曲柄滑块机构 slider-crank (or crank-slider) mechanism+ B k8 o5 o1 f: s7 w* z
曲柄摇杆机构 crank-rocker mechanism
& v4 f+ |8 n0 [1 @曲齿锥齿轮 spiral bevel gear1 t+ F& F" W1 [1 t* j$ o
曲率 curvature
# C/ J( y& n& [6 m曲率半径 radius of curvature
, {) W2 Q3 m8 V" N曲面从动件 curved-shoe follower s# L' h' i9 U- `8 P+ k
曲线拼接 curve matching
2 N- V6 Q! i5 b. ` O曲线运动 curvilinear motion
( m+ x& ~6 {# N曲轴 crank shaft& M8 Y/ M- A Z) m; I$ D
驱动力 driving force
. o) f2 Y7 C8 x9 E8 z驱动力矩 driving moment (torque)4 q% Y) C, Z [ R7 M
全齿高 whole depth
2 A2 Q. D( g: P. A) P, R权重集 weight sets
: \/ R }# D+ n球 ball
) y u, u* ^$ M8 J8 O" y球面滚子 convex roller
1 N5 L' f9 b/ F4 S( k9 i9 g球轴承 ball bearing
/ F B6 y3 ?- ~# n! q) }' E球面副 spheric pair Q1 H" u9 A, {9 \" Z
球面渐开线 spherical involute
/ L! v) W2 y% r9 U球面运动 spherical motion
! a) V O4 {8 ?- Y3 H6 N+ P8 v9 }球销副 sphere-pin pair% c" C! ]$ n; p m
球坐标操作器 polar coordinate manipulator# l# `- Q6 m! F9 D
燃点 spontaneous ignition
, t. S; C* C, ^7 F; g* ?( S热平衡 heat balance; thermal equilibrium ; W+ y2 t: F+ R/ U" D5 a
人字齿轮 herringbone gear
5 c5 F$ L3 b0 a; U冗余自由度 redundant degree of freedom
# _+ B9 _" _ m; Y0 }7 m柔轮 flexspline
+ r4 c9 V+ B q- q8 ^3 r柔性冲击 flexible impulse; soft shock6 b+ Z) I/ b+ R9 p9 Y" q3 V0 e
柔性制造系统 flexible manufacturing system; FMS, p* y# [" c7 x9 |. A6 u( I; h
柔性自动化 flexible automation
# r3 k& R6 q/ L+ }* b润滑油膜 lubricant film
- ]$ {+ I6 y9 L" N. o5 M润滑装置 lubrication device% s9 J0 [0 K. r7 M; \3 E0 i( D# W
润滑 lubrication2 f2 g7 a7 R6 } K$ @ S& L
润滑剂 lubricant: J, a" O: A' ^
三角形花键 serration spline 5 c I: Z. G) _' C
三角形螺纹 V thread screw
' D( q. @: {9 h# M8 b1 Z三维凸轮 three-dimensional cam
F, o: `; d- u8 M6 {8 M三心定理 Kennedy`s theorem
" i) }' F/ j& u5 z5 P' P砂轮越程槽 grinding wheel groove$ E3 Y+ S3 v2 {' ?# y
砂漏 hour-glass, ^2 N- i! j% n" e1 t3 n N
少齿差行星传动 planetary drive with small teeth difference
% x, t7 h- O* e8 @7 C# ]& w0 m; C6 }% k设计方法学 design methodology
+ }' b8 K7 A5 ?/ I设计变量 design variable
* u" u0 i( M. i# O- @设计约束 design constraints" ?: a( I$ q: i$ K) n, B' O
深沟球轴承 deep groove ball bearing5 P+ B; Z' N" E* T4 \
生产阻力 productive resistance( c: n: W& `' n9 `$ |" F3 H# O
升程 rise
/ Z" i* z# g: f) x+ F升距 lift# D) g% M$ M& r3 b
实际廓线 cam profile
