曲柄滑块机构 slider-crank (or crank-slider) mechanism) O7 h2 k- A1 o8 ~7 o9 A. t0 O
曲柄摇杆机构 crank-rocker mechanism
/ f1 B9 p; Q! k- t曲齿锥齿轮 spiral bevel gear
N# E% o1 ]$ [" }曲率 curvature3 i/ Z; E9 \) g2 ?8 {
曲率半径 radius of curvature: o/ J+ k4 e3 ~
曲面从动件 curved-shoe follower
4 A+ s8 W1 W% E3 `曲线拼接 curve matching9 F' J( U* O8 }7 K
曲线运动 curvilinear motion
/ ^( N! a8 k0 x3 ^曲轴 crank shaft
, Z! p, m! v$ D" J& l, I# A4 I0 ~驱动力 driving force) J9 P' c5 i/ Z) H7 A
驱动力矩 driving moment (torque)
2 g8 j5 G3 k5 d3 g全齿高 whole depth5 K2 t7 F6 |+ J9 V# h8 |
权重集 weight sets4 i% w1 V, `! A; O
球 ball
/ Y6 B1 V1 b+ m2 _. M球面滚子 convex roller
8 Z% D; J1 K8 ^, n球轴承 ball bearing
8 c8 e* @) O2 t9 o1 }球面副 spheric pair
3 N& E( `9 f$ ?& H球面渐开线 spherical involute
) V9 |; z+ w. k- K球面运动 spherical motion
* P5 C- q# ?& q- b球销副 sphere-pin pair, M6 _0 i& x; g
球坐标操作器 polar coordinate manipulator
6 `- n v. u# T1 ]+ @; N燃点 spontaneous ignition
1 w- g, z! G* f热平衡 heat balance; thermal equilibrium
1 i3 S% ^6 T3 k5 O) `& b5 |, W0 x人字齿轮 herringbone gear
C: X( j9 Y$ O2 F冗余自由度 redundant degree of freedom9 q- G4 S# J9 p/ ?: ]
柔轮 flexspline3 K1 Y* [8 [' n3 g2 o6 l' g- ?, ~
柔性冲击 flexible impulse; soft shock
9 H {! ? Y# o+ r/ t2 R柔性制造系统 flexible manufacturing system; FMS; \6 g! ^! W+ K! [$ Y
柔性自动化 flexible automation; K7 e# ^6 ?' B
润滑油膜 lubricant film
& O% X/ y3 r+ g, v润滑装置 lubrication device, B8 q2 @) \7 [0 r2 N, ]- ?* D
润滑 lubrication; D2 o6 ~/ Z/ z J6 a9 E
润滑剂 lubricant5 x5 }1 ^! F6 T/ ]9 u5 ?! K" F
三角形花键 serration spline
' w$ s1 P! p J3 }! X3 V三角形螺纹 V thread screw ' [% b0 z- G1 w3 v3 O% t( I3 n
三维凸轮 three-dimensional cam
- N0 _8 b3 e& R* t. K三心定理 Kennedy`s theorem6 {/ e3 o7 Y2 \% m4 Y
砂轮越程槽 grinding wheel groove) P- ^( n% b4 a+ p6 x) e9 L
砂漏 hour-glass0 N$ j4 w X6 c$ D
少齿差行星传动 planetary drive with small teeth difference
4 f0 W* y; X, Q# d0 g# S0 D设计方法学 design methodology
# W3 ^& S$ @ R, @ v y6 k: i! Y设计变量 design variable# W2 x0 d1 [- l
设计约束 design constraints
0 H8 w' r# y2 J6 o( \深沟球轴承 deep groove ball bearing. g/ Q' h3 H$ F2 ^" p4 Z
生产阻力 productive resistance W6 V5 m) A! E, Z9 Z
升程 rise4 A) Q2 \ q' f7 G; i, i6 x
升距 lift. l: i2 F* Y6 _% _
实际廓线 cam profile
. l: }7 i, l- @, x# x0 D6 ~十字滑块联轴器 double slider coupling; Oldham‘s coupling
$ H, a2 @' e/ l矢量 vector
# K" X7 h. d* x* {输出功 output work8 O7 ]( L4 A! g8 e
输出构件 output link' D9 v% w$ ^8 y2 w- N2 c% v& k
输出机构 output mechanism
5 M3 `7 b8 J$ D9 e T) z* \输出力矩 output torque
E: S0 p& S7 g$ c: R. @2 S输出轴 output shaft
( c) }$ g n8 i% \, Q; v& B& p1 N输入构件 input link0 ?& z* X1 [0 `
数学模型 mathematic model
* u9 \+ F: X+ {% e实际啮合线 actual line of action
