曲柄滑块机构 slider-crank (or crank-slider) mechanism' L1 V! Z9 |; f: E6 W
曲柄摇杆机构 crank-rocker mechanism7 e2 I' D& E' H: K) z/ p2 B: t
曲齿锥齿轮 spiral bevel gear
( y, Z" M, L0 r2 M% ?. S, x曲率 curvature* n) Z0 L! f" D7 B4 x; l: H$ c+ y
曲率半径 radius of curvature
6 ^7 P1 R+ G/ Z3 P( I: [曲面从动件 curved-shoe follower
4 Q( U$ P* F6 O5 x# t& @% v: [曲线拼接 curve matching
- m5 Y" V# [, k p* [3 e) d曲线运动 curvilinear motion
" z0 f6 F* `" U3 _曲轴 crank shaft
6 C+ Q. u6 l y* b+ f3 E! s( S驱动力 driving force
# ^' u. n2 z7 Y0 z% e4 L驱动力矩 driving moment (torque)9 r3 M9 V: k- B6 F7 q/ Y* B( b% v9 N
全齿高 whole depth9 l/ a! G1 T; i/ p. j. a/ [
权重集 weight sets. |8 P/ f. h: b+ `8 q+ W/ P
球 ball- X* Y4 S- E6 ?0 m
球面滚子 convex roller9 [5 f2 f1 T/ |- Z! K
球轴承 ball bearing6 W5 i- ?* D* f
球面副 spheric pair
/ F; s- j( Y, q球面渐开线 spherical involute, L y' A. I4 b
球面运动 spherical motion; M( o }% Y* n7 b- Z, g
球销副 sphere-pin pair
# @. n2 U( }" _# ]- v球坐标操作器 polar coordinate manipulator5 U& R. F! ~0 }- E5 A j. G" V
燃点 spontaneous ignition
' j0 j' ]) ^) w3 q热平衡 heat balance; thermal equilibrium ( j$ M) Z% h, p8 Z: b
人字齿轮 herringbone gear
5 i% Y* h7 A$ B; `: [8 m& M冗余自由度 redundant degree of freedom
8 t* K+ ]- u) L5 D柔轮 flexspline
. l+ V& r2 s& p柔性冲击 flexible impulse; soft shock
0 a: o' K# s) b0 J+ j柔性制造系统 flexible manufacturing system; FMS
- z: w% _. ^9 `) Q, ?柔性自动化 flexible automation' q2 V7 x; }8 O6 Q' g# ?# K' s
润滑油膜 lubricant film% S1 k: _0 Y. ^8 I* G- }7 S6 C
润滑装置 lubrication device
* i' t4 T# C- L8 N7 `0 W润滑 lubrication2 W. W0 G$ B( j' Q
润滑剂 lubricant& D8 i* e7 m4 {4 P9 n. _
三角形花键 serration spline
1 D# u' T2 ~9 _9 _三角形螺纹 V thread screw # N8 z7 J" q& S/ C" w" _
三维凸轮 three-dimensional cam) m9 q7 F: X/ i# ?
三心定理 Kennedy`s theorem s& z% Q; c6 m
砂轮越程槽 grinding wheel groove% |4 T8 m- v% P
砂漏 hour-glass. V+ p4 R. D) v% D5 a( D/ Y# p
少齿差行星传动 planetary drive with small teeth difference
) Q+ t' H& ?" y3 q) o8 K/ I) x设计方法学 design methodology8 i* e- Y. {8 Z: K( M
设计变量 design variable
9 _0 H7 i# ]8 n设计约束 design constraints% x; n: m; M9 `4 [# U; ]
深沟球轴承 deep groove ball bearing# k. k5 G$ A+ u% i4 K: D
生产阻力 productive resistance. h1 ~- g* m% T- x" _: o
升程 rise
& T1 b, _% m0 G l4 o升距 lift2 b* T' O4 p5 d/ Q/ |8 x
实际廓线 cam profile
! I J: x* T# d" r. H) |. C十字滑块联轴器 double slider coupling; Oldham‘s coupling1 N8 h7 F% P) I8 a- t
矢量 vector
& T# u) E5 r6 _$ k! K输出功 output work9 A2 }0 y1 v# _2 H
输出构件 output link9 {4 @& N& d& F% R# {( v* g
输出机构 output mechanism4 [% o: @: L% c3 p% F# r5 K, d
输出力矩 output torque
1 _& x9 ]+ ]- p2 @输出轴 output shaft3 H% j: \1 f3 K4 T
输入构件 input link5 x9 s H! p" f- P0 @4 q: y
数学模型 mathematic model
8 e% z, ?. i; ]2 ]8 F3 s实际啮合线 actual line of action
( C T0 T8 [1 L" T# H双滑块机构 double-slider mechanism, ellipsograph3 X( W3 U- r, e