1 H) h3 N) e0 _4 |十字滑块联轴器 double slider coupling; Oldham‘s coupling1 N \# ^/ P4 D7 J# M
矢量 vector+ R" q& N* p& h9 c3 P
输出功 output work' {! u4 b( y( T8 Y
输出构件 output link9 I4 f r; d2 v7 f8 I2 `
输出机构 output mechanism
' v$ j+ E1 R" N: e& m& h3 S输出力矩 output torque) ?' R) D0 K- C/ s& Q" H, D5 ~
输出轴 output shaft
: i' S! P# ?+ ?输入构件 input link( c0 A4 h+ e$ j- x: }9 [
数学模型 mathematic model# T" ~: x+ Y3 U* ?& w7 v
实际啮合线 actual line of action5 n+ G! l6 f. L# e, w
双滑块机构 double-slider mechanism, ellipsograph. v0 R6 }; G( A
双曲柄机构 double crank mechanism
3 H' B! B) C8 f6 a2 ]( o双曲面齿轮 hyperboloid gear
! e& \6 I2 c# ^# x8 _双头螺柱 studs
% z& ]3 p/ i( t1 r双万向联轴节 constant-velocity (or double) universal joint
$ O, ?/ N0 ~$ G- u5 w% q; G双摇杆机构 double rocker mechanism! T; ?( m7 w+ b3 |
双转块机构 Oldham coupling9 [7 S7 V) }( s7 |
双列轴承 double row bearing3 \( }1 M) Z, n# _1 u
双向推力轴承 double-direction thrust bearing7 u+ o1 X7 |; C- V, P5 O" q; {2 d4 T# W
松边 slack-side
# H5 n7 ?! K2 w9 [$ `+ m7 D" S顺时针 clockwise
5 \0 g- s5 r4 o5 ?- r瞬心 instantaneous center' `! H8 V6 T( @, M
死点 dead point( k* @, @; J0 n# ?0 ~
四杆机构 four-bar linkage E; s% v2 Q+ O/ M" n) f/ L" x" B
速度 velocity
4 k2 I1 b, n' G+ j8 Y% H2 ^ S速度不均匀 ( 波动 ) 系数 coefficient of speed fluctuation1 ^% ?3 Q: d0 E2 Z0 Z* x
速度波动 speed fluctuation1 F0 {0 B$ O+ X% Z, p
速度曲线 velocity diagram
7 N( S; L: {/ Z" J2 n速度瞬心 instantaneous center of velocity( i2 P0 X4 R9 T
塔轮 step pulley
- q- ^" x' v0 A7 f踏板 pedal
/ \# p. B2 N; j4 o; b- H台钳、虎钳 vice
6 ?) {9 S, l9 Q3 p0 x1 u太阳轮 sun gear1 o( Z" |$ O \" I# c, o2 z) h2 M
弹性滑动 elasticity sliding motion; l. u7 K/ H, A& P9 x1 n0 R
弹性联轴器 elastic coupling flexible coupling
2 o! d" G! f. a5 u4 E/ C& E0 D弹性套柱销联轴器 rubber-cushioned sleeve bearing coupling
0 p7 [* F* N2 b8 ]2 n: g套筒 sleeve
: x7 U7 L) [3 _1 O& Y. l梯形螺纹 acme thread form$ @7 _! O' B+ X% E2 V
特殊运动链 special kinematic chain; F$ }# q& B5 j4 P2 H
特性 characteristics9 _! p, o+ z* N; t
替代机构 equivalent mechanism; ~4 S. j! l* _( b
调节 modulation, regulation
) P+ Y' N/ I8 Q, G调心滚子轴承 self-aligning roller bearing O: i3 S: L J+ A# q4 P
调心球轴承 self-aligning ball bearing
* l T, l; J) j( h# ^* d调心轴承 self-aligning bearing
- Z* d, D3 I X# t6 T0 m调速 speed governing
+ M H1 t M, ^# p' ~$ I调速电动机 adjustable speed motors- Z8 w* S" m8 _" L6 Q# Y6 k
