曲柄滑块机构 slider-crank (or crank-slider) mechanism/ I) F9 R( a9 G$ D4 a2 N" M
曲柄摇杆机构 crank-rocker mechanism3 u' ?2 e: {% G$ w: ?" w8 T
曲齿锥齿轮 spiral bevel gear
; y2 u5 j9 R, H' s8 ^' j H曲率 curvature
! r' m2 d7 X, r2 \6 a曲率半径 radius of curvature
1 i1 }2 R7 J+ L7 T: @1 H曲面从动件 curved-shoe follower
9 s' ~& o. I7 O% @' ?曲线拼接 curve matching4 U2 w+ K( g2 ? T; R, T
曲线运动 curvilinear motion1 }* ~+ n$ M# _- A, w! s4 O) t% F
曲轴 crank shaft/ \- V8 \" M5 N! K% g4 k6 C) _% O9 _
驱动力 driving force$ s; K. \( r( R% j: M
驱动力矩 driving moment (torque)
. z+ D& L J4 Z) e9 Z( M全齿高 whole depth1 G o; A! W( h6 ]; s, N$ b
权重集 weight sets4 N H5 j6 s& p% W
球 ball
9 v, G3 `: B: b, _0 ]球面滚子 convex roller
Q5 ~# x3 E4 l9 x" F I球轴承 ball bearing0 r9 W& c, y% _' K% f4 {0 h, X
球面副 spheric pair! }$ x/ ? E3 z+ V X% p4 F
球面渐开线 spherical involute. v7 {1 f) S" r
球面运动 spherical motion
0 t% x0 \: }+ D球销副 sphere-pin pair
; w8 y \" M E8 s球坐标操作器 polar coordinate manipulator- [1 @, h+ J0 k$ z0 ^6 o
燃点 spontaneous ignition # P) m9 S* s4 n, R0 K; S
热平衡 heat balance; thermal equilibrium
$ l! h( K0 y8 H/ }人字齿轮 herringbone gear n2 s* ~3 o+ W- F4 u! ^
冗余自由度 redundant degree of freedom9 e$ I8 z5 T# ^7 E) V
柔轮 flexspline% v7 i* X7 T0 G7 s
柔性冲击 flexible impulse; soft shock* ?$ r9 R4 r; N2 x
柔性制造系统 flexible manufacturing system; FMS9 B* C( m( ?5 s% @3 U
柔性自动化 flexible automation
0 \% K, ?# q& ~ Y7 t7 N润滑油膜 lubricant film( W" v3 P7 {. X: O x
润滑装置 lubrication device
& V: l0 X: C0 p1 X' F润滑 lubrication
5 [8 u% U2 t8 X) f润滑剂 lubricant
" k9 V- z- D8 `- e/ Z5 H: l8 T三角形花键 serration spline
?2 d S, z7 Q8 }" }' U$ q: _% m三角形螺纹 V thread screw
6 \" ^0 S& v/ }5 h三维凸轮 three-dimensional cam
7 B: x# Q, {8 z9 T三心定理 Kennedy`s theorem& ~5 ]3 H& }+ M* z( z8 [2 l% `
砂轮越程槽 grinding wheel groove7 K* x* g9 U1 {# B8 V+ A
砂漏 hour-glass
2 U4 P. L2 N; M! z少齿差行星传动 planetary drive with small teeth difference& H8 _0 a7 c+ D0 n& L
设计方法学 design methodology
`0 R; r- g l8 w- i设计变量 design variable
( Z$ b3 x T( V# F: F0 i设计约束 design constraints, U- Y5 s; p9 K2 G