& [9 l1 ]. Y9 p8 \7 d- Z4 n双滑块机构 double-slider mechanism, ellipsograph8 l$ C7 \* o* J! P: w
双曲柄机构 double crank mechanism% z( K; @' T5 Q
双曲面齿轮 hyperboloid gear$ `: G0 U2 ^! L
双头螺柱 studs
@- n" U. Y' r8 G- q3 O双万向联轴节 constant-velocity (or double) universal joint: r; s# R. d4 f3 f
双摇杆机构 double rocker mechanism
& s2 D- V ?% ^ |5 }; L8 H3 D双转块机构 Oldham coupling
* F. H4 ]2 ~ {$ ^7 m: J, J双列轴承 double row bearing6 I) d9 k- J2 @2 Q" l9 M
双向推力轴承 double-direction thrust bearing
2 o( b6 j& B9 i ~3 C松边 slack-side h$ t+ q) j+ x9 U9 @9 J4 h2 b
顺时针 clockwise
# X- F) m- ]7 ?. f5 i瞬心 instantaneous center6 E5 U# @5 H& n9 ^) k
死点 dead point
4 G) f! s. I6 e' M! v# _2 J四杆机构 four-bar linkage; B9 y& d( N% L
速度 velocity' l1 A/ J6 X8 X: t( C
速度不均匀 ( 波动 ) 系数 coefficient of speed fluctuation* g ^5 m7 J B# y" w6 U/ b
速度波动 speed fluctuation
5 c& O' Y$ ^* h# E* g速度曲线 velocity diagram
4 F V _% x0 S$ @+ [( n7 e速度瞬心 instantaneous center of velocity0 L- R, ^. t/ _* S
塔轮 step pulley
! t; f) T7 v! y! H$ R. \. n' g踏板 pedal
) K5 [0 X" [% M台钳、虎钳 vice
+ h) `5 J! m+ l太阳轮 sun gear7 R) y0 q6 X# F7 w6 M# z U0 A
弹性滑动 elasticity sliding motion( F- m5 A4 O- _
弹性联轴器 elastic coupling flexible coupling' _. N7 ?+ F6 b* m0 w+ G2 f m
弹性套柱销联轴器 rubber-cushioned sleeve bearing coupling/ k, e1 ]( T6 {1 W
套筒 sleeve
- x- H; n" u" m$ O梯形螺纹 acme thread form
0 @' N. u( O. |8 P) e$ b特殊运动链 special kinematic chain! B |6 c; J& }
特性 characteristics/ I) U4 g/ l: e. [2 W
替代机构 equivalent mechanism
- ?* ?# D: B0 H% n' O0 l: W调节 modulation, regulation
4 h( e; X% x" s' o$ Q) L调心滚子轴承 self-aligning roller bearing- \" E9 Z; B: K1 U: ~0 Q, n
调心球轴承 self-aligning ball bearing0 `( A! O* e4 a9 F+ M: z( f w
调心轴承 self-aligning bearing9 m) N5 n: Y \6 M! F2 _1 _" |
调速 speed governing
" B/ G6 \* _$ @/ E$ s调速电动机 adjustable speed motors
H7 U$ H' J4 F调速系统 speed control system
; Z* H" i: h( n调压调速 variable voltage control* k$ N3 r6 h9 P# ]3 J
调速器 regulator, governor& d+ S' X/ E u8 j1 m4 b
铁磁流体密封 ferrofluid seal
# ^# l& R2 ?7 _2 i K停车阶段 stopping phase3 Q) k! H- t& Q# d
停歇 dwell
3 p* h, N9 j9 H2 |8 u, U' m0 X同步带 synchronous belt
: C- Y; ~8 U8 w同步带传动 synchronous belt drive
. R1 A+ c( ^2 |! Y3 O- {凸的，凸面体 convex
9 p3 b7 {, g1 \凸轮 cam
& i" a6 d4 ~) l3 O- d) N2 I8 q/ z凸轮倒置机构 inverse cam mechanism
: t9 ^. p' x1 j) M) z9 q凸轮机构 cam , cam mechanism
6 P. ^) G: E" v% y2 t, n凸轮廓线 cam profile& C3 h) E1 k$ Q% K
凸轮廓线绘制 layout of cam profile1 K$ {" ^$ n7 T( o
凸轮理论廓线 pitch curve
1 c0 X4 \7 ^; v0 b) M" b5 V凸缘联轴器 flange coupling6 p1 d0 O9 D2 \9 i5 ^) f
图册、图谱 atlas
9 Z: t! o0 C! R3 l# q$ R. a图解法 graphical method3 a# x$ M* G+ Y* Z8 Y
推程 rise
/ O' X, p9 w3 e推力球轴承 thrust ball bearing M8 l* p9 X( l
