曲柄滑块机构 slider-crank (or crank-slider) mechanism
6 _0 G( C4 d: V6 N2 O曲柄摇杆机构 crank-rocker mechanism8 [# I9 k6 N( H* c4 M. k
曲齿锥齿轮 spiral bevel gear
. u/ Q( n. `( q! E' c' C曲率 curvature
6 k% _ j g+ i( c4 x; b, V$ w曲率半径 radius of curvature3 o0 u. T9 {$ R' L! I
曲面从动件 curved-shoe follower0 f3 h+ j: c4 f( b. t! E, W
曲线拼接 curve matching
1 r! b" K- S; y4 j曲线运动 curvilinear motion. G$ z/ }2 H/ |, l r" a i2 |0 J& k
曲轴 crank shaft7 q$ K# ?0 u, q( {
驱动力 driving force( e% a% U# X1 g. \1 W
驱动力矩 driving moment (torque), Q1 x g" m% d. ?& Z9 k- h) V- Q
全齿高 whole depth4 g3 p1 x# U& m
权重集 weight sets' i: `2 _! _% |$ y* Q/ p
球 ball1 w4 Q, R5 y9 K
球面滚子 convex roller& l* h# J& H; Q
球轴承 ball bearing
4 R v4 T' u# ^& G6 Y, q& Z球面副 spheric pair
- K. d5 p, i5 s+ ]球面渐开线 spherical involute- i; J7 V* M$ \) |6 g9 I+ p
球面运动 spherical motion/ F* l* i+ S9 }* }8 z# G4 G
球销副 sphere-pin pair
$ G. h' e. T) a% ^, v球坐标操作器 polar coordinate manipulator" ?) }: @. s$ i- `' i% W
燃点 spontaneous ignition
/ a7 o/ d e1 r热平衡 heat balance; thermal equilibrium ) Y. h$ @! h6 I" P' R S
人字齿轮 herringbone gear, T" j$ G1 `( p d8 W* a+ w6 @
冗余自由度 redundant degree of freedom
" ^/ m% M+ ~( O: L7 t' `柔轮 flexspline
; J% n! T; [. N' a- m' O柔性冲击 flexible impulse; soft shock
/ z! P) }- n2 _3 m柔性制造系统 flexible manufacturing system; FMS9 y7 z1 f0 ]+ Z+ i1 U
柔性自动化 flexible automation, i9 [; ^! P0 v- o
润滑油膜 lubricant film* N1 W, M1 l) H6 H9 |
润滑装置 lubrication device; k) H. K4 I2 t0 p% L& ?' H
润滑 lubrication
- L; o8 |8 g( t. z0 {9 E润滑剂 lubricant/ j, `8 t0 [5 B% v" v. o9 P9 v, o
三角形花键 serration spline
9 O1 V0 s& Y, Q' {. i) a三角形螺纹 V thread screw " W9 o4 r$ K' R/ z# O
三维凸轮 three-dimensional cam6 H5 s& b, [' _/ h$ J
三心定理 Kennedy`s theorem7 E! _* N3 [# B6 i" D# w( @
砂轮越程槽 grinding wheel groove
% ^3 \. p5 n/ a, S/ R" u+ p6 _砂漏 hour-glass) _5 v2 l }6 X: K% u) h0 o" z1 z
少齿差行星传动 planetary drive with small teeth difference/ W0 P' q/ [* E( l6 W$ d) y
设计方法学 design methodology
" ?3 b6 k. h" `( K; {设计变量 design variable
& k8 C: ~6 ^* b I0 f设计约束 design constraints3 F) T% j" S. q l6 [6 h
深沟球轴承 deep groove ball bearing
+ D4 Z6 ]- f, I. Q" D生产阻力 productive resistance) ~% _( o( Z& u+ D. Y0 P0 t
升程 rise
