/ N. U) t1 [速度曲线 velocity diagram) d$ T2 C* D6 i
速度瞬心 instantaneous center of velocity
0 ~/ V2 I+ \3 ^6 _2 d塔轮 step pulley
9 \: n# r& h, z0 b5 }# j踏板 pedal
: w- C) P3 X8 G' L台钳、虎钳 vice7 ^# u% F/ H( f; \. N, |
太阳轮 sun gear7 e5 G ?( ~4 b- y/ m2 \6 w) Y
弹性滑动 elasticity sliding motion
) {' F- b7 R- L u# F' V, R弹性联轴器 elastic coupling flexible coupling. }! J e' |* A1 O
弹性套柱销联轴器 rubber-cushioned sleeve bearing coupling
& t! [# M/ @; m( ]9 P1 \& U8 S x套筒 sleeve
7 _6 Q. H' W+ i) E- `: N( V/ N梯形螺纹 acme thread form
6 q* w( q5 X7 K8 _& l特殊运动链 special kinematic chain
4 n" t4 e4 k9 |: b/ F* {6 z特性 characteristics
. y M( I- [# n/ F- r5 q/ c替代机构 equivalent mechanism
# p- D) t5 G2 w8 c/ y% h' v调节 modulation, regulation
* \( Y* d ^; h; a. ^调心滚子轴承 self-aligning roller bearing) x+ |& V2 A9 v; K* b9 V+ L
调心球轴承 self-aligning ball bearing4 w# ?$ f' z; U, J) F& U2 h2 v
调心轴承 self-aligning bearing
z/ f' D( M h* [* h% m. P调速 speed governing7 D+ }" v, ^5 D. Q: q2 w
调速电动机 adjustable speed motors
$ D* t6 Z& P) m" Z2 x3 q( Y, Y调速系统 speed control system& \# _: y2 U, ^2 T! ^5 g: I
调压调速 variable voltage control, r7 k: U5 l& c( s
调速器 regulator, governor
3 i2 [5 {$ ] D: Z- R$ @铁磁流体密封 ferrofluid seal
6 }2 L/ M/ ?6 E( ^1 R停车阶段 stopping phase
. ?% {, |7 O' ]. ]9 d4 |% @; N停歇 dwell Y# j) @3 [ Y/ I g
同步带 synchronous belt, ?! w( [, r- U/ g: b: \4 e
同步带传动 synchronous belt drive
; S: Q) X9 T/ y; f f凸的，凸面体 convex
9 y' k7 p& [9 y- L凸轮 cam- B" g. P Q- |& K7 \" q
凸轮倒置机构 inverse cam mechanism
1 n3 `! x/ P% E+ p( l: r凸轮机构 cam , cam mechanism" u0 g$ h7 Q6 X J, G( c0 x' y7 d
凸轮廓线 cam profile
" ^. v: `1 @6 ~ x凸轮廓线绘制 layout of cam profile
/ g" c4 ]: n6 V8 e" X凸轮理论廓线 pitch curve1 C) Z: p1 \* i! O( j
凸缘联轴器 flange coupling" V3 P5 }2 b0 k5 S4 g
图册、图谱 atlas, H" q, r3 i ? g8 }/ R8 g. J: w
图解法 graphical method
( R% k; D: }( F& d推程 rise. |" [4 o+ Z/ i; O9 s0 G0 e I
推力球轴承 thrust ball bearing
5 g, F3 t. y F6 o& g推力轴承 thrust bearing. a7 F7 p( ]3 A8 X) A
退刀槽 tool withdrawal groove8 g, V g( ?" Y; p z
退火 anneal/ x( E' n$ m2 d0 w+ _! R: U y
陀螺仪 gyroscope
3 ?9 h K+ }2 U' Y( P, ?V 带 V belt) [, {( G. e9 I" @
外力 external force + f" o* s5 i7 I5 e0 Q$ P
外圈 outer ring
" W6 O4 m$ m/ P9 Z, `+ P0 P) [外形尺寸 boundary dimension
: B, W0 x8 T$ b" Y9 p& H' Q) J7 @万向联轴器 Hooks coupling universal coupling
6 ~6 w- ]& F( x外齿轮 external gear2 {1 x, O7 s! w* O* {/ L$ e, z
弯曲应力 beading stress
2 k4 |, F3 N: J4 w, m弯矩 bending moment
& S! |' d, [) Z0 t& a6 }腕部 wrist
9 ]( O- \- S) V' M( ~' K6 I往复移动 reciprocating motion& N" U/ V% i1 S1 F. H- i5 v
往复式密封 reciprocating seal
1 S7 e$ b3 Y5 W+ O! c- ?+ v7 @网上设计 on-net design, OND
; A. x/ ?# f/ r/ D+ I2 W$ N微动螺旋机构 differential screw mechanism
3 U/ W8 r- { |& {. w! k1 t位移 displacement& M3 @- N- s, ~, ~! d- @ ]( z
位移曲线 displacement diagram8 h3 c- W: Q o6 I- v F1 Q) J
位姿 pose , position and orientation3 X6 |" H, j2 ?