推力轴承 thrust bearing
! ^( {2 u: `/ c2 a退刀槽 tool withdrawal groove
( G. h6 a' N1 L: W- D( Q% n+ y; ]1 }退火 anneal7 K1 v* k$ [- W; k C' x1 x
陀螺仪 gyroscope# o- U) p* N; h
V 带 V belt( m& [: U+ a+ E- l' n9 G( a; D( U
外力 external force
; q2 f p2 t4 e0 P外圈 outer ring
{( y- U! m* b3 e外形尺寸 boundary dimension
3 r) M S/ b D" f& ?! ?! F万向联轴器 Hooks coupling universal coupling' u/ B6 L) f6 |/ i; ~. z H
外齿轮 external gear
( q' R; c' k; X5 Q# ^0 ^; e A弯曲应力 beading stress
' ~7 r, u# x* p0 @) I8 J2 P弯矩 bending moment4 `& C: R. r# @' X* E5 ^9 c1 I: L2 v9 n
腕部 wrist# B( S, M% \5 x* K1 Q7 t
往复移动 reciprocating motion$ r0 Y8 a6 _+ C9 X& g1 O
往复式密封 reciprocating seal
( L. E" N6 S# M网上设计 on-net design, OND. R1 G7 ?! Z9 l9 ]
微动螺旋机构 differential screw mechanism3 A4 d- w2 m6 b
位移 displacement5 O! M+ Y) d8 W4 ^/ x0 Z+ V
位移曲线 displacement diagram
$ Q9 J' L7 k9 I7 `6 Q位姿 pose , position and orientation" ?- ]( c2 C9 B
稳定运转阶段 steady motion period
+ n3 d' \& \. T Y& b; i稳健设计 robust design; D+ X/ |9 R A/ ]! l
蜗杆 worm
& ^0 U% A6 f9 i2 g& n, i1 C! H蜗杆传动机构 worm gearing5 b4 g" w& O" [
蜗杆头数 number of threads% C$ h1 h& g$ D% W" c2 q9 s
蜗杆直径系数 diametral quotient
+ l2 H! r! X- i蜗杆蜗轮机构 worm and worm gear
7 |# O- J, ]3 @& q蜗杆形凸轮步进机构 worm cam interval mechanism( e; A: [" h( J
蜗杆旋向 hands of worm
& d: x$ Y/ ~% f0 Y蜗轮 worm gear
' q% k, {$ X9 F) A- }6 K* Y/ x涡圈形盘簧 power spring
9 o3 o# ]% @- `/ M L+ ]无级变速装置 stepless speed changes devices# g: B( G' \! u8 `9 [
无穷大 infinite
+ a! {& K% x% k系杆 crank arm, planet carrier
# [) }$ D5 Q* n7 h# ?% Q6 q现场平衡 field balancing
- F" p3 S! s# |2 L向心轴承 radial bearing. J3 \3 z1 x# y: G
向心力 centrifugal force% q) r0 T0 U, c
相对速度 relative velocity
3 R _' ^) C+ b( C% b/ r% w: e相对运动 relative motion ~ Y9 c8 D; m) q; V* q7 R s
相对间隙 relative gap
) E+ ]" O0 I0 f+ V& }. i. }& M象限 quadrant7 }- `3 O" S$ t9 B$ G* h
橡皮泥 plasticine
! v; y3 R4 q& _6 r4 d6 t( v细牙螺纹 fine threads3 f- W4 g2 F/ N0 q/ t+ Z, C( S }
销 pin6 x+ L# F7 g3 D$ V j: F
消耗 consumption" T, y0 t/ ^$ N$ z1 V* f, o- T
小齿轮 pinion! z1 e2 y) ^9 d$ s; o! H
小径 minor diameter% Y$ x& F1 ?7 }! c- v2 u
橡胶弹簧 balata spring
6 H1 Q) p2 H D修正梯形加速度运动规律 modified trapezoidal acceleration motion2 x [/ p9 q& ^0 l7 a
修正正弦加速度运动规律 modified sine acceleration motion
, _; Z, a& y. k/ G斜齿圆柱齿轮 helical gear* ^, O; Y: T( Z9 w' B3 N1 r* h
斜键、钩头楔键 taper key, }5 |! K; W }
泄漏 leakage7 ^2 i* N. ~, S2 E: \/ V
谐波齿轮 harmonic gear
- l: h4 f) L2 s6 ^谐波传动 harmonic driving# z; ?& ?& O% v9 h3 I3 o
谐波发生器 harmonic generator) a p, V5 u H- d) m9 R
斜齿轮的当量直齿轮 equivalent spur gear of the helical gear7 P6 o' Q* C/ Q& d
心轴 spindle/ O( i# F& i$ [# ?
