曲柄滑块机构 slider-crank (or crank-slider) mechanism8 u! v( }/ m, K1 J
曲柄摇杆机构 crank-rocker mechanism9 b+ j# C' T. p, K8 x/ z
曲齿锥齿轮 spiral bevel gear! d5 c& o% G. ?7 L
曲率 curvature3 H# u8 G1 E3 V3 V( F+ k2 y
曲率半径 radius of curvature
1 b# P: d1 G! _+ T$ h x7 G曲面从动件 curved-shoe follower3 U, L$ j j3 @2 M2 Y$ Y
曲线拼接 curve matching
6 i2 m( A2 f3 I曲线运动 curvilinear motion E7 V4 C F( J/ M* o7 w
曲轴 crank shaft8 t" t/ ?9 P( m, L2 [$ ]
驱动力 driving force$ K0 R& a5 D Q4 [4 z
驱动力矩 driving moment (torque)
2 m8 Y: Q2 j6 K4 {: b全齿高 whole depth# |0 O) W) K- f; n+ e5 q) \5 f5 q4 H
权重集 weight sets
7 K; S9 ~/ T' N5 d& n) H, K1 G. |球 ball# d; T, V K, E4 Y3 m
球面滚子 convex roller
7 p3 n5 H% H$ y! V, h球轴承 ball bearing
5 S" _) B u- k+ F: t! M球面副 spheric pair
0 w K' _1 K% I8 q! p# k球面渐开线 spherical involute
, ?) q* _8 U5 X' t- U j8 Q) B& n) k球面运动 spherical motion) l% ?9 ?3 T8 V
球销副 sphere-pin pair
% J0 z, b( ^5 t7 _! P% L球坐标操作器 polar coordinate manipulator) ] s: x H2 H% s
燃点 spontaneous ignition & O: f" I# T2 L; v4 J3 c0 v+ p3 G8 _
热平衡 heat balance; thermal equilibrium
5 q- D/ p/ O8 f5 ^人字齿轮 herringbone gear
. ~0 Q7 C. ~# P8 d6 y/ D! J冗余自由度 redundant degree of freedom5 ?* U4 p6 k6 c; E
柔轮 flexspline
' ^5 i- `4 o$ p+ e) F' P* M( F4 k4 W- t柔性冲击 flexible impulse; soft shock
- X7 N" Y3 P$ ]2 h7 a- ]& p柔性制造系统 flexible manufacturing system; FMS& U: N3 z7 ^/ f4 U7 U i
柔性自动化 flexible automation
1 Q7 `- f7 M. ]# f润滑油膜 lubricant film
; {% C/ g4 L" w7 ?) e: p! M润滑装置 lubrication device" h1 f# r- j* D% u
润滑 lubrication
! Q8 q$ z1 _) w润滑剂 lubricant p8 L- e8 a& E6 N
三角形花键 serration spline
0 D; {: h8 T# R* K3 d( d$ f三角形螺纹 V thread screw
8 f( M2 }0 {) M3 b三维凸轮 three-dimensional cam! t- y( k+ \4 {. r5 q7 W
三心定理 Kennedy`s theorem
; R5 Y( a& t& m, y砂轮越程槽 grinding wheel groove1 a" e% |' l. ]( y8 W
砂漏 hour-glass: | T o1 Y# c3 [% J; y! q( y
少齿差行星传动 planetary drive with small teeth difference: Q% W) V( ^1 C% f- k5 c
设计方法学 design methodology' D6 q' D5 g+ b3 P% U& j. d+ }
设计变量 design variable5 j9 K, K5 v1 k
设计约束 design constraints5 m# a2 ~+ Q1 c |6 d8 W2 @
深沟球轴承 deep groove ball bearing
/ r5 ] Y$ [# P7 v4 T! l0 f生产阻力 productive resistance
3 C; [0 T# }0 X% }升程 rise/ e7 S% e. x. c% G
升距 lift
8 f% X' l- n/ e! i$ ]实际廓线 cam profile