深沟球轴承 deep groove ball bearing
2 u. T% ]8 e/ v生产阻力 productive resistance
4 ]8 d5 S! b3 O升程 rise
8 p% d, `; K0 e升距 lift$ ~( F' R7 ?' z, Y9 s
实际廓线 cam profile( W" ^" s! u. U
十字滑块联轴器 double slider coupling; Oldham‘s coupling
% g+ o. b0 a: _1 b矢量 vector c0 i% Q2 _8 l8 q6 E3 Q2 t& `
输出功 output work
" ]# N1 c, w6 Y" G- b4 D, \* ^输出构件 output link$ l: b# i/ d( F' f9 w
输出机构 output mechanism; c1 d* S+ X0 o1 R
输出力矩 output torque# U! `- U9 e4 V! b+ p% R+ P% l
输出轴 output shaft
g N, C2 w9 D M' I" y' j/ _# P输入构件 input link
( Z' u$ x; y* d7 f4 P3 o数学模型 mathematic model
3 u6 e+ f+ v% m. E4 g3 [- L) g实际啮合线 actual line of action
' R3 |/ }1 q" i: Y双滑块机构 double-slider mechanism, ellipsograph) W H+ n B5 e$ l
双曲柄机构 double crank mechanism- Z6 ^/ e! k- x5 \, b; b
双曲面齿轮 hyperboloid gear
% v# v8 \% A4 [& S4 _) C- w0 {双头螺柱 studs0 {& q9 d: N: U) w, ?, w, l
双万向联轴节 constant-velocity (or double) universal joint3 y9 d- Z9 q, V {8 ` L
双摇杆机构 double rocker mechanism
, x/ f9 B# b; B) f- j$ v8 m* j8 y双转块机构 Oldham coupling4 m9 \% N" u3 ?, y" Y8 H
双列轴承 double row bearing
# Q* _0 u/ {% l+ e3 z双向推力轴承 double-direction thrust bearing5 W( g5 V$ O' e9 \# A4 b! D
松边 slack-side
0 \" M1 a" v" M( |/ ~% O1 ^! F顺时针 clockwise
' x' j x& l9 _. n( H瞬心 instantaneous center
, q! S5 ?7 R) u死点 dead point
/ j/ J+ I9 m, A' h四杆机构 four-bar linkage0 Q$ h8 M+ K1 M1 b. L5 F' W
速度 velocity% B$ f v7 ]8 @
速度不均匀 ( 波动 ) 系数 coefficient of speed fluctuation
6 l- G! H" J8 d5 |" \速度波动 speed fluctuation
5 t2 U: A g0 A8 A: {3 t$ @ F速度曲线 velocity diagram
1 L5 u' n& C8 K2 s3 f: C速度瞬心 instantaneous center of velocity
. {' H3 S$ G# a" R$ c# T/ Y塔轮 step pulley 0 E4 y- M9 X" N) _
踏板 pedal
( ~7 T/ C, _1 }8 d4 \9 }3 O台钳、虎钳 vice, s4 Z8 l5 [" n) w
太阳轮 sun gear4 s: \" d( o' P% a
弹性滑动 elasticity sliding motion
9 K% a9 [" W2 Q0 T$ H& h. Y7 y! ^弹性联轴器 elastic coupling flexible coupling- t( d$ d5 {5 _* o1 n
弹性套柱销联轴器 rubber-cushioned sleeve bearing coupling
. _% I; U4 Z+ J1 f. P套筒 sleeve
" g% i0 ]. A. {1 A! G8 H1 m梯形螺纹 acme thread form% l2 p( H6 T! ^! G. Q, |
特殊运动链 special kinematic chain
