曲柄滑块机构 slider-crank (or crank-slider) mechanism8 r7 ^+ S2 d: v* a
曲柄摇杆机构 crank-rocker mechanism+ m& y# ]: V v) f" |
曲齿锥齿轮 spiral bevel gear
3 F6 _+ M) b# D9 U* O0 I曲率 curvature! T( ~! u% w" e: R
曲率半径 radius of curvature
/ S1 V( I/ y' I- b2 ]; l曲面从动件 curved-shoe follower' s' P. P% u5 P! j5 o/ L& U: Y
曲线拼接 curve matching% h2 ?, ]% ^: J. _
曲线运动 curvilinear motion# d0 H: l/ {7 X$ |
曲轴 crank shaft. j/ W3 I9 o; w) x5 u% ^" D+ L7 ^' r
驱动力 driving force
7 ?" |; n, k! y- K驱动力矩 driving moment (torque)
5 V# b6 t& h/ E, |8 M6 x9 w5 A. d全齿高 whole depth b6 z* E6 z( ^1 q
权重集 weight sets n# K; D( N3 {% n9 L6 ]
球 ball/ i7 i4 f6 ?( b2 ~: N) z w
球面滚子 convex roller4 _' B4 a# K3 C
球轴承 ball bearing- t/ j. ~0 u" P1 h
球面副 spheric pair, l# T/ e7 m2 Z% V# Q2 C
球面渐开线 spherical involute
3 q7 S. N; ~. u- {, o球面运动 spherical motion) K `, f/ R( j) [2 X
球销副 sphere-pin pair
" ~! D! {% w C+ k球坐标操作器 polar coordinate manipulator1 [8 _9 L( u6 d3 g( W/ R1 ] U5 t5 {
燃点 spontaneous ignition C% p8 C6 y% W7 F* F% w
热平衡 heat balance; thermal equilibrium & T+ s2 e$ M# y8 X' J* s; d' R
人字齿轮 herringbone gear
& p2 D' |# L- j* Y+ b冗余自由度 redundant degree of freedom
! t5 K+ W6 @9 r# l* _* `柔轮 flexspline
( F2 x+ Y3 v) l+ n$ r- r柔性冲击 flexible impulse; soft shock) F6 R' s; Q3 }1 A% o6 T) f! {
柔性制造系统 flexible manufacturing system; FMS* U! e) ^8 g1 V5 y4 f7 d
柔性自动化 flexible automation
* V% U6 c$ A3 d5 u润滑油膜 lubricant film9 u1 A+ C! g: U* g# y! v
润滑装置 lubrication device$ g3 f% E( s8 G9 N9 l: f7 P! h
润滑 lubrication
. h. M* Y- g( U( [) y润滑剂 lubricant
. V% o* Z |4 a0 M三角形花键 serration spline
8 [, q& h7 i( B2 U三角形螺纹 V thread screw 4 A" [1 k4 P* C
三维凸轮 three-dimensional cam
5 z" a$ }+ v, M' H3 S三心定理 Kennedy`s theorem Y# _% j' I3 l- t* j
砂轮越程槽 grinding wheel groove
; T# c: L4 _; P% S. ^- p砂漏 hour-glass
' K) H7 h8 {( i- V! r- ^少齿差行星传动 planetary drive with small teeth difference
/ R% W! ?1 A/ n; j9 G6 g设计方法学 design methodology
4 O- _2 ^5 p' `7 W1 @0 f设计变量 design variable
* I/ z% f$ h+ N6 K' Y w8 P设计约束 design constraints" I ~: E/ E! O
深沟球轴承 deep groove ball bearing1 k4 I% v" T& e- b' }% a6 s1 ?