调速系统 speed control system
* b) B, y0 H7 b: I! W5 G调压调速 variable voltage control
% F! _# A* h. x0 {3 Y( G% n调速器 regulator, governor! G7 U+ {% \3 L
铁磁流体密封 ferrofluid seal
. | G/ A$ R' O; K停车阶段 stopping phase& F& E0 t% E/ k4 j
停歇 dwell
. G& H% N; ~6 E$ S同步带 synchronous belt
. n, `: z0 w; A2 G+ }. W同步带传动 synchronous belt drive$ h5 F; e4 z' S4 _# C! _, B0 B, B
凸的，凸面体 convex* F# H! z% h7 w- A! I* u: x
凸轮 cam
0 J! a, P2 A- L( e: I凸轮倒置机构 inverse cam mechanism
- m' i7 \, `: Z1 `凸轮机构 cam , cam mechanism8 [1 H" v' \& n. c) O
凸轮廓线 cam profile0 c7 k& [9 h6 f$ X, m0 ~) Y
凸轮廓线绘制 layout of cam profile
, X' x: h3 s9 t1 l7 T凸轮理论廓线 pitch curve( i9 \- S) _# N. [/ n7 ~
凸缘联轴器 flange coupling5 L: O! Z4 d! z" _0 Y' k
图册、图谱 atlas
7 u" e3 q. K) O+ Z- w# @图解法 graphical method+ q, \( z& v$ q( a
推程 rise
) j! U, o7 Z+ Z0 C" s8 b* ]7 T推力球轴承 thrust ball bearing
, z( s* C( M! ` a d推力轴承 thrust bearing% S, }/ h4 D$ j3 x
退刀槽 tool withdrawal groove/ i$ m" [1 f$ @9 N
退火 anneal
- z/ P# [7 O9 Y8 U/ C8 r陀螺仪 gyroscope; M/ Z7 d0 I1 O7 I, X
V 带 V belt
0 v5 k) N9 L# r- Q外力 external force ; u6 v. Y7 J D9 c7 P
外圈 outer ring
4 ]# D1 P& F6 H+ ~6 _外形尺寸 boundary dimension
% ^% ?/ _# W* ~. ~. X万向联轴器 Hooks coupling universal coupling8 x# X4 p) |+ s, q8 D- l
外齿轮 external gear
) P% I/ d3 i3 s& ?弯曲应力 beading stress
, u) g$ E1 Q/ e# }4 N% @; f弯矩 bending moment- i1 c. ?' Y3 j# I/ E
腕部 wrist
: Y$ d! c. u- |往复移动 reciprocating motion
/ M6 R, p7 t& ^6 g! {0 {1 L往复式密封 reciprocating seal p7 W U! L6 h, g
网上设计 on-net design, OND l# {$ _. s9 c/ p; A( i
微动螺旋机构 differential screw mechanism
) z; h" i/ N8 j- e+ V( @' [* P位移 displacement
/ B) ~0 L5 K6 b Q3 z3 ~7 T位移曲线 displacement diagram
# a, F" ^* T) v/ J: C/ t4 u) m9 A位姿 pose , position and orientation
6 M$ P+ n0 a! [# R/ m2 d稳定运转阶段 steady motion period
0 A( U! s+ j* _: g稳健设计 robust design( z9 g6 f- @# {' O" G: f4 l5 g& w" y
蜗杆 worm
, w8 p5 E2 l: ]8 k( z5 Y u( z蜗杆传动机构 worm gearing* F* J% Y, `8 O# H
蜗杆头数 number of threads( l1 \' X7 n; g* I2 g6 w1 o
蜗杆直径系数 diametral quotient
6 F! F1 V( p" F2 Q蜗杆蜗轮机构 worm and worm gear
9 c& |; q, p0 k8 |蜗杆形凸轮步进机构 worm cam interval mechanism
7 H9 m8 ^: x0 R2 C( M7 s4 J8 j蜗杆旋向 hands of worm) \- Z9 |( O0 G+ H
蜗轮 worm gear0 N0 P. i! B) f2 y* p' n
涡圈形盘簧 power spring% _3 ~; H% P* y% l8 \, [