6 d% { p" Y1 O8 t- Z特性 characteristics
4 Q) ~ Z- s* G6 g% ?% ^替代机构 equivalent mechanism
5 o: O I1 ~. W, e. s9 O# R% a调节 modulation, regulation5 J/ N3 z7 o. t
调心滚子轴承 self-aligning roller bearing
4 a5 n4 m& K# t' j8 t调心球轴承 self-aligning ball bearing
, P" O9 k. ~0 V& w0 |5 o+ k调心轴承 self-aligning bearing( \' Q1 z# m f* \$ M! L' G& b
调速 speed governing
: n# t g4 c! M+ I. y调速电动机 adjustable speed motors4 y8 D3 z0 P3 H
调速系统 speed control system2 x3 L" M) K: e( b0 ? c8 F
调压调速 variable voltage control8 B+ ?+ e3 ~& @+ N0 u! L; w& H% y
调速器 regulator, governor
7 L9 G9 `+ i9 e' i8 N8 G铁磁流体密封 ferrofluid seal0 ~2 W6 \" W! _$ u
停车阶段 stopping phase. c; A+ t2 f/ R3 P! `& w7 D; n9 `
停歇 dwell
. ~. H* N1 Q* V9 U" S1 E+ F ^同步带 synchronous belt
6 v8 B4 d' r" e2 j. P同步带传动 synchronous belt drive
7 X9 @8 R8 H9 @* w凸的，凸面体 convex
1 Y O4 {* l2 x. n- ~) J凸轮 cam
$ u' i) O: ~; T( P4 ~凸轮倒置机构 inverse cam mechanism
# p) g, M4 a7 a2 `! f4 i凸轮机构 cam , cam mechanism
" C, X/ h' e6 ?" {6 Q# a- ~' X3 N凸轮廓线 cam profile% v* q- w' \6 T+ G2 m
凸轮廓线绘制 layout of cam profile
0 p$ M" |4 o3 I% G8 R凸轮理论廓线 pitch curve
( W& z9 D! _, J+ o; T w! g5 r凸缘联轴器 flange coupling
0 ]: D! ^% h2 t6 G+ \# o图册、图谱 atlas
" D7 C; G: g3 p' ]' D图解法 graphical method, ^$ ]2 i# D v! z
推程 rise+ ]% }3 R+ B3 s t1 Z$ Y. u: S$ f
推力球轴承 thrust ball bearing
y8 z# }. Q# |7 `0 S推力轴承 thrust bearing
# D2 {' d$ o3 s6 }9 [ c7 Y退刀槽 tool withdrawal groove4 A7 [! d- e0 z1 n% z
退火 anneal
8 v4 b1 q" R2 ~0 k陀螺仪 gyroscope
8 b) n/ c+ l* ~, M, J) QV 带 V belt% q X5 {' m+ V8 G+ X
外力 external force
% Z5 a* G2 J6 w! U, P外圈 outer ring
. F$ Q- F! k& [; R外形尺寸 boundary dimension
) n+ r$ ^0 o, ~3 c/ o6 I万向联轴器 Hooks coupling universal coupling
3 R: p" |; m) \" q& w3 C) r4 t外齿轮 external gear
% |/ D/ y6 r6 b3 Q+ e弯曲应力 beading stress
5 @, Q+ v/ j' [ r弯矩 bending moment
2 M& O" t8 d+ i. i腕部 wrist4 A; N% ]$ m5 q9 s( o# K( G: `
往复移动 reciprocating motion u) p" T: m# x e$ m
往复式密封 reciprocating seal$ B7 ` O% ^$ w) i
网上设计 on-net design, OND
3 U2 y' z- w" N2 s0 Z4 d. {微动螺旋机构 differential screw mechanism" v) a9 ^8 t% T