双曲柄机构 double crank mechanism+ h! n/ c; @ r6 ?' L
双曲面齿轮 hyperboloid gear s, X( e1 G; Y9 L% j% z2 m H* |0 p
双头螺柱 studs
! q# F9 l4 C! a1 ]4 t双万向联轴节 constant-velocity (or double) universal joint) Q7 i! \6 u; U) v' w
双摇杆机构 double rocker mechanism7 @% \4 W1 k( c- D4 G* e) A
双转块机构 Oldham coupling
+ T0 w4 ]6 W( k! ^& I- l双列轴承 double row bearing
" Q; _- f0 N0 p' K双向推力轴承 double-direction thrust bearing! E* P1 J( T( t% B
松边 slack-side
. e! @0 B: N1 x' k0 L顺时针 clockwise
9 j& n4 y9 J+ B瞬心 instantaneous center }6 E8 e$ L( r5 l
死点 dead point
/ h# ?, d7 i* _% v9 D- ~四杆机构 four-bar linkage9 C8 i& L) Q3 F
速度 velocity
5 Q7 c0 k; P4 F6 }( d7 V+ w速度不均匀 ( 波动 ) 系数 coefficient of speed fluctuation
" r: m& m- R5 p$ H. K速度波动 speed fluctuation1 _" j H2 _* U! P7 p
速度曲线 velocity diagram
, K, V2 G' y* b% z( p速度瞬心 instantaneous center of velocity' u4 P' v* q9 G0 i, w
塔轮 step pulley ; o. `- `( b9 @% n
踏板 pedal $ r' w7 x4 |9 N. }% `; v( F! r }% A
台钳、虎钳 vice2 ^- B9 T9 c( J/ Y% G4 C, U& J/ n
太阳轮 sun gear
. N+ J, s) X3 v9 f' `' H7 G0 [弹性滑动 elasticity sliding motion) A" q8 s4 s# d. H" L
弹性联轴器 elastic coupling flexible coupling
# D! U/ d% h* G0 T7 ^) _: d. C8 x弹性套柱销联轴器 rubber-cushioned sleeve bearing coupling- P( G5 T8 n! U: t- y
套筒 sleeve. t* T4 G$ G. ~4 ^- l" [: R" p$ w* r
梯形螺纹 acme thread form
0 f% j" Z+ Z) s* y8 F+ w特殊运动链 special kinematic chain7 [( ?" ~: J. s7 J) F
特性 characteristics
6 I. T) ?' ]& {# L, {6 c0 c替代机构 equivalent mechanism% A9 V7 _: g0 i W* I1 q) E) Z0 p* e
调节 modulation, regulation7 S. p; ]/ d, ~4 |1 ~: z
调心滚子轴承 self-aligning roller bearing% X/ \5 ?1 u5 H' e
调心球轴承 self-aligning ball bearing
' S0 d' g U6 @& _4 @: Z3 l( @; W6 A调心轴承 self-aligning bearing" v* `4 j% p2 Y" a* P* Q
调速 speed governing
f$ r( l" T7 A$ F c( D& c调速电动机 adjustable speed motors0 w# v, B: ?" _6 g& Q! W
调速系统 speed control system
* e7 H2 L8 m( `5 ^/ g调压调速 variable voltage control
+ R7 s- W* s" [% S" p L调速器 regulator, governor
9 c8 ?: V/ J$ i0 @0 q# d/ g5 K铁磁流体密封 ferrofluid seal- f4 D( O4 W* p) r' M
停车阶段 stopping phase3 x0 N: e! O% N! E
停歇 dwell
+ o1 c3 V0 T7 |: Q9 }同步带 synchronous belt
0 X# H/ _# u" [4 a同步带传动 synchronous belt drive
( `! ]3 V; ^5 M' c. J3 \凸的，凸面体 convex
% u" a. O- y! O8 t, S6 e3 w凸轮 cam
! A0 |" D* ]$ y凸轮倒置机构 inverse cam mechanism% n/ p" U5 m6 @
凸轮机构 cam , cam mechanism
# I2 Y! }" J F0 z+ N( d凸轮廓线 cam profile
# x7 g4 ?* S3 h# }凸轮廓线绘制 layout of cam profile
- D% Q3 M9 K! p* Y% F( A凸轮理论廓线 pitch curve# ?9 s1 V* ?: w C/ n* V) D
凸缘联轴器 flange coupling
$ H$ d0 b2 @% t7 x& U图册、图谱 atlas
0 V/ |$ R" Z$ }4 |图解法 graphical method& L- l, |9 Q8 e3 O- ^6 D8 N+ i7 L' X
推程 rise2 P) ], ?! y) i+ K5 u0 C# [7 ^2 k
推力球轴承 thrust ball bearing/ Z- R, ]$ R4 j* U8 s( G/ b# X! {