; l8 h" f6 |. ?升距 lift; T- B+ x- k5 T: c* |
实际廓线 cam profile
8 D' i. m# z+ d G4 ]十字滑块联轴器 double slider coupling; Oldham‘s coupling4 k( m5 g+ A: `; ~, i0 N, {
矢量 vector7 p' V, O8 _# G
输出功 output work
: G) Q4 z$ K* d1 g1 ?6 D* s输出构件 output link. v* w3 z: O1 |! ]6 X+ U8 L5 }
输出机构 output mechanism
3 r- I8 n8 ]; r- j( A输出力矩 output torque, ]/ s) `& V! q& o" |
输出轴 output shaft2 i" x1 {, l. D8 T/ @+ d- n4 o# f
输入构件 input link
8 G5 k4 N% r9 J/ G( {数学模型 mathematic model! v$ B4 l# B. E% S/ {$ p
实际啮合线 actual line of action1 `: o6 Q* n: U+ x/ `- G+ _* p
双滑块机构 double-slider mechanism, ellipsograph' Y7 F" ~. z) K
双曲柄机构 double crank mechanism
3 G U0 r' q. d) ^7 Z$ C双曲面齿轮 hyperboloid gear
, d. K- B' P% L+ c1 [- F双头螺柱 studs; U" }% @9 S, ]0 L# A
双万向联轴节 constant-velocity (or double) universal joint
6 p! `; I% n# X5 c双摇杆机构 double rocker mechanism
; G+ C2 N( _7 @- T* D2 R0 {6 e/ f双转块机构 Oldham coupling3 p6 z( M+ u% ]1 v
双列轴承 double row bearing) _; Q; K8 F7 b7 T7 k) Z( s4 Q
双向推力轴承 double-direction thrust bearing
' k0 u1 P! X% [' R松边 slack-side; K/ x3 D! e( y% ?+ c. H
顺时针 clockwise; K0 V$ X2 e$ h' w
瞬心 instantaneous center) Q5 M2 S, R' U( [5 m3 d+ O6 ~
死点 dead point" j3 `- J2 l9 H" q+ {# D3 J2 N0 \$ R. d
四杆机构 four-bar linkage& F3 w( V% H! @6 F3 R- J& Y
速度 velocity4 h9 u: N" E8 p# G! `7 j* {8 C `# T
速度不均匀 ( 波动 ) 系数 coefficient of speed fluctuation
6 x8 @% N5 ~5 K3 j+ |速度波动 speed fluctuation+ P$ b% w! U' S
速度曲线 velocity diagram+ C. ^! D$ h3 u0 W( e* O
速度瞬心 instantaneous center of velocity
5 T( O0 z4 [8 x6 m k塔轮 step pulley
C8 p0 N$ w q踏板 pedal
8 N! U" m, B ~, F4 C% Z: M9 F台钳、虎钳 vice1 C, Z9 [ z6 t& m
太阳轮 sun gear% j# h0 s1 q5 Z0 Z
弹性滑动 elasticity sliding motion
: l" N: A5 V0 `* {4 `! {, V弹性联轴器 elastic coupling flexible coupling6 R6 H- g: V9 J4 u% s, I7 p
弹性套柱销联轴器 rubber-cushioned sleeve bearing coupling
/ j" n8 j+ y- ~ g4 f; ~套筒 sleeve6 ~! c: k8 H c+ T9 O
梯形螺纹 acme thread form
+ V. Y( ~" i, @$ t8 {) ^* \$ t( a特殊运动链 special kinematic chain$ X8 k. I m+ j0 Z/ `' Y
特性 characteristics
4 v8 E# y% M; `* B( x6 i替代机构 equivalent mechanism
. s9 P$ h" c% Q( @9 f& g3 l调节 modulation, regulation
. l+ e: c7 d& x9 b# i调心滚子轴承 self-aligning roller bearing# T8 b$ z5 V; ^* }5 e# `6 P9 {