( V! g& b+ E, s, i) \1 b9 _2 G十字滑块联轴器 double slider coupling; Oldham‘s coupling
& s9 B4 _" f& C& u/ F矢量 vector5 Y( ~: V4 b* Q' w9 ?/ J
输出功 output work
5 [- ]# w3 y+ S/ q输出构件 output link, Y, S" @2 [3 n1 I& d! f0 x
输出机构 output mechanism0 {9 j U0 r; L8 b! y' s
输出力矩 output torque. `# R* n( Q1 A; W5 l0 ]
输出轴 output shaft
& F% @- X# D9 u9 O输入构件 input link0 q& Q+ ?; m3 X! F0 ^ Z: @
数学模型 mathematic model
" h3 |! e# t8 K- F# z, ~4 s实际啮合线 actual line of action5 ?9 s5 V# @8 U N+ ^4 p
双滑块机构 double-slider mechanism, ellipsograph' N: b# n5 ?5 A/ h% o% t& `7 |
双曲柄机构 double crank mechanism
f4 ~" e7 j& _; ^2 h, \双曲面齿轮 hyperboloid gear: F Q8 Z- w: N+ J I
双头螺柱 studs- b7 B( v* R9 I6 I" A
双万向联轴节 constant-velocity (or double) universal joint
t% X: n( {. }双摇杆机构 double rocker mechanism
" g2 k( P+ O2 O双转块机构 Oldham coupling
# b# v W; d& f2 O9 @& y双列轴承 double row bearing
; t0 u$ ?6 V7 y' ^. z) M% }双向推力轴承 double-direction thrust bearing
: E/ N; F5 G0 d' i* h% W5 Y6 M松边 slack-side
( r/ w: K* V" [1 X2 k" G4 N顺时针 clockwise7 R/ G4 U% W8 |' O) m( |- u
瞬心 instantaneous center# g" V5 b1 R) X( S& A
死点 dead point S( f! L$ ^; L& q. {6 P3 R) h! L. X% a3 Z
四杆机构 four-bar linkage2 |4 ?8 [$ o1 ^* `0 i! I
速度 velocity
7 z0 D z0 W, ?- h0 q {速度不均匀 ( 波动 ) 系数 coefficient of speed fluctuation
5 ?( `% D- s) F9 T2 b" C/ {$ x速度波动 speed fluctuation% [- g6 k9 d0 d$ ]/ Y3 M' o+ V2 Y% b
速度曲线 velocity diagram/ ?" O3 S& Z$ @0 S+ \. u2 c" U
速度瞬心 instantaneous center of velocity
: q3 T; W; N' ?2 |塔轮 step pulley 3 d+ y( k; J: F1 n8 s% w) }' h
踏板 pedal
/ m! w/ f4 B6 F- i" ?; g台钳、虎钳 vice& G+ L3 l, q! _/ R, |8 `5 `7 l# d
太阳轮 sun gear
$ v7 _& a8 ?2 N$ Q" u弹性滑动 elasticity sliding motion
o% {3 F3 ?3 t- l- t. L- |弹性联轴器 elastic coupling flexible coupling: O5 u$ V, ?+ f& f
弹性套柱销联轴器 rubber-cushioned sleeve bearing coupling
2 m2 F6 Y; m7 ] o0 @$ F套筒 sleeve
1 J' |6 _$ _# f B2 N% c梯形螺纹 acme thread form
" p' ^& {+ y$ K2 V特殊运动链 special kinematic chain) P! p) n6 }$ ~0 r- k. W& A
特性 characteristics; Q- Q. J0 V v4 r2 q* {
替代机构 equivalent mechanism: u1 T" C: G5 _
调节 modulation, regulation W8 C q: R# t" z' _8 s
调心滚子轴承 self-aligning roller bearing: [" r0 z o" s9 l% I# D
调心球轴承 self-aligning ball bearing
3 Q- r' ]4 Q# c; N# ]/ }8 p调心轴承 self-aligning bearing9 A4 W0 K' s B
调速 speed governing# d0 ^+ J* i) d! N