位移 displacement
2 y- } j& C; Z. b; f$ T" q位移曲线 displacement diagram+ s0 @! a% z) b# f# s+ I7 R( o
位姿 pose , position and orientation
6 I6 a, |& X6 N稳定运转阶段 steady motion period% D" f, a6 F3 ~
稳健设计 robust design( b8 ?- @, s* O; [ e: t2 f5 v
蜗杆 worm
/ k0 }& l q) n/ @+ n5 c3 O$ s蜗杆传动机构 worm gearing
. y- L$ f& m, V( {( B+ E蜗杆头数 number of threads4 Q6 `5 c+ B4 ?8 t
蜗杆直径系数 diametral quotient
7 S4 I4 I* `2 \$ l0 o1 ^4 }蜗杆蜗轮机构 worm and worm gear
* p' w' o9 u, ~2 ?" N蜗杆形凸轮步进机构 worm cam interval mechanism
/ K8 f) q3 D# s' F* [蜗杆旋向 hands of worm
3 u5 `% i/ f! \2 i/ b% ?; Y蜗轮 worm gear
: L3 o, S' ]7 V7 v涡圈形盘簧 power spring
+ M' Z" D: R( `无级变速装置 stepless speed changes devices# e7 Y) \- A2 G* k" m4 H% t4 S( C
无穷大 infinite
7 g5 Y6 c8 p" F" j7 u! g系杆 crank arm, planet carrier 0 R- I$ b) F% t
现场平衡 field balancing 3 _8 V" T, D8 H7 d2 i7 R% {1 {
向心轴承 radial bearing
0 ?% w1 i4 G$ K& u/ S向心力 centrifugal force
7 E* R- T7 g7 |相对速度 relative velocity6 L: c( _, J+ W9 d( J9 p
相对运动 relative motion0 m- p- H# z7 J+ [
相对间隙 relative gap
- U4 N0 d7 x/ i4 I9 q象限 quadrant J: z$ C" b1 d0 R+ x r6 |0 t0 S
橡皮泥 plasticine2 `) E9 `4 G6 r1 l8 x
细牙螺纹 fine threads/ \3 L" E0 ~. d) C; J
销 pin; x+ h6 Q1 j8 h( R; w
消耗 consumption
1 H. {, m6 r& z) Y* i3 h+ k3 F& V小齿轮 pinion1 F& X8 ?) @: B& o
小径 minor diameter' T* a& @. Y% t# k# ^/ ?, o
橡胶弹簧 balata spring
; e2 J2 a4 I3 M0 {修正梯形加速度运动规律 modified trapezoidal acceleration motion
/ H% Z5 J% Y# C! _8 S* W7 ]修正正弦加速度运动规律 modified sine acceleration motion+ d- C+ O' O7 x: |( d1 r0 R* k
斜齿圆柱齿轮 helical gear b0 h( l1 ~1 u3 X
斜键、钩头楔键 taper key2 z+ d) d! ]8 s3 F; S
泄漏 leakage/ J2 A2 ]9 u' _# h0 i4 J* J
谐波齿轮 harmonic gear) o9 K& W5 m/ {2 z' o9 |- V
谐波传动 harmonic driving
+ Z5 r9 A: t' Q! @3 }2 ~$ i谐波发生器 harmonic generator+ H2 ^- B: f+ ~1 y
斜齿轮的当量直齿轮 equivalent spur gear of the helical gear# p% J) i' u% u" s
心轴 spindle# N/ A. \4 ` r. s6 s
行程速度变化系数 coefficient of travel speed variation
, N. j; T/ a6 a+ ~行程速比系数 advance-to return-time ratio8 Y. q3 b9 U5 N8 @ H& ?