生产阻力 productive resistance
0 n5 h( s" p P0 I' e5 U$ H+ \5 m+ V0 ?升程 rise
* x$ H0 }1 B& O: b升距 lift6 ^# X" ^8 m; x+ m C
实际廓线 cam profile7 D& Y: J- C# s* j. \5 l
十字滑块联轴器 double slider coupling; Oldham‘s coupling& D! ^ K) T9 T7 @
矢量 vector
0 b8 }3 o% e/ o8 }& n输出功 output work
' l v w7 U& P% f9 ^输出构件 output link5 J ^- A! m5 \9 z4 {5 m3 V) `$ P
输出机构 output mechanism+ P4 N* E6 l/ w: }: [
输出力矩 output torque7 ?8 |8 Z1 H E& I
输出轴 output shaft
4 @' h# k- K/ P$ Y9 A输入构件 input link
* v Q- \. W0 e( t" k. h. N* B& }5 o8 Y数学模型 mathematic model
. x4 K& Z2 l6 K% j8 r实际啮合线 actual line of action
U/ p7 n/ ?! i8 {双滑块机构 double-slider mechanism, ellipsograph
) E* s4 Y' k s" A3 X# Y# A v4 {双曲柄机构 double crank mechanism
# `, t2 k( P8 y5 q' J$ t9 }8 p双曲面齿轮 hyperboloid gear
! F# U; @- G: e% l6 I0 I) B双头螺柱 studs9 y6 _* @" ?6 ]
双万向联轴节 constant-velocity (or double) universal joint9 b n9 {! d+ E, ~; m: ^. j7 @
双摇杆机构 double rocker mechanism B: I! T. a# C7 {: g( ~
双转块机构 Oldham coupling
" v0 X6 N C- H4 D1 t; w双列轴承 double row bearing9 r( d9 J! r1 u% Y6 p
双向推力轴承 double-direction thrust bearing
' K6 S8 n k) O/ G& \4 y( ^松边 slack-side
* T; n# L6 K' m1 U6 ~3 e顺时针 clockwise0 S6 |4 w+ U- }$ m1 U2 u9 I# T
瞬心 instantaneous center2 S$ c- C( B. z" \: Z
死点 dead point
- g; J3 C* V* t# i0 L: N; I5 x四杆机构 four-bar linkage- U, w3 M% A8 B W7 e# Z: f
速度 velocity
[2 I1 X: R& p' i8 O速度不均匀 ( 波动 ) 系数 coefficient of speed fluctuation0 w) T% c3 `- U# t
速度波动 speed fluctuation. f" `. ?. i3 a, ~" } n& q) y' \
速度曲线 velocity diagram
4 J9 z' M x0 d1 a4 c速度瞬心 instantaneous center of velocity: l/ E' q6 n: ?+ y* I
塔轮 step pulley / O6 ?2 k; U+ O! T3 P. \3 s, Y9 ~( A
踏板 pedal
$ G: k2 T9 g B3 n/ W$ A& z台钳、虎钳 vice0 o4 |$ i$ Y; q) c6 H
太阳轮 sun gear
1 E0 d5 }' f0 G7 V1 Y e弹性滑动 elasticity sliding motion
, l$ j$ C' q% S% B; }3 U$ S弹性联轴器 elastic coupling flexible coupling8 z8 Z) a5 u1 O
弹性套柱销联轴器 rubber-cushioned sleeve bearing coupling$ i! d* V1 L& W/ w
套筒 sleeve- f5 M* Z* n* y# I
梯形螺纹 acme thread form8 R0 S n; y" R3 E% }. l
特殊运动链 special kinematic chain9 Q6 V4 M. K i+ M( h, Z$ {
特性 characteristics9 Q5 f3 i! ]! P+ [7 A
替代机构 equivalent mechanism
! [1 E2 U. R$ B8 r9 \# o调节 modulation, regulation
: l7 F0 u9 e0 g, u+ W; @( e. I调心滚子轴承 self-aligning roller bearing
0 g* N; x8 r/ G5 q: H' e9 u调心球轴承 self-aligning ball bearing1 f, m! l3 E# P# y3 F( g
调心轴承 self-aligning bearing7 ?$ [0 r1 M4 u/ b) c) G& D
调速 speed governing0 j# R% T& ^6 \+ x) H# g4 |$ h4 b
调速电动机 adjustable speed motors
+ J0 w% l: w: Y% n8 p调速系统 speed control system& o# F f9 B' o2 I+ b @& H
调压调速 variable voltage control; z( Z9 a) @9 b0 s" I4 @
调速器 regulator, governor
! [( s3 A% C' _6 q, B铁磁流体密封 ferrofluid seal
5 m5 E% ^* q! p5 Y: c& T停车阶段 stopping phase% m, e- \2 F1 c
停歇 dwell+ e3 ^3 m' Q1 ?3 |
同步带 synchronous belt( j o3 W8 u F& _
同步带传动 synchronous belt drive# p3 R# f8 y7 ?* R8 D2 _
凸的，凸面体 convex0 C7 m+ S* [4 O5 B1 T
凸轮 cam4 t! B' @8 B9 X# G4 _9 f) q. M
凸轮倒置机构 inverse cam mechanism4 M/ c& } I H+ J; O