调速电动机 adjustable speed motors
% U8 j. s2 X2 X/ g( l调速系统 speed control system* L9 y/ ~9 M3 F* u
调压调速 variable voltage control
- W+ h% d( l% C调速器 regulator, governor
c5 t X7 Y$ t! Q6 _' D1 r铁磁流体密封 ferrofluid seal2 @- T, W/ Q# A9 X! Y5 x! ~- q
停车阶段 stopping phase
; U" t m4 x) U2 m* d' t, L停歇 dwell6 x/ T7 s* l1 q; u- |3 b& P+ f: G. p
同步带 synchronous belt
$ m4 P4 w$ ]) \9 s4 C9 t7 h同步带传动 synchronous belt drive9 y+ w+ I, j8 U# ~) d* n
凸的，凸面体 convex2 @* g/ @6 k* e) G, O; `
凸轮 cam4 D9 T" C; g/ A& _6 ~- f
凸轮倒置机构 inverse cam mechanism$ `& |5 A- L9 m! \' o
凸轮机构 cam , cam mechanism
D4 P( r1 n- g. y* \凸轮廓线 cam profile$ f: f/ ^/ R5 @1 J+ O+ ]
凸轮廓线绘制 layout of cam profile: h/ a, ?# x' z
凸轮理论廓线 pitch curve) H4 D/ r4 D. L) L& z
凸缘联轴器 flange coupling
* W S* ~5 q$ Z' V# O图册、图谱 atlas1 ^+ |9 P7 E5 E$ s
图解法 graphical method
. R! R( {( {9 q7 u1 K推程 rise( m* Q) J" K4 y& [: R1 G
推力球轴承 thrust ball bearing N; f8 @8 p4 ^' l! h7 {* w
推力轴承 thrust bearing& Q: h4 _% C1 s- ?' y, i
退刀槽 tool withdrawal groove* T- L+ h% @5 o @0 x
退火 anneal1 T ` R# t) E- |9 N+ ]7 u: V3 ~
陀螺仪 gyroscope9 \' E' D6 R4 @+ S+ ~
V 带 V belt
# P- j3 ` ^/ \外力 external force
4 h- s: h( p. t$ } j0 S6 \' E2 q外圈 outer ring , g: k) t" }1 M4 M0 m
外形尺寸 boundary dimension7 [& t" Q; w- W# V& j
万向联轴器 Hooks coupling universal coupling8 H/ Y' O* p- P8 b# n
外齿轮 external gear
+ ]) t, W; f, p1 U; |* ^弯曲应力 beading stress; t: {& ], \5 a7 O& L
弯矩 bending moment
* m) n6 o- R/ h' P腕部 wrist
$ Q+ c1 `0 [2 n, v# }2 c, p往复移动 reciprocating motion
& p7 X5 H* T5 }5 V9 N2 w! R) U往复式密封 reciprocating seal( ^- G- c, Z3 F: H' j
网上设计 on-net design, OND# v" O- I" o4 r# @3 `* c0 i
微动螺旋机构 differential screw mechanism
- E6 C- E% m, i. z0 y9 G i位移 displacement
! m% {) @' L. Y1 H: E* r位移曲线 displacement diagram
* ?: b( v3 x! p位姿 pose , position and orientation5 M! E. i# r" Z. w: c3 L
稳定运转阶段 steady motion period
2 n. o- r% T6 V3 R8 {# M5 n稳健设计 robust design4 w. ]+ K. T+ q1 s* l+ g6 \
蜗杆 worm3 C* z: j! A' j
蜗杆传动机构 worm gearing9 b! F9 v: \& \; l4 y* F
蜗杆头数 number of threads! F9 a, c9 @, n1 i
蜗杆直径系数 diametral quotient8 e; ` C$ a0 F9 U, B/ Z3 F
蜗杆蜗轮机构 worm and worm gear: R z* `7 ^- b4 D) L4 u
蜗杆形凸轮步进机构 worm cam interval mechanism
4 P6 s3 {: P6 j& [# W蜗杆旋向 hands of worm# g/ { J* f! P; \