调心球轴承 self-aligning ball bearing" H* F# P! P6 P: t9 D
调心轴承 self-aligning bearing
_, y/ B! s( g- {% j调速 speed governing
5 _4 W; v( C; n7 l) B+ p' ~4 D调速电动机 adjustable speed motors6 C) `3 b# p! v( {# W% h6 d
调速系统 speed control system( {3 N$ T$ P4 ]6 I. @/ f
调压调速 variable voltage control
- z8 n4 @3 L' t/ I' u3 ~. U调速器 regulator, governor8 P5 o# ^, M. o7 u
铁磁流体密封 ferrofluid seal/ H1 g! j9 e3 d4 R! z
停车阶段 stopping phase$ l. w. p. n/ A" B+ F; W. b1 [
停歇 dwell# Y/ p% U7 a. d" {+ d/ t% `2 M/ |
同步带 synchronous belt
& p3 t% |' [1 }4 _. t% i同步带传动 synchronous belt drive- W0 u/ ]" D+ v! g) ]0 f5 q
凸的，凸面体 convex7 t; @2 x9 J) W7 t X
凸轮 cam
; V# Y1 T, ?# o6 T: N. {3 Y/ D; I v* }凸轮倒置机构 inverse cam mechanism( Q8 T! I( a, U+ n/ `" a
凸轮机构 cam , cam mechanism6 g# k {% V$ D0 }% O
凸轮廓线 cam profile& F h6 O7 R0 W8 c/ m( J
凸轮廓线绘制 layout of cam profile5 {6 J2 N/ ?% A7 i5 \$ ]$ B1 k
凸轮理论廓线 pitch curve
! W1 k' J& A) t凸缘联轴器 flange coupling
: F" [8 e3 c; n4 k9 D图册、图谱 atlas
. v5 Q) {' A, }$ s ~图解法 graphical method
6 }: D% ?( i! J2 g$ w% ]" U( a h推程 rise+ `- ^8 d ]' H; G, V
推力球轴承 thrust ball bearing
; @1 ?% |2 k9 ?8 t推力轴承 thrust bearing2 y! B, ?% o) r
退刀槽 tool withdrawal groove
, C* W6 L* x+ R) E, C3 m退火 anneal
' ~: o% w* f/ g* C% G* r6 G陀螺仪 gyroscope& ]; \1 V7 T2 H l9 k
V 带 V belt7 H2 h6 Q% B" W# Y/ P
外力 external force , b' \$ S' Y9 l% |7 g8 X0 M
外圈 outer ring ( k! p. t! N% ~% R
外形尺寸 boundary dimension2 c0 p6 r! T6 T" m
万向联轴器 Hooks coupling universal coupling
# L9 a6 x, u1 O2 I' u1 J外齿轮 external gear
2 g' r( H d9 h% ?; m弯曲应力 beading stress. p+ U: k; {$ t
弯矩 bending moment
' ^# Y; J* m$ d" p腕部 wrist
0 e$ Z( ~6 u2 I3 I往复移动 reciprocating motion0 b6 |& i( o2 n! a6 O
往复式密封 reciprocating seal% p/ B1 x. X, i7 a5 }, _# \. K
网上设计 on-net design, OND% E4 e: V/ |) `
微动螺旋机构 differential screw mechanism
! d. \! u6 p8 b! m9 b9 D. i位移 displacement
! h" k* U" ^' ] n- B位移曲线 displacement diagram
: x: Z3 f. A2 o" @! i& g8 y1 O8 K7 k位姿 pose , position and orientation( F" r! b# `: H! r; }
稳定运转阶段 steady motion period$ E( O- B+ @: M4 P6 N: O5 m
稳健设计 robust design9 S' W0 f/ G2 f$ H n. P
蜗杆 worm$ b+ S A' i4 I& h$ w
蜗杆传动机构 worm gearing
6 `+ Z! b$ m0 `" U: _$ W) W" q蜗杆头数 number of threads