稳定运转阶段 steady motion period q# y2 q3 ~6 d r6 w: k
稳健设计 robust design
+ w4 e1 P- S& _. |4 j4 h蜗杆 worm! t* I8 M" C, i5 r" Q) r
蜗杆传动机构 worm gearing# X% ?! R( Z+ Z4 x+ H" l
蜗杆头数 number of threads7 B# `1 [/ `7 [+ K
蜗杆直径系数 diametral quotient
! ~8 c W. w4 B' P% ?9 Z) G4 O; r蜗杆蜗轮机构 worm and worm gear, i7 [0 {9 C5 A- n" W' W
蜗杆形凸轮步进机构 worm cam interval mechanism
, e" C: Z. L( [, {, ^+ ?- ?蜗杆旋向 hands of worm& q7 A B X" \' G, Z5 I/ e' s( Y$ i
蜗轮 worm gear
. _7 h: R; _8 A, Y+ m; X* N涡圈形盘簧 power spring
- K* \% S3 E9 n3 U0 G% g1 H3 l无级变速装置 stepless speed changes devices& q% _- D O% ?. }8 j1 }
无穷大 infinite
: r! a& \- w# G% c6 @. o' @. B- ]系杆 crank arm, planet carrier 8 E& _7 J. v3 j1 d2 D. {, R
现场平衡 field balancing
V) |# e+ w1 ?, F/ ?6 \7 D( ?5 \向心轴承 radial bearing4 D+ ?3 K) }# I$ T
向心力 centrifugal force
# J: ]; y+ b! S/ K相对速度 relative velocity
' q. O; g" W1 h9 v0 F" ^8 X6 M相对运动 relative motion' O' b& p8 _! p
相对间隙 relative gap
( _( } E" S) M p3 [: A# j; ~象限 quadrant! `+ D2 A P! c3 [: r( r
橡皮泥 plasticine. E& T. E& D1 o( V5 H6 \5 z
细牙螺纹 fine threads* F% U, z. \! F& I; o. ]3 [
销 pin
7 \& y6 Y! _0 o6 |0 u消耗 consumption
/ a2 {0 f' _0 c; G2 T ?6 z j小齿轮 pinion- E) i8 ^7 b; S! J7 h" T' K
小径 minor diameter- f& W# w2 E, {# j) H8 b
橡胶弹簧 balata spring5 p6 c* ^7 `7 J/ T
修正梯形加速度运动规律 modified trapezoidal acceleration motion
( [7 H' k. z/ m5 ^. o修正正弦加速度运动规律 modified sine acceleration motion) ~$ m$ @3 M" a" d1 `# P6 C& y