无级变速装置 stepless speed changes devices* Z6 ]6 G: L. x" L: G& M6 Q6 \
无穷大 infinite
6 a* D2 y$ @0 B( U) p p5 D系杆 crank arm, planet carrier ' l+ x1 n: Z7 p: R
现场平衡 field balancing ) N3 S* K& e& f* K0 g, ]9 c
向心轴承 radial bearing
$ q4 {' a2 I, p# ?向心力 centrifugal force
# G D7 U3 r! q, Y9 T" y相对速度 relative velocity6 ]6 \3 t z- j
相对运动 relative motion& X: g1 y+ `# n' D! H( s- q1 L
相对间隙 relative gap- d5 q! \8 Z1 R( E
象限 quadrant# D% V. n; k2 g" Q! A8 g9 N B
橡皮泥 plasticine
0 G9 N5 I1 O" W) E: n细牙螺纹 fine threads
3 \) t( m0 R' J( I5 `* l a销 pin
4 ^/ x: I6 g# j' V4 N消耗 consumption6 p$ _( i: T2 G2 r, {) w% n
小齿轮 pinion
$ }" t& s( J( T2 J小径 minor diameter
, j# j. {9 D2 Y: s6 h# y z, b橡胶弹簧 balata spring
' f1 M6 r+ P( k修正梯形加速度运动规律 modified trapezoidal acceleration motion
& _# l2 H& B6 r+ e$ ]修正正弦加速度运动规律 modified sine acceleration motion
" |+ I3 I N' D- J4 F+ C% B斜齿圆柱齿轮 helical gear g" @4 O0 m( Q' f
斜键、钩头楔键 taper key H) q# \$ D2 ]5 S9 T
泄漏 leakage# u& ]& ^! [7 i+ r5 z3 M( T
谐波齿轮 harmonic gear. Q' b! k; q. K! V/ Q
谐波传动 harmonic driving
- o ^0 q, k$ H' I" V b谐波发生器 harmonic generator0 r5 J1 y5 r6 [7 {) G
斜齿轮的当量直齿轮 equivalent spur gear of the helical gear
, b7 `! d2 u3 {; s) x# _/ h心轴 spindle
4 k; `5 N8 A' C8 m3 \行程速度变化系数 coefficient of travel speed variation
& s1 U, h! @( n- ?4 B D, p" h行程速比系数 advance-to return-time ratio/ K! }3 w+ @( @) A* v+ h S
行星齿轮装置 planetary transmission8 n5 e& s( E2 ?3 `; E2 h
行星轮 planet gear. A% F1 X, ?+ V6 z4 S9 ~- M
行星轮变速装置 planetary speed changing devices: k# d! I& Z3 s7 O9 U
行星轮系 planetary gear train& g0 R' ~* u' q$ i. l5 M
形封闭凸轮机构 positive-drive (or form-closed) cam mechanism
, {! r+ k. a7 O+ _虚拟现实 virtual reality* w) \8 U' W1 ?$ W) X
虚拟现实技术 virtual reality technology, VRT
6 X: x ^7 s0 }/ d7 J/ P虚拟现实设计 virtual reality design, VRD
1 \, P0 H& m; y* ` p: E虚约束 redundant (or passive) constraint1 Y2 z- D1 p" Q+ {
许用不平衡量 allowable amount of unbalance+ g9 ~1 ~0 d: o4 q
许用压力角 allowable pressure angle
: b% p1 S# ^1 V3 ^2 b4 `$ \8 j许用应力 allowable stress; permissible stress, y0 v2 E6 W9 l
悬臂结构 cantilever structure
8 m% _1 d5 ]4 }* n r3 ?- A3 _) B悬臂梁 cantilever beam
" e1 \( z& e! ~0 E, _循环功率流 circulating power load% }( p; G4 t2 j4 [
旋转力矩 running torque+ N- |7 l% p) v* ?
