曲柄滑块机构 slider-crank (or crank-slider) mechanism' W+ ?. P) C: Y. V# j$ K& l& H
曲柄摇杆机构 crank-rocker mechanism4 c0 D2 c5 a# l6 Y* A/ f4 L# M' r
曲齿锥齿轮 spiral bevel gear1 m" u! _) l7 j4 t( l& P4 b
曲率 curvature* P" W7 M8 L4 M: k9 W
曲率半径 radius of curvature
|8 |; q! ^1 ~2 z& k8 O曲面从动件 curved-shoe follower
" s( F8 q! W5 J- h曲线拼接 curve matching4 r5 {" ^8 G1 `4 q3 r" m2 ~9 T
曲线运动 curvilinear motion4 S" ^3 L0 i) t. o2 L
曲轴 crank shaft
N9 I* n8 ?/ H3 |驱动力 driving force
) [1 M$ T3 {2 T. D: e" w驱动力矩 driving moment (torque)- x7 X# i8 K2 d) A( }' F
全齿高 whole depth
X) V, _/ v/ \- M$ y# e( j4 P权重集 weight sets! R+ N' }9 u+ V
球 ball6 {( _# } C1 y
球面滚子 convex roller. L; M2 v% i0 q. E) H
球轴承 ball bearing
, }2 I4 l# ]# z' e球面副 spheric pair( E4 i7 A9 y3 U4 {1 i' U
球面渐开线 spherical involute3 R) K3 ^6 v6 ^ ~0 E1 J
球面运动 spherical motion0 A3 z8 Y. V# l- P
球销副 sphere-pin pair5 ]7 t4 z0 q' h& }2 v
球坐标操作器 polar coordinate manipulator
1 [8 x+ ~) f% E% O) Q- ?6 @) D: h& w' p燃点 spontaneous ignition " n5 I- {- Z5 \+ s7 y* E1 A+ c
热平衡 heat balance; thermal equilibrium 9 |9 }6 Y$ c/ t4 I% D
人字齿轮 herringbone gear
: D2 ]8 b; [5 a冗余自由度 redundant degree of freedom: A5 p! O, [! M
柔轮 flexspline
3 a4 g$ I% b, c6 a7 P柔性冲击 flexible impulse; soft shock2 o; \4 A! ^+ h& W# B
柔性制造系统 flexible manufacturing system; FMS9 C2 V: }+ x; `+ K! S
柔性自动化 flexible automation
/ {! t" j- l' H' [6 y润滑油膜 lubricant film9 {, g1 P0 K/ U, O% P. y5 q0 ?
润滑装置 lubrication device" M M r0 p( v8 Q' \- B5 i( F
润滑 lubrication3 P5 C2 b0 C& @! p' h7 D
润滑剂 lubricant: D' e9 D+ k1 C- I6 x
三角形花键 serration spline
0 d0 y+ f2 W, A2 v三角形螺纹 V thread screw ( A1 y. m- {, ?" Q# b: O2 X8 T, k
三维凸轮 three-dimensional cam
' q3 l" Q( o! s ~ z三心定理 Kennedy`s theorem
: ~0 d1 r8 W# x砂轮越程槽 grinding wheel groove1 Y, t& r0 P0 K8 ?/ d$ k5 R
砂漏 hour-glass
# g: i1 O* L. K3 j* I少齿差行星传动 planetary drive with small teeth difference
/ ?! y! m1 [/ r. n" k7 S1 ?9 M: W设计方法学 design methodology$ ]. U4 i/ Y/ r! e5 Q4 R, ^5 Q
设计变量 design variable
2 Q% H, C) L* C* c6 N3 u! a设计约束 design constraints' j' C: b4 @" R5 u1 Y B
深沟球轴承 deep groove ball bearing
- u. ]' h4 s9 L+ D) Y$ t, c生产阻力 productive resistance
& n# ^& g- r5 T- u, ~1 h$ [6 S9 e升程 rise
, F- O2 A# a& _5 W6 g" X升距 lift0 w4 c/ s6 `; V/ U