推力轴承 thrust bearing; n7 d9 {2 y* W) W6 C
退刀槽 tool withdrawal groove1 [% ?& C! ~% e( Z1 o) k I
退火 anneal4 m7 g) q5 x* e5 h/ Q4 A/ ]3 P
陀螺仪 gyroscope
! D. i1 q' M6 ~! pV 带 V belt
) o1 j/ X0 F M) o0 d# x外力 external force ; ]9 ~# W/ V% C
外圈 outer ring 3 ` N; r7 k1 F& G( _5 l/ m
外形尺寸 boundary dimension
. A6 o7 L3 G* X J万向联轴器 Hooks coupling universal coupling
- E+ x; R9 p$ O5 `6 o8 W9 `& n1 s外齿轮 external gear2 o& ?! N1 h' Z! L% H+ q
弯曲应力 beading stress, E5 U" l( M- w6 I1 v
弯矩 bending moment
* C" t! P1 ~1 [, J& }7 x$ b( D/ H% @! l腕部 wrist& g9 G6 {5 B b: G G( z
往复移动 reciprocating motion
9 r; p8 p# n" N7 f; q: |% Z往复式密封 reciprocating seal: z% ]) n; r% ^! x
网上设计 on-net design, OND
4 G! ~3 |# P; G& l( N微动螺旋机构 differential screw mechanism4 }( B! f5 h A/ e* R! {' N
位移 displacement
M1 }2 r! w/ W2 F) \位移曲线 displacement diagram: N& g% i2 |' X9 M1 {
位姿 pose , position and orientation. X+ s+ }# l* R
稳定运转阶段 steady motion period) F- }: Z" p1 y, o8 _
稳健设计 robust design
1 x6 x2 I3 y, |, r% U+ c8 { O6 w蜗杆 worm
+ _& U0 F7 Y' P蜗杆传动机构 worm gearing" ], Z$ Q' Y ^
蜗杆头数 number of threads
( A1 {" J3 z9 g3 ?蜗杆直径系数 diametral quotient
# d& w( Y' A) m7 u2 I蜗杆蜗轮机构 worm and worm gear- d5 U1 e" `- ~7 d& F
蜗杆形凸轮步进机构 worm cam interval mechanism9 @' c' j- W0 V
蜗杆旋向 hands of worm' O5 n e0 X9 f. \: w, P7 c4 W
蜗轮 worm gear
# M' J% G/ x( N1 q2 i; {涡圈形盘簧 power spring: V3 C0 C' f% Y$ |2 {
无级变速装置 stepless speed changes devices
1 g) e: R6 f/ C: b无穷大 infinite
* x! m7 F! `, _+ o. p/ b, c+ `系杆 crank arm, planet carrier 5 b: @: n L& f. L w5 I
现场平衡 field balancing
! M2 V q- Z+ y3 h# D! O; w. c5 e向心轴承 radial bearing
2 z" f* @6 \: i' H+ f! Q" z向心力 centrifugal force
D8 |% F8 R! o, V" |8 `% n4 m相对速度 relative velocity
& Q; J2 m. X3 f) y/ b4 X4 F. w* Z相对运动 relative motion! N4 T8 e" {7 H& j+ x
相对间隙 relative gap3 p! I5 E* M. c+ s/ j8 i! N
象限 quadrant
+ s$ Y$ d7 e, c$ ^橡皮泥 plasticine
: N- c2 s: R% b& |" A* O4 A7 R细牙螺纹 fine threads
C1 Q3 X: v0 G- p" g销 pin' K# d3 X/ A) s. V4 v( Y2 q/ e: g
消耗 consumption
8 s9 U7 ^9 k. Q& `' ~; Z! b小齿轮 pinion) O' b R. J Z3 H6 V
小径 minor diameter
' e) ]( |6 G3 j& u) n: l" `( w8 R橡胶弹簧 balata spring% E& L5 s) t" W: e: l
修正梯形加速度运动规律 modified trapezoidal acceleration motion4 H6 }" i8 G3 y( a
修正正弦加速度运动规律 modified sine acceleration motion+ [# {" X4 i! I; h
斜齿圆柱齿轮 helical gear
% K) }, p! O9 O$ M4 i斜键、钩头楔键 taper key3 u, o1 e/ w! g7 l' b6 D
泄漏 leakage
" ] w4 m1 x. |( Y, i! ]谐波齿轮 harmonic gear& V' l3 k5 B6 N
谐波传动 harmonic driving9 D( R0 P) P1 [
谐波发生器 harmonic generator; g9 h( a0 I* \7 D
斜齿轮的当量直齿轮 equivalent spur gear of the helical gear+ B2 b& {' z% h- T
心轴 spindle) |& X9 J" z# \- u- x# g6 @9 W
行程速度变化系数 coefficient of travel speed variation
/ T. B& Y5 c, E6 m* Q( L/ \行程速比系数 advance-to return-time ratio