+ _. X! B+ [7 s7 m" L! K8 f4 }蜗杆直径系数 diametral quotient6 Q/ U# H, K8 }8 P6 [' I" S
蜗杆蜗轮机构 worm and worm gear$ l: m0 E7 Z6 X* C# i5 o. i9 i* {
蜗杆形凸轮步进机构 worm cam interval mechanism4 d F8 U. p" `) Q( x) D9 A
蜗杆旋向 hands of worm, k# D9 @! ]' M6 n! i
蜗轮 worm gear
! o4 U) }( o/ J- W涡圈形盘簧 power spring. R, y" A* i+ m4 o5 B. S
无级变速装置 stepless speed changes devices
2 o* i+ Y% D5 B无穷大 infinite/ H" R/ a1 g7 Q3 y. G3 J, c
系杆 crank arm, planet carrier
* r1 t8 i7 U. F4 ]2 P0 M现场平衡 field balancing ( r/ {) @1 @8 a4 s/ Z- p
向心轴承 radial bearing
0 M4 }# T. H3 [' k! z' ^3 i向心力 centrifugal force' E/ G$ V' T. U0 u
相对速度 relative velocity
5 f7 U8 t& H" R; }相对运动 relative motion
8 U, E* z2 h( h' B/ c9 j- M相对间隙 relative gap
. r- ?5 ^) Z+ t& S象限 quadrant$ {/ s) E6 R2 K8 o0 o+ g2 o
橡皮泥 plasticine
" Z( @ F+ ]' f细牙螺纹 fine threads
, Q! Z1 D, s* d: q5 T) K( Q销 pin9 k2 H$ F9 t1 r
消耗 consumption
1 t5 p3 k, W5 G! X/ ?小齿轮 pinion
0 U- y) t- J( ~; y, B4 S2 \: ?& b小径 minor diameter- D$ h8 V; f7 P0 d0 e3 x/ O: P
橡胶弹簧 balata spring4 U5 n. r" }& K7 X/ [) s. W! i7 o
修正梯形加速度运动规律 modified trapezoidal acceleration motion
. i i- i& k6 h' b# y修正正弦加速度运动规律 modified sine acceleration motion
}, J* [2 c& I- ~' `3 q斜齿圆柱齿轮 helical gear7 x- y% J7 X1 V" u4 H
斜键、钩头楔键 taper key
- P$ `' V$ u# Y7 s# u泄漏 leakage! G. c$ S( i" D% a/ |# A
谐波齿轮 harmonic gear
6 a" D9 u% [; k& ]5 i谐波传动 harmonic driving" R m2 l( `" F# t2 P* O
谐波发生器 harmonic generator
0 s- m6 v( D4 J/ d2 R0 j/ c斜齿轮的当量直齿轮 equivalent spur gear of the helical gear
2 T7 B% N, s& c; w心轴 spindle
* W' f5 D- u3 `+ A: l0 D+ @4 H行程速度变化系数 coefficient of travel speed variation; _* h; O# D# ~: }' I3 v, s
行程速比系数 advance-to return-time ratio
: k* e5 {% p3 p7 b/ s行星齿轮装置 planetary transmission
8 G( i& K O7 Y: D0 S+ G `9 \: w行星轮 planet gear" K( t9 p: [. H
行星轮变速装置 planetary speed changing devices
9 Y; ~0 m! r4 }' u4 P行星轮系 planetary gear train
' |& v5 d' V# y) K7 Z形封闭凸轮机构 positive-drive (or form-closed) cam mechanism) Z# u8 {& @* B+ h' A5 m+ B) w
虚拟现实 virtual reality
7 m, v5 h- ?; {虚拟现实技术 virtual reality technology, VRT( X6 s" r& l& p* W- a$ _
虚拟现实设计 virtual reality design, VRD
8 B3 K7 P! y7 K6 d( E虚约束 redundant (or passive) constraint& j" K, [( T3 G3 q