实际廓线 cam profile
# a. K, q; @% f! |& O9 g" J: u十字滑块联轴器 double slider coupling; Oldham‘s coupling* D+ O$ A @/ Z; l' s9 d8 E
矢量 vector
0 w3 Z: w7 K7 X2 [3 J$ @输出功 output work% }. j# w# w* C! V; w( y1 v
输出构件 output link! [- z; G7 m8 {+ F
输出机构 output mechanism3 j* H6 \$ O5 b8 y( ]8 R+ M
输出力矩 output torque
) d1 M# s: x. e输出轴 output shaft; e! t- N4 K1 C4 }, ?( o
输入构件 input link
- n5 n% i4 Q+ y- |数学模型 mathematic model
$ F; i$ z' o8 M0 @: H实际啮合线 actual line of action
/ ]9 O8 |* m+ z, z双滑块机构 double-slider mechanism, ellipsograph
( w D. h! k) R8 X双曲柄机构 double crank mechanism4 b5 n/ |8 r" e9 o3 I; \
双曲面齿轮 hyperboloid gear
* M z; I3 M4 u+ c ]双头螺柱 studs( ?3 I; N/ b4 U
双万向联轴节 constant-velocity (or double) universal joint
1 J& o% Q8 j. f! m双摇杆机构 double rocker mechanism% l' t1 p+ g% K& h2 w/ f
双转块机构 Oldham coupling6 y& j7 k; B$ b+ _
双列轴承 double row bearing
# p1 Q8 X v+ W/ N3 A& V6 P% g双向推力轴承 double-direction thrust bearing
& y7 Z5 |; L" ?" F' }+ _# ~2 x松边 slack-side
# U+ F* [3 K6 v1 z8 a* D ^3 g顺时针 clockwise0 {$ k7 m7 W) N- C
瞬心 instantaneous center
' `6 W- q M, q) b q# v: @# M死点 dead point$ O1 K2 Q6 q v" E
四杆机构 four-bar linkage: m: c/ I0 ~$ K# u
速度 velocity
1 v; K2 T+ z* ^3 l; o! _' ^: m9 V! W速度不均匀 ( 波动 ) 系数 coefficient of speed fluctuation( q I' x2 J1 w! e5 `% w
速度波动 speed fluctuation
' T/ t7 ?& }) r, z; X+ T. n1 `速度曲线 velocity diagram
& p& ^3 [8 p) H5 b6 Y8 ?* x# A速度瞬心 instantaneous center of velocity5 V k0 J. X& \% Z: N- U6 p3 p
塔轮 step pulley ) `; A5 ?2 N( K2 _5 X+ G; A+ G7 f
踏板 pedal , z j! k, r. K7 O7 g j
台钳、虎钳 vice$ m/ s' Z) n: c' i6 j8 X l
太阳轮 sun gear
/ C! d* ~9 |4 M) p q弹性滑动 elasticity sliding motion4 e/ ~% a+ A8 W1 C; A9 s- O( N1 D
弹性联轴器 elastic coupling flexible coupling
" {0 ]: Q- ~& {9 O3 C6 d弹性套柱销联轴器 rubber-cushioned sleeve bearing coupling$ U) M+ }* }) B' [
套筒 sleeve5 @+ f6 m! A, A' X
梯形螺纹 acme thread form- D2 S0 p+ D8 h# |) x/ v" A" H& \7 v
特殊运动链 special kinematic chain9 h, o1 K ^! t# a
特性 characteristics
& y0 {2 x$ a9 K6 N2 y7 f! Z替代机构 equivalent mechanism
( K1 z) G8 o. F1 v ^! V, M: V调节 modulation, regulation
2 B/ v4 H8 ^: O2 u调心滚子轴承 self-aligning roller bearing
; i* o+ O) |4 d调心球轴承 self-aligning ball bearing