凸轮机构 cam , cam mechanism
! F/ V6 N/ M* v9 H8 I7 s凸轮廓线 cam profile
+ x f: Y% O' h1 C凸轮廓线绘制 layout of cam profile2 e1 T- J2 ^) M
凸轮理论廓线 pitch curve
8 x0 l* @# H# ^. u; @. T' F凸缘联轴器 flange coupling4 x' _: H4 A |( O2 i' \/ }& x7 o
图册、图谱 atlas
4 T3 r4 F5 {) f; t: m3 _图解法 graphical method3 ~3 `- l: _6 Y- Z0 Z, z( b3 Q
推程 rise& C" l7 q- R2 D3 v: S! {
推力球轴承 thrust ball bearing! [0 W# v2 ?0 C4 r% C
推力轴承 thrust bearing8 A+ X- v, w5 W1 b; e# ~
退刀槽 tool withdrawal groove
4 T0 C' m+ X% _) Z9 N# @+ J7 K2 r8 p, \退火 anneal1 y E7 h% F' n! K
陀螺仪 gyroscope
1 x6 Q# Z! u! ^, n6 E& @# WV 带 V belt
[( e8 |- _ `外力 external force / q( a- c; Z" G) L; ^% y
外圈 outer ring & N8 z, {& e+ i
外形尺寸 boundary dimension
3 R5 V$ E0 A+ L# H! ]. N万向联轴器 Hooks coupling universal coupling4 d7 [5 q4 W- [6 l
外齿轮 external gear
+ s0 V7 d5 @) g! b+ s' ]% u* ~, i$ P6 X弯曲应力 beading stress
6 w p0 m( y% ], i1 J弯矩 bending moment7 T( ?7 c: E+ T8 ~* V
腕部 wrist
/ C( X6 v, L! E* B, ^ B: E/ {( }往复移动 reciprocating motion& ?; F, m7 |6 ^* g
往复式密封 reciprocating seal2 w' V# c1 Y7 `4 u7 E7 o
网上设计 on-net design, OND
; y' v2 j! P! h2 ~4 {微动螺旋机构 differential screw mechanism5 c$ i! K2 d, L
位移 displacement. O& M1 p" |/ Z7 N" i
位移曲线 displacement diagram
2 U3 d4 a" m% n" c位姿 pose , position and orientation
; ]) c2 `- U3 ?- _1 V) O. v稳定运转阶段 steady motion period
' M" R G1 z7 ^6 {: o7 p+ ]稳健设计 robust design9 D6 ~; ]; [! X# Y2 g* p- s4 b
蜗杆 worm: F% d* ?2 ^7 v; a% C1 t1 D
蜗杆传动机构 worm gearing; h0 l( J. U2 n$ x9 |1 r5 s6 o- u
蜗杆头数 number of threads
" R0 h% f( \! s7 X) t7 d- ^蜗杆直径系数 diametral quotient
4 f7 s+ H2 P; v7 A; F蜗杆蜗轮机构 worm and worm gear, [9 O! F5 m p( i' ^
蜗杆形凸轮步进机构 worm cam interval mechanism
) p8 J, {8 D9 E* \. n蜗杆旋向 hands of worm9 U" ]4 R& X4 P
蜗轮 worm gear
; r' W1 [' r; k涡圈形盘簧 power spring) H! z9 _1 y m& ]1 M( a+ ]
无级变速装置 stepless speed changes devices
" n: B! k. ^1 i3 I- h无穷大 infinite
! X4 {4 E& `( L系杆 crank arm, planet carrier * c+ `/ X% Q& `% z8 @" N$ X
现场平衡 field balancing 4 v4 l4 k% [: R1 n" r
向心轴承 radial bearing
7 Y4 d9 W0 E9 Z+ M, t6 k向心力 centrifugal force5 b3 E5 _. U- E
相对速度 relative velocity3 l9 Y( ~3 U. r; W* e) X8 K% }
相对运动 relative motion& N5 M/ _' i. j( p3 Q% y
相对间隙 relative gap
8 [* |6 y& g8 p( |$ y( U) w; f象限 quadrant" d4 F3 ^4 z- i8 L y
橡皮泥 plasticine
k3 u; w9 ~+ w0 Q, B, X* p5 Q' t细牙螺纹 fine threads
/ w9 d8 m$ l1 W+ n销 pin: C b- H8 e: A, r' r! d
消耗 consumption. k3 j+ N# s4 K* f2 h
小齿轮 pinion
' e) o9 Y& @( h小径 minor diameter
$ r6 e+ I0 O6 X. P5 u% F' q, ?橡胶弹簧 balata spring
$ u3 q, T+ U2 N. m修正梯形加速度运动规律 modified trapezoidal acceleration motion
* _1 i }7 ^* N6 F修正正弦加速度运动规律 modified sine acceleration motion
+ H' {: J% V, ? D) l斜齿圆柱齿轮 helical gear
5 x; T( p, I! F7 E% D; y/ K斜键、钩头楔键 taper key
: d/ S( ]. E' w泄漏 leakage* r6 w0 S- I+ _6 q
谐波齿轮 harmonic gear$ N, [/ [% g: u, c- h1 a$ q1 f4 ?4 }
谐波传动 harmonic driving
& ^" l! v. X1 W: A谐波发生器 harmonic generator8 [. x* l7 b- x