许用不平衡量 allowable amount of unbalance$ I# Y D/ t* Q1 z( [8 r$ y% K
许用压力角 allowable pressure angle
: f# ^9 v0 m. W" h. B许用应力 allowable stress; permissible stress; m3 ~# i* y" F4 f, l
悬臂结构 cantilever structure1 Z( u* o/ i% O* c1 m5 n
悬臂梁 cantilever beam7 [# K* o3 W- g- }. m3 N- \
循环功率流 circulating power load
) m5 u1 S+ x) V3 X) v) G5 I3 h旋转力矩 running torque# {( a3 f, N2 |2 V
旋转式密封 rotating seal
2 |2 { d* v( n8 ^. u2 | h9 P- p旋转运动 rotary motion
' p, s! g0 J+ u2 I+ ]选型 type selection/ x0 u# y( ~4 p+ `% d
压力 pressure
" D8 n2 f7 Q2 c3 T/ D压力中心 center of pressure
+ i& {6 K- e$ a压缩机 compressor
8 q: ?& W( k. k1 ]" N压应力 compressive stress
6 X% G& g, N! ^! W* [% Y; h压力角 pressure angle
6 w2 o( Q/ r( l. A8 f. m! y6 h' ?牙嵌式联轴器 jaw (teeth) positive-contact coupling' X1 a9 A+ i3 k2 \
雅可比矩阵 Jacobi matrix; _$ B" S- `, [/ e }
摇杆 rocker
5 h, D( o. U7 G液力传动 hydrodynamic drive
* t8 U* G4 T/ b$ V# w液力耦合器 hydraulic couplers
. A" v& n, C: m4 F: I1 D1 u1 V3 S液体弹簧 liquid spring
) P! X" P: z- n液压无级变速 hydraulic stepless speed changes
: [7 j0 w8 ?9 E% |* `, S3 r液压机构 hydraulic mechanism6 Y* o8 w8 H2 h5 V# M
一般化运动链 generalized kinematic chain
1 z1 ?6 _7 O, h5 J: y移动从动件 reciprocating follower
# m7 `! q+ I0 P. ]4 q移动副 prismatic pair, sliding pair
, w( a5 A0 W+ y0 B移动关节 prismatic joint
& }( O" Z- }. G' R移动凸轮 wedge cam
7 R# q2 J, {. W; P. ?7 ^盈亏功 increment or decrement work- s9 ?( U( P; S. K. c; M
应力幅 stress amplitude. R, l# J% v. s2 N4 [
应力集中 stress concentration
: g3 Z9 V2 i$ L, C) q应力集中系数 factor of stress concentration
7 m- k9 r0 C' v9 t8 g3 Q应力图 stress diagram
: \7 e- X& e, i) h应力 — 应变图 stress-strain diagram
4 T/ ^1 U. k2 I1 ]- L7 s* q8 m优化设计 optimal design
' v8 V. I8 l3 d油杯 oil bottle: F% Y6 G3 e" W3 ?7 B
油壶 oil can* ]* M% X# o3 u. a0 ~
油沟密封 oily ditch seal5 }" i- r+ f J+ f# ?, [
有害阻力 useless resistance6 V; P! Z" u9 I8 K, a F
有益阻力 useful resistance
3 }- p1 @* }3 l$ k+ R- J有效拉力 effective tension; B4 b( ?& T" g% [$ n
有效圆周力 effective circle force
6 r7 x8 p0 b3 Y9 H有害阻力 detrimental resistance
# k2 z6 v3 W! @+ U3 j余弦加速度运动 cosine acceleration (or simple harmonic) motion
, J# \5 w' a% [% J预紧力 preload- Z8 ^1 K E! C0 _, Q V1 F4 A
原动机 primer mover |
发表于 2008-2-21 11:42:15