. ^+ K6 t. \9 |( f3 J" c调心轴承 self-aligning bearing) a: U4 y+ c4 Z4 M- O$ M8 b
调速 speed governing6 E4 n" |7 F e, p( n( I1 ~" d! r4 N6 d8 f
调速电动机 adjustable speed motors3 U8 y R6 {1 C
调速系统 speed control system
# @- y' w; F' {, L/ J调压调速 variable voltage control
( M, b& }: C3 d: `- o O/ B4 o调速器 regulator, governor
/ Y+ a" M0 i R( p. l; t铁磁流体密封 ferrofluid seal) w/ N1 j6 D$ {0 Y0 T! O
停车阶段 stopping phase A+ V8 z4 O, t5 |0 u p q- X
停歇 dwell8 Q& Y2 I# M& o: {7 i ^: f
同步带 synchronous belt
2 m$ o2 {4 T- _4 e同步带传动 synchronous belt drive2 N0 ~/ S; I+ G- D/ D
凸的，凸面体 convex
- r- ~5 x5 C, P/ g. x; o凸轮 cam
) M! s% A( R: E. G w* [7 G凸轮倒置机构 inverse cam mechanism
. I0 X. H- x+ r% k+ R凸轮机构 cam , cam mechanism
6 u& _: S/ h8 _$ O# s7 n$ ~- P6 U凸轮廓线 cam profile7 b4 A0 j, M3 n; v. f9 D/ X
凸轮廓线绘制 layout of cam profile) Z4 [ S* g2 j
凸轮理论廓线 pitch curve
8 g: m* e, z$ N; ]2 O( D5 ?% `凸缘联轴器 flange coupling
0 w5 U" j7 o" d% Z6 r图册、图谱 atlas, I2 a- @4 ~, Y- ? a' }
图解法 graphical method
4 X) K9 T9 ~' H推程 rise
n( ^2 @/ g% I. {6 x推力球轴承 thrust ball bearing# _+ z0 M1 u9 [& w
推力轴承 thrust bearing
& k- y. S5 Y4 `1 y退刀槽 tool withdrawal groove
- d0 O& v# E' T" r退火 anneal
4 N9 b3 l8 T- I4 ]- I陀螺仪 gyroscope
! r# m& Y" [: O3 }, EV 带 V belt
. a3 c q; R+ n9 ]( a外力 external force ! b. L/ |, r+ c
外圈 outer ring
! K$ ^' I" k& G8 U5 @! e, T外形尺寸 boundary dimension0 O Q6 y' h3 D. P- q
万向联轴器 Hooks coupling universal coupling0 y8 F0 g" p7 @8 P' n7 d* t
外齿轮 external gear
( a. s+ s; o6 t& r5 g4 |3 @7 N9 p弯曲应力 beading stress: O; T3 q M7 Q, [3 D- b
弯矩 bending moment; |4 J: h/ [1 T+ r) I: V& g, X
腕部 wrist
* M. C' w q- p ^" |& H- L1 }' w往复移动 reciprocating motion
! H" D: K8 Y2 |) W- I- ~往复式密封 reciprocating seal
2 n2 @. _( |( z' Z9 }+ b; \网上设计 on-net design, OND9 t/ A2 e- }: d: E! v2 c
微动螺旋机构 differential screw mechanism
0 Y* _0 O/ E& f4 [4 t! u+ R3 L位移 displacement* A" E, J. @6 M1 q) b; G: e3 x
位移曲线 displacement diagram& U6 r6 {/ A H. f# M
位姿 pose , position and orientation
" K' i: d7 W) o稳定运转阶段 steady motion period
- [- Y S4 @" i4 k+ M( G稳健设计 robust design) m" y2 i( u# T/ K- k
蜗杆 worm
7 {' z5 B$ ]$ J) b蜗杆传动机构 worm gearing/ v( e* r, G/ |4 z) [
蜗杆头数 number of threads
) E" D, S) b. w c蜗杆直径系数 diametral quotient. ^9 y$ l& ] g7 S% \" B3 M! I