斜齿圆柱齿轮 helical gear
) \3 K, O! e$ @斜键、钩头楔键 taper key1 o! T' a" }5 i3 }, k6 s. U- E# k3 q
泄漏 leakage7 _8 z5 t( o/ f G* y* M, |
谐波齿轮 harmonic gear
9 h4 P3 U4 |4 D- I谐波传动 harmonic driving
0 S/ s/ t, a: R5 W* A谐波发生器 harmonic generator- E2 _; m* w6 q0 _4 k$ s$ ?
斜齿轮的当量直齿轮 equivalent spur gear of the helical gear
5 {+ ]/ Q" U* }# X6 ^+ d* f, B" `0 ~8 _/ b心轴 spindle
+ \+ b& B" h, d) b* p, ]$ l行程速度变化系数 coefficient of travel speed variation) B' F2 ~- z6 U G( X
行程速比系数 advance-to return-time ratio
! J8 ^. I9 p3 M. q. H行星齿轮装置 planetary transmission
. X" ]/ x9 _, t% m行星轮 planet gear
% [* C! A7 ]: t9 n: f! d' |( ^: |行星轮变速装置 planetary speed changing devices
; H+ v0 B" B/ Z行星轮系 planetary gear train, _' u2 p( r* U+ L9 u
形封闭凸轮机构 positive-drive (or form-closed) cam mechanism
' ]2 v2 q- k. ?: D虚拟现实 virtual reality
1 u3 f2 T' L3 f8 q3 h虚拟现实技术 virtual reality technology, VRT
0 z! T" v6 B1 H# }1 f2 L0 ]虚拟现实设计 virtual reality design, VRD$ V( d- t8 h8 g% k
虚约束 redundant (or passive) constraint
9 j5 j* y3 v+ V+ P( e" o) b1 y许用不平衡量 allowable amount of unbalance
" K( F4 b% W% `$ c3 x许用压力角 allowable pressure angle
8 C3 W2 D) ]. } d. R5 r: @8 E许用应力 allowable stress; permissible stress
- _" E8 c, I \8 y悬臂结构 cantilever structure- P, q3 ^' h' Q+ a- e
悬臂梁 cantilever beam
+ C: E7 ^6 y0 ]" Y) v) A8 K循环功率流 circulating power load
& I: i# o/ t2 p S* U0 K旋转力矩 running torque
- I& |2 n% X- A5 I旋转式密封 rotating seal
$ K. L7 {9 Y8 H旋转运动 rotary motion* e0 y6 h/ y3 \. @' o7 A
选型 type selection( B% d t# S) K" O
压力 pressure
K3 S6 ?. w: q4 _- Y压力中心 center of pressure 3 \$ D7 ]' R9 D* p% b( t, x1 f3 H
压缩机 compressor, ]& X. d6 p' n+ v5 V9 Y$ f3 C
压应力 compressive stress: t3 h' R% P- v( G$ P/ c
压力角 pressure angle
+ d8 q- e2 _! x b- |. i6 n0 K/ O牙嵌式联轴器 jaw (teeth) positive-contact coupling @; c9 I+ @' ]: H
雅可比矩阵 Jacobi matrix
! I- k: u& S' _4 A2 i* z8 _/ j& o: c) y摇杆 rocker' O2 Z3 Z! e$ n
液力传动 hydrodynamic drive9 j8 p* X" f1 O5 K6 T, n
液力耦合器 hydraulic couplers
7 U. |; q+ S/ L+ f0 _- H液体弹簧 liquid spring
- ~9 R! o- G* E$ B( ~) k4 f液压无级变速 hydraulic stepless speed changes6 Q b8 ~. ^% G
液压机构 hydraulic mechanism3 D: p3 q1 F6 |- `# |& E- |
一般化运动链 generalized kinematic chain2 F' W& q5 g7 e# A' v
移动从动件 reciprocating follower
+ j1 o, t' }% N) Q移动副 prismatic pair, sliding pair
) Z* @: u1 w* b; r5 z移动关节 prismatic joint4 I, P8 }( o7 ], O6 I! R
移动凸轮 wedge cam
8 e$ H5 n8 v. @6 G/ R盈亏功 increment or decrement work
+ X9 i3 C+ M/ F, |1 g8 B应力幅 stress amplitude* L5 a* R; Q" s$ ~. b9 L( V
应力集中 stress concentration; z8 E$ x t: |, d
应力集中系数 factor of stress concentration7 h7 T' p4 Q$ Q i- ^" Z4 ]
应力图 stress diagram0 I. J" N( ]+ @0 P0 e
应力 — 应变图 stress-strain diagram& l6 w- z& L1 `; ], e
优化设计 optimal design8 Z% p% {2 a, T
油杯 oil bottle3 l8 m; q# g: X x9 c/ y* P
油壶 oil can) k" E, r r9 i" h1 g! `- ]: v0 b
油沟密封 oily ditch seal
" S. h* r5 P8 y7 E7 Z: Q有害阻力 useless resistance
+ H7 Z3 C7 p o1 R3 s" k! `* I有益阻力 useful resistance
: g1 i5 g, O1 t# g' h5 \有效拉力 effective tension
/ L/ m9 p' ^. ^7 P2 j有效圆周力 effective circle force
- g" y, V4 ?8 R有害阻力 detrimental resistance5 ~9 h3 R9 U3 J& ~. D: D. [! p9 l
余弦加速度运动 cosine acceleration (or simple harmonic) motion, |+ B' B- i( C) D+ K
预紧力 preload
. O/ E' |4 ]: _2 E) u6 G8 q4 t原动机 primer mover |
发表于 2008-2-21 11:42:15