旋转式密封 rotating seal
2 E" I) Z9 y% T- z& G8 n旋转运动 rotary motion6 l3 H9 s) J* R1 y4 C" a. ?, G, z6 r
选型 type selection
4 T& s9 b4 H3 M! ]+ h压力 pressure 6 B6 u) ?: G: {: \9 O0 ]; r* ^
压力中心 center of pressure : D e$ X3 X+ m: Z2 B" F$ t8 }* z
压缩机 compressor) [2 H" h5 N7 _, a. ]) M
压应力 compressive stress
, Q/ E( E" ?$ A4 E; L! v压力角 pressure angle6 o( m* c+ o% u
牙嵌式联轴器 jaw (teeth) positive-contact coupling8 q. J! m) N% U% Q0 M2 w- U
雅可比矩阵 Jacobi matrix+ h8 I. v% c1 @1 F9 m* C! @
摇杆 rocker) ?! Q F/ w# l2 ^: ] f
液力传动 hydrodynamic drive
* ]4 O) b+ J7 N7 c9 P5 c; [液力耦合器 hydraulic couplers5 a; e; a5 s4 k
液体弹簧 liquid spring. S& I3 [- y( O( x! u4 A
液压无级变速 hydraulic stepless speed changes
2 u9 k9 v3 ^! J/ l* B' T6 N! k液压机构 hydraulic mechanism
6 B$ `+ s. M: q5 v, Q0 t) S: r一般化运动链 generalized kinematic chain
; w0 i- J A; E9 l6 L: B& z6 O& L) C移动从动件 reciprocating follower- W/ X! i* r d- r/ B8 _4 r
移动副 prismatic pair, sliding pair$ A8 \1 I8 F% T7 p# Y( I* ?
移动关节 prismatic joint+ V7 g# |2 _7 E4 t" j# H3 K
移动凸轮 wedge cam; _4 \4 s6 E. s. C8 n
盈亏功 increment or decrement work) d1 a( f4 i9 b [; m$ u" F3 W9 V
应力幅 stress amplitude
8 C) v" m: E8 f( K* H# T应力集中 stress concentration- A0 w" e. {7 w5 S) e& N
应力集中系数 factor of stress concentration
) ^0 l9 v' h Y" W2 Y& A应力图 stress diagram
7 `8 u, H8 v; d% J6 s2 h应力 — 应变图 stress-strain diagram
0 k2 w5 V, f4 [7 s- i. U( g1 w优化设计 optimal design
) M# o' C' j% ~& h6 Y油杯 oil bottle
. I/ ?( a/ t/ B油壶 oil can6 ^' O+ z* t% x( s! U
油沟密封 oily ditch seal% R. j( o! u' p, E w
有害阻力 useless resistance
8 ^" a3 a6 e* i& i* l3 ?有益阻力 useful resistance
$ q$ D4 N! q' @1 t5 J& R2 V有效拉力 effective tension5 F8 t( i: z* n
有效圆周力 effective circle force
s5 N/ e0 s5 O3 }1 K4 z+ i有害阻力 detrimental resistance+ k! q% R% K5 O! r' o
余弦加速度运动 cosine acceleration (or simple harmonic) motion
7 e% H7 ]5 t0 R; Y5 G预紧力 preload& z" p$ V9 ~6 u# o$ D* O L, }1 w
原动机 primer mover |
发表于 2008-2-21 11:42:15