蜗杆蜗轮机构 worm and worm gear s: w- u- _6 O, l2 ~( S
蜗杆形凸轮步进机构 worm cam interval mechanism
+ ]3 }* ?9 _% C蜗杆旋向 hands of worm
7 ?0 T+ G5 ?& }, V0 n& z蜗轮 worm gear
( [1 G" J' e$ U1 X涡圈形盘簧 power spring
5 V- m- ?2 d! h( E) Z) K无级变速装置 stepless speed changes devices
: Z8 }$ T2 X. i: k9 O- @& q无穷大 infinite
" h9 K3 g& c8 L1 W% G! ]. e系杆 crank arm, planet carrier ! I& v5 }, O% `
现场平衡 field balancing + \4 K) E- S* T" v
向心轴承 radial bearing! Y$ [- ^ a( y. {2 I& u
向心力 centrifugal force5 H0 `: o' W( D9 c$ S* S
相对速度 relative velocity
$ z( ~6 w& D# Z5 u: n3 b! `相对运动 relative motion6 F* g! o! L: W0 p1 E1 d0 ~
相对间隙 relative gap
; V/ l% ~$ V, S7 \, v5 u象限 quadrant
3 ]) M4 @1 o0 J: S Z橡皮泥 plasticine% S n7 v4 \. J' X5 l
细牙螺纹 fine threads- v9 k3 |6 |, U8 @* l$ R
销 pin1 Y7 U- R+ C9 \+ y+ ~
消耗 consumption2 V |! @1 \+ L" d" F0 g, Y4 S+ r
小齿轮 pinion
' X5 s( @# G8 A( R6 S8 C; D0 P2 u9 Q7 R小径 minor diameter% u3 [( ^/ g. D7 h/ j, C0 c
橡胶弹簧 balata spring
5 @, @. A2 D. q# t( x0 t; Z& F修正梯形加速度运动规律 modified trapezoidal acceleration motion
# Z h: {. K; F, }修正正弦加速度运动规律 modified sine acceleration motion
. ~( y! A' f+ g斜齿圆柱齿轮 helical gear3 L$ p4 M( H! f0 f& j" z, R5 r7 K6 C% k
斜键、钩头楔键 taper key
9 w+ B% N, w2 t3 F, ~! H% b泄漏 leakage
8 h/ ?/ c! k3 O谐波齿轮 harmonic gear
( S) A, p! b+ J9 D; Y8 Q ?谐波传动 harmonic driving
7 R# N5 o# W! z A+ c m谐波发生器 harmonic generator
0 s& j# [: e' k6 r0 I% r/ G6 z斜齿轮的当量直齿轮 equivalent spur gear of the helical gear$ z! x5 p+ d6 h3 e+ O' m) j2 K
心轴 spindle, c9 U$ ]6 ^1 W% e2 Q' B+ z
行程速度变化系数 coefficient of travel speed variation) @ b( }2 F1 c. }' w3 u1 |% \6 |
行程速比系数 advance-to return-time ratio
4 k, @# |6 C( E3 @7 ~3 m4 A行星齿轮装置 planetary transmission
- p" f$ T7 N( v行星轮 planet gear
2 h. s G) h- _% d$ D1 [% o7 `3 u行星轮变速装置 planetary speed changing devices: ~ m3 B w- G$ D; F3 [
行星轮系 planetary gear train
- v9 S" s& T8 E7 W {2 U5 ^形封闭凸轮机构 positive-drive (or form-closed) cam mechanism
- _/ {8 _5 P: R' U" `9 [* N& w虚拟现实 virtual reality8 K5 m& U+ l! U W
虚拟现实技术 virtual reality technology, VRT
7 ~" q- k8 N$ b: W" z虚拟现实设计 virtual reality design, VRD
0 x1 M8 H! ^ R2 V5 n' ]( B* e$ ^虚约束 redundant (or passive) constraint& k d! l6 S& L2 ^ w! C
许用不平衡量 allowable amount of unbalance