斜齿轮的当量直齿轮 equivalent spur gear of the helical gear# b5 L& k3 N/ C; M3 a$ u- J% o
心轴 spindle2 Z$ u+ Q% c: u: U6 |$ ^ a% h
行程速度变化系数 coefficient of travel speed variation
/ }" M# l1 e5 i) e2 I# g& U# c- k行程速比系数 advance-to return-time ratio; B* z3 G1 v& V% g8 [7 d7 A
行星齿轮装置 planetary transmission
8 |' J9 C, q( t5 h @' l, L: P行星轮 planet gear
# E' R5 P {5 ?) v$ F7 t5 u行星轮变速装置 planetary speed changing devices
. K! D+ W& @# ^# R: V行星轮系 planetary gear train- N) i" T3 m, ^' @* U* R2 J% ?7 k
形封闭凸轮机构 positive-drive (or form-closed) cam mechanism
7 ~( i/ |( w) b2 m+ b7 w, J2 _# T1 U虚拟现实 virtual reality
* u- A% ?, q- ?虚拟现实技术 virtual reality technology, VRT+ H7 O8 G3 R/ u- o k- \/ g' G$ r( w/ z
虚拟现实设计 virtual reality design, VRD$ f E; P9 `9 ]: l+ l- c
虚约束 redundant (or passive) constraint
' S. X7 w b% |; `许用不平衡量 allowable amount of unbalance
8 R4 Z1 Z- |6 a/ T许用压力角 allowable pressure angle
5 V, n' h6 i! G: D' u许用应力 allowable stress; permissible stress' F, ]: t8 b% x) K) S/ C. Q
悬臂结构 cantilever structure
' @6 R* M& f1 b' ]悬臂梁 cantilever beam) v6 H2 ]2 {' Y" t7 P7 H
循环功率流 circulating power load
7 |6 l5 [2 A, u( \旋转力矩 running torque
. D% Y' y5 W0 `旋转式密封 rotating seal1 j* t& f" {& W2 Q
旋转运动 rotary motion) E, E3 Y' y. n2 y4 g; w, S' |* ?0 ]
选型 type selection
7 C! W( {5 ^$ s& W压力 pressure , @" v! I- j; l* |; R, j9 x
压力中心 center of pressure 1 M- |; B6 F$ A4 B
压缩机 compressor8 R0 q" d2 @2 W( t, L) r4 l( k
压应力 compressive stress! `0 U: d3 c% l+ [* M
压力角 pressure angle
* K& n4 F# S& [/ o% P& b牙嵌式联轴器 jaw (teeth) positive-contact coupling
" ~, j1 l# o3 T& \雅可比矩阵 Jacobi matrix
9 A3 j/ f, W9 e$ O摇杆 rocker
6 V8 T$ P/ u& C# k7 \液力传动 hydrodynamic drive
' w8 [0 M* e' w( N; G7 q液力耦合器 hydraulic couplers
4 F8 \$ ^+ \* `液体弹簧 liquid spring6 D) ^! V [* V( O! Z; U6 h S- q) W
液压无级变速 hydraulic stepless speed changes
' K$ Y' u( w) }: h+ L* s/ n液压机构 hydraulic mechanism
x; o7 \. Q- B6 U+ Z一般化运动链 generalized kinematic chain2 C: Z6 ?& ^5 _ i
移动从动件 reciprocating follower$ B$ F1 y- R3 `6 K- r+ T' k
移动副 prismatic pair, sliding pair
$ D0 @7 H! M* p& g# }移动关节 prismatic joint
- b' W/ C; c1 ?- _移动凸轮 wedge cam
/ ^' J; g; r2 H盈亏功 increment or decrement work
, H( ^6 H8 e- ~; z1 j) l应力幅 stress amplitude
i- c0 t7 u2 i* i应力集中 stress concentration* y K8 F9 m) C. j
应力集中系数 factor of stress concentration9 i. ~* _0 w- z6 L% @
应力图 stress diagram0 B: b! ^& g' N3 ~! ^, E
应力 — 应变图 stress-strain diagram7 ]1 O ^) t" ?7 x' C6 @4 P
优化设计 optimal design
! c8 u+ w+ d' i3 ^油杯 oil bottle
w& _# g8 N7 ^3 w% v; ?油壶 oil can
: P+ S2 A0 H& T4 k: F油沟密封 oily ditch seal
0 @4 {6 g# m4 g0 B, F- D有害阻力 useless resistance
, q1 O5 C S2 a有益阻力 useful resistance
! _0 T5 O2 y" d% D6 q- c; }有效拉力 effective tension
& `, t+ l& {% [0 l有效圆周力 effective circle force3 R; p( h1 l: h! ^
有害阻力 detrimental resistance5 m6 g' O1 {( q2 T
余弦加速度运动 cosine acceleration (or simple harmonic) motion
8 p' ^. D% H9 ^, P! t5 i预紧力 preload( T6 B4 F5 J$ W6 q% p( O: x! r
原动机 primer mover |
发表于 2008-2-21 11:42:15