行星齿轮装置 planetary transmission
+ E: L4 F! p$ t1 D& O. F行星轮 planet gear5 t$ v5 O ]% | j7 o
行星轮变速装置 planetary speed changing devices
8 X/ ?4 [( l. q: [- o行星轮系 planetary gear train
9 ]4 h! B i! I" g( P+ j形封闭凸轮机构 positive-drive (or form-closed) cam mechanism: \; i" P. C) {, a; J3 M
虚拟现实 virtual reality9 H, B5 |) j0 ]) k* ~
虚拟现实技术 virtual reality technology, VRT
5 \. s* k( U: D- x" _/ P虚拟现实设计 virtual reality design, VRD
" i! {+ V/ q+ }虚约束 redundant (or passive) constraint1 n2 ~$ ]& v1 H4 J9 ] a7 j& ]" g6 Z
许用不平衡量 allowable amount of unbalance
, l3 x+ W- e; y* i) \- l" B& W6 I0 |许用压力角 allowable pressure angle
* s B6 c, P* k5 ]' s+ @许用应力 allowable stress; permissible stress
' |9 Z! v; j2 e) B9 A悬臂结构 cantilever structure
" g5 H8 d/ x7 h悬臂梁 cantilever beam; U) ~1 a6 ] \/ j; A' F& A- U
循环功率流 circulating power load
& z8 M* O4 P: o; D" C" B- _旋转力矩 running torque
- N; D( r% \; p8 e0 F# r旋转式密封 rotating seal1 i8 M% P! D+ I# e/ f
旋转运动 rotary motion7 D: ?5 V9 ^# @
选型 type selection
: t) ]6 H. i! w6 y2 }压力 pressure % H3 q9 T( w9 V8 S
压力中心 center of pressure - h9 [% s2 {) |0 S
压缩机 compressor
% U; b. M- h5 N压应力 compressive stress
/ J: G4 \8 H4 K+ p0 H压力角 pressure angle
0 W9 o2 A& Z* {! R6 \3 l) g牙嵌式联轴器 jaw (teeth) positive-contact coupling
3 D: p8 p1 l. R1 A4 V. Y& `雅可比矩阵 Jacobi matrix
# v; D+ |% f5 e摇杆 rocker
4 \6 Y+ T' ~; n }液力传动 hydrodynamic drive
% Z' g" h* f; q/ r- q4 z液力耦合器 hydraulic couplers
5 ?3 c9 M4 T& B液体弹簧 liquid spring% z A( ^" I3 R8 h
液压无级变速 hydraulic stepless speed changes& u5 ]1 s! o) m7 n
液压机构 hydraulic mechanism
+ J+ H( K& y; J+ @. P4 h一般化运动链 generalized kinematic chain
1 K. ?, R7 Z8 H: C移动从动件 reciprocating follower# U. z' L2 W2 r! n" A: K: ?# ]
移动副 prismatic pair, sliding pair, x+ w" o3 `3 |" P% ^5 g$ ]# U
移动关节 prismatic joint( s( J7 g/ b) z. Z4 F) N6 c4 V5 d
移动凸轮 wedge cam" N- Z/ m( V) V0 A/ ~0 ~
盈亏功 increment or decrement work
- X! r3 f Y, m& S# C4 a3 t* S应力幅 stress amplitude
* Q/ N( {# j- T; D9 q应力集中 stress concentration
- E6 p! ?# ?- Y3 E# p+ ^" K$ R应力集中系数 factor of stress concentration
2 |# E; x7 h' R) U; D2 z# u应力图 stress diagram# W3 p% w- A) f h& H- H( ^! R
应力 — 应变图 stress-strain diagram
! x/ B+ m* D9 f) W( B+ `优化设计 optimal design" C0 `+ R" O& l# v" z4 M+ V8 s, b$ x
油杯 oil bottle
9 y8 \- b3 {9 a( Q1 ~: F. E油壶 oil can
2 F% E+ A8 V! `2 M2 s: L# g油沟密封 oily ditch seal
- q4 u; k- Y4 W$ u% s有害阻力 useless resistance
# [5 T |6 a C' v有益阻力 useful resistance( `8 h' U- K" ]6 n C1 {' D4 I. @: c
有效拉力 effective tension- C" z) |6 l7 R' o- R/ S
有效圆周力 effective circle force
5 ?' A' Z( E4 \% F; ]4 H- p+ i有害阻力 detrimental resistance, T$ _- F3 ?; o7 Z4 g: s
余弦加速度运动 cosine acceleration (or simple harmonic) motion6 M( I( g% R L$ D& a
预紧力 preload( ^7 [' K2 m& @
原动机 primer mover |
发表于 2008-2-21 11:42:15
QQ好友和群
收藏
淘帖
问题专业，描述清楚
伸手党/灌水/看不懂