1 A; P+ C- D! A许用压力角 allowable pressure angle
3 L- e- T `( q7 u% J- t许用应力 allowable stress; permissible stress
% L& O9 z) \3 K& [/ q5 ?# y悬臂结构 cantilever structure5 V/ h$ O$ S. i. F
悬臂梁 cantilever beam/ x$ C" ~: g4 o0 q% ]
循环功率流 circulating power load
1 y3 X3 o! o3 ]9 m1 q$ s: v旋转力矩 running torque: R' H! j. ?2 Y, v8 N
旋转式密封 rotating seal
" ~2 t7 H% j3 L* y& Y3 V) C. u旋转运动 rotary motion
7 \. x* N7 T) @4 F4 m0 V# D+ {选型 type selection) ~1 h- U# Y& |- w$ f8 r& o4 S
压力 pressure , b5 |: _: \* Y( D7 n
压力中心 center of pressure + L! R; x: v! `5 L; l$ Q8 S
压缩机 compressor
5 s! }% D! Q5 k1 B1 ~压应力 compressive stress1 V; U/ V- L( Q8 z6 O- e
压力角 pressure angle
4 s: @ ]3 `! j: `8 a: o7 i9 _牙嵌式联轴器 jaw (teeth) positive-contact coupling0 N$ O- N1 _1 \ p! a* l5 [
雅可比矩阵 Jacobi matrix
8 z2 P4 ?; H% t4 }+ ^摇杆 rocker
8 ~( p; x. G% ^! u' g液力传动 hydrodynamic drive, m8 g7 N6 h) E; D, h8 e) E3 b
液力耦合器 hydraulic couplers
6 N+ Q& c# }" @液体弹簧 liquid spring9 `9 _) b9 ]/ |$ _ Y/ O4 a$ ?4 d
液压无级变速 hydraulic stepless speed changes
v X" _, f& r* p9 w3 {液压机构 hydraulic mechanism
; U: k+ ]8 W1 W% O一般化运动链 generalized kinematic chain
7 ^$ v8 U0 J3 P: }' B5 ~移动从动件 reciprocating follower
0 P5 m/ Q; v, H" O! y1 E移动副 prismatic pair, sliding pair
/ ]. H* ^' {9 S, H4 d8 @8 P9 l! Y移动关节 prismatic joint7 G& F$ X2 V6 W0 ^! J6 {
移动凸轮 wedge cam3 }" V& d; |- N: R3 C( F
盈亏功 increment or decrement work- ]& G6 k' E7 Y8 t. w
应力幅 stress amplitude
: ^+ ~! |# M) `+ m% h7 k应力集中 stress concentration
/ P/ |$ i# V5 M& E4 Y8 u' O应力集中系数 factor of stress concentration
8 t9 l: h, ^; x1 b {应力图 stress diagram
' U; `( L, R3 Q! o应力 — 应变图 stress-strain diagram
# m* H7 t% J3 U8 t优化设计 optimal design
9 p: A) G: [; m, M U8 q$ x油杯 oil bottle
9 ^3 G" X; Z8 F! A" H y7 Q油壶 oil can
- {7 d) R; Q; q, Q- r- o/ t; o油沟密封 oily ditch seal8 y$ X# L) i! K7 S' }, \$ t5 k
有害阻力 useless resistance) ^" r& d# [% F8 [$ o
有益阻力 useful resistance; L {. A# e' M9 e0 L
有效拉力 effective tension
# d: @. k1 m3 O2 Z) K* f, J有效圆周力 effective circle force
6 J1 k5 @; G2 B5 N有害阻力 detrimental resistance4 |* d' S( y, @- j% q' W
余弦加速度运动 cosine acceleration (or simple harmonic) motion4 y) p- u7 c" B) b" | O* r
预紧力 preload
, P9 V9 h4 @& ]) C7 ?! @& s6 Y原动机 primer mover |
发表于 2008-2-21 11:42:15