: S1 q, h. [2 y& i: b5 L* X: h行星齿轮装置 planetary transmission
" {1 Q( j& N* _7 q# I+ I行星轮 planet gear# N$ V2 U9 N0 B; z
行星轮变速装置 planetary speed changing devices3 t9 [; k0 Y z" Y1 ^
行星轮系 planetary gear train
2 ?" j& i% t$ b3 Q* ?形封闭凸轮机构 positive-drive (or form-closed) cam mechanism
, g' y( W, c/ \. i虚拟现实 virtual reality
' u9 M3 ~2 d' I虚拟现实技术 virtual reality technology, VRT! Y( X+ W' g6 r. |6 m, w2 o* p
虚拟现实设计 virtual reality design, VRD1 W+ p3 S7 _" ^1 g4 ?4 _. Z
虚约束 redundant (or passive) constraint
$ L5 {5 s" V. R许用不平衡量 allowable amount of unbalance! W) i2 l/ D7 {% c3 S; z
许用压力角 allowable pressure angle
- _& C/ Y- l, y+ k. c许用应力 allowable stress; permissible stress; l( K$ p* {& ~' B4 x
悬臂结构 cantilever structure
& b: f% e) u8 ^& M+ k6 R悬臂梁 cantilever beam/ w) k6 E5 V: F9 n( A& [
循环功率流 circulating power load
Q/ }# J6 U5 J, b旋转力矩 running torque
/ K; e {+ V/ K旋转式密封 rotating seal: L: U- O/ |1 }" D3 C$ {, ^
旋转运动 rotary motion- ~4 X& Z8 v- |1 K& E
选型 type selection% x: B3 b+ g3 J W/ W
压力 pressure
( X' g% V* j1 V& t压力中心 center of pressure
2 M4 N$ d( T# ^5 Y& i/ e+ ?4 L压缩机 compressor
% B( l" v* W7 V. u压应力 compressive stress
* U+ b' e6 w b8 ~0 d( c' h压力角 pressure angle, M+ {) n6 O }, u* W1 K3 ~5 T. x
牙嵌式联轴器 jaw (teeth) positive-contact coupling
8 H6 v8 P) a) [; y' H( a雅可比矩阵 Jacobi matrix
& a- e/ F5 k( N摇杆 rocker6 k( t3 ?% i( j+ ?
液力传动 hydrodynamic drive' }8 r ^. T0 s4 Y4 x
液力耦合器 hydraulic couplers, R2 r. p" \) D& Y
液体弹簧 liquid spring
) a6 Z3 N. t+ \/ y, t液压无级变速 hydraulic stepless speed changes
7 Y- h& m5 v9 x& D# U液压机构 hydraulic mechanism' `# A* w8 N+ \5 k
一般化运动链 generalized kinematic chain
6 v) r: } \& t9 a移动从动件 reciprocating follower' ]2 \: d* D4 ~7 \- G
移动副 prismatic pair, sliding pair: l9 ^1 Y3 F" c* y$ q# N7 B5 ]
移动关节 prismatic joint
3 o3 K% \3 `: s% m移动凸轮 wedge cam, |. l" Z% _1 D( f
盈亏功 increment or decrement work1 U+ p- C7 @& W! a- h
应力幅 stress amplitude
1 l9 \& d( k, A* F3 L9 {应力集中 stress concentration5 u |! o4 ]0 y5 F" J* V/ U
应力集中系数 factor of stress concentration* O% p8 k' O+ F6 z/ p( w3 ^+ t
应力图 stress diagram! F$ j. Z( i# O5 i* z+ C
应力 — 应变图 stress-strain diagram- g! y# G* L: S6 o
优化设计 optimal design7 F1 C L8 m: T: n5 g ^
油杯 oil bottle& p) j/ _4 C! h% v; i8 u# I3 n4 A+ ?
油壶 oil can5 M: J1 r2 o/ q& |6 L, q+ l
油沟密封 oily ditch seal6 ]: a" {8 \3 _' r# v2 B p
有害阻力 useless resistance
7 y1 m& _/ a f5 M/ F% R3 c$ w: d有益阻力 useful resistance
3 p' y3 u; H( i" ]+ t有效拉力 effective tension
) p5 u6 J- i' D有效圆周力 effective circle force+ G0 b2 D8 E, }" a1 }2 T' g* c
有害阻力 detrimental resistance+ [9 L; @" ~# D( A- r M6 T8 B
余弦加速度运动 cosine acceleration (or simple harmonic) motion
0 l$ [* q* G' x$ C+ Z& F) y预紧力 preload5 t$ n) Q3 R7 d- p) P
原动机 primer mover |
发表于 2008-2-21 11:42:15