行程速度变化系数 coefficient of travel speed variation" E$ q0 \0 a/ m4 j7 w
行程速比系数 advance-to return-time ratio
# ~% K u! ]( ^9 d; I) r行星齿轮装置 planetary transmission, K4 l6 E' D, x; ], \' R
行星轮 planet gear
" e5 i4 K* C+ K. w k3 q9 O行星轮变速装置 planetary speed changing devices
- n' h& s& @) y% p* n: V行星轮系 planetary gear train" Z5 E, s) l: M4 j$ P8 [" }
形封闭凸轮机构 positive-drive (or form-closed) cam mechanism* ~- X( ]& }* B r) q* _, ?# `6 l
虚拟现实 virtual reality4 V5 |5 M9 |! Y% v/ C. f
虚拟现实技术 virtual reality technology, VRT7 a4 k2 r( [ ?! |! q, Q0 T
虚拟现实设计 virtual reality design, VRD
X- w/ N3 V$ I( ^7 p; p虚约束 redundant (or passive) constraint* f1 {5 [. i4 M, ?6 G' u! [
许用不平衡量 allowable amount of unbalance2 x) Y' N, J( [/ G
许用压力角 allowable pressure angle
4 B& B. o; l8 I% ^8 w. }许用应力 allowable stress; permissible stress
" T- W; i( T7 E" i, _$ x悬臂结构 cantilever structure* S8 W* _9 `% S6 D
悬臂梁 cantilever beam# r L$ {( E: Z# l
循环功率流 circulating power load% u2 K7 ^' Z& ]/ h, f2 D
旋转力矩 running torque
) P1 l( p$ U# ^) ]) n2 F$ ~旋转式密封 rotating seal
+ ], s; I2 p, F8 G旋转运动 rotary motion
! T$ _4 g; n+ j3 i! g1 {8 S选型 type selection2 x9 [8 c7 q, y( Z8 i7 C! z
压力 pressure - S5 K; R1 W" Y- Z1 e7 f; ^
压力中心 center of pressure : s, A2 d( s/ G+ U6 J# P
压缩机 compressor# {1 s$ S2 Z3 d, H2 {
压应力 compressive stress2 Z4 z. D. k( ~7 p" q% i
压力角 pressure angle
0 V$ T+ @: }4 ~5 }牙嵌式联轴器 jaw (teeth) positive-contact coupling) V! _' c5 i$ z2 [( ?
雅可比矩阵 Jacobi matrix
; E% h! h6 v* L6 k4 r摇杆 rocker
/ ]4 s% m& `6 M# V" f液力传动 hydrodynamic drive
5 X) k4 W% ]7 H7 C& r液力耦合器 hydraulic couplers
7 l$ {9 J1 V- B+ g2 b% O+ C g: x0 M液体弹簧 liquid spring
3 [: o; z- X- }液压无级变速 hydraulic stepless speed changes
2 ]3 P6 {% z u# k液压机构 hydraulic mechanism1 ^' c/ I" [5 ~ x$ R y, K
一般化运动链 generalized kinematic chain& C- Y6 d0 V5 r- K/ m0 S$ x
移动从动件 reciprocating follower3 ~* h/ u8 S6 I7 u
移动副 prismatic pair, sliding pair( L9 J1 A- P! [( L
移动关节 prismatic joint" L2 P+ j: X6 |8 e4 u2 ?# b
移动凸轮 wedge cam
; ^( k% f0 w* {2 a盈亏功 increment or decrement work: D" L8 V. o# s3 @- b# w3 q" k3 O
应力幅 stress amplitude
, j7 C. S: r7 }. d8 }# i应力集中 stress concentration7 {% D% k0 A: _5 v9 T8 r+ L
应力集中系数 factor of stress concentration
5 T* V4 I% V* K5 R! o应力图 stress diagram9 Y4 t. A; L+ ?% Q/ \2 Y5 t( Q
应力 — 应变图 stress-strain diagram
' ^! s. N3 X2 }: U优化设计 optimal design! f9 _, m& _ h5 {
油杯 oil bottle
" O7 z6 O% C8 T) A6 k' k油壶 oil can
+ R: ?1 C) ^7 S3 ]油沟密封 oily ditch seal
?3 h! q* F6 t" s! C有害阻力 useless resistance
1 \' e1 E' A! ]有益阻力 useful resistance. B- c- A* A+ {% Z% ]6 \
有效拉力 effective tension
8 h9 I9 }3 u! ~5 I有效圆周力 effective circle force+ l! a$ ]3 L' N6 I5 S
有害阻力 detrimental resistance y" E! Z2 t7 O
余弦加速度运动 cosine acceleration (or simple harmonic) motion! J& L, d j$ d, q A3 R
预紧力 preload9 g W: |4 b- l
原动机 primer mover |
发表于 2008-2-21 11:42:15