蜗轮 worm gear+ h# w! x5 b; c
涡圈形盘簧 power spring: \0 F9 M% N4 J
无级变速装置 stepless speed changes devices
9 ~6 n, ~$ x3 T9 t5 |+ F无穷大 infinite8 A0 C" N% C8 r$ Y+ y8 C
系杆 crank arm, planet carrier 1 y4 }' q1 y/ u9 f
现场平衡 field balancing + Y/ c8 y( B. L. o
向心轴承 radial bearing
* N5 `* ^. R# i" S向心力 centrifugal force
( f' P3 d7 n$ W2 n9 \" o0 P* m: ?1 B相对速度 relative velocity
& S" J. |& F0 Q! F相对运动 relative motion
- F5 ~/ S% d! ?! \: ]% z相对间隙 relative gap) A# x! [& s2 R: d- q
象限 quadrant1 Z: e" i8 n- l) i7 ^- J
橡皮泥 plasticine7 t5 _8 P& r1 ^ X+ g
细牙螺纹 fine threads
$ T+ u) U N& {; R. @: ]+ ]销 pin
- J7 I2 l+ f4 T+ a$ H2 s8 c8 |9 b消耗 consumption$ S' E1 k' [' N* ?
小齿轮 pinion& m1 H+ q) \% `" `1 _ @9 n
小径 minor diameter/ n; {1 _) ?+ a' u5 N9 M n# j
橡胶弹簧 balata spring
5 I& C7 l3 [* Q' t6 Q8 r修正梯形加速度运动规律 modified trapezoidal acceleration motion0 _; V @ {2 ^
修正正弦加速度运动规律 modified sine acceleration motion& X) `2 z' @3 [. m9 m+ Y+ @
斜齿圆柱齿轮 helical gear
6 }4 [7 {$ K- w4 Q5 @+ i斜键、钩头楔键 taper key, x( g/ R7 \7 P& K& L) V3 c& }4 ~8 }
泄漏 leakage7 D1 K0 T+ k0 z( R: W
谐波齿轮 harmonic gear' p) z2 y& ^8 y5 [$ B5 N) P
谐波传动 harmonic driving
# w4 ?% [ b% z8 y: o谐波发生器 harmonic generator
, p: e* o4 O4 `. {$ t7 k; h3 M斜齿轮的当量直齿轮 equivalent spur gear of the helical gear4 D' S) q0 L5 u: b6 t% ?
心轴 spindle6 n' M1 x6 b& ]' n" W
行程速度变化系数 coefficient of travel speed variation
# N6 o- [3 T' n5 L行程速比系数 advance-to return-time ratio! Y6 U1 x. K; J1 j: J% t
行星齿轮装置 planetary transmission
+ _' U' o0 C( v" t/ l行星轮 planet gear" R: i/ C: R) x1 C/ r: h
行星轮变速装置 planetary speed changing devices
: Z3 H4 T! v6 b- r, E行星轮系 planetary gear train
6 t( k' G6 Z: _8 S形封闭凸轮机构 positive-drive (or form-closed) cam mechanism1 `" y8 o9 x1 s& x
虚拟现实 virtual reality
t% U& t5 c* Y8 O6 ^( ]7 f虚拟现实技术 virtual reality technology, VRT
! W) ?5 c$ ~+ [" ?+ r) `, x虚拟现实设计 virtual reality design, VRD
% T8 Q/ ]8 d! `# a) J8 H9 {6 ]" a z7 X虚约束 redundant (or passive) constraint* h; Y5 m) l4 j i$ G+ _
许用不平衡量 allowable amount of unbalance
* r# y3 U) v9 u& [8 c- H许用压力角 allowable pressure angle
7 O) o7 F, `3 j许用应力 allowable stress; permissible stress
( k' p# S* k# k) M2 k, |) `" @悬臂结构 cantilever structure+ {3 n# d0 g+ o2 @2 t: z
悬臂梁 cantilever beam/ g$ x n. J g# K L) C
循环功率流 circulating power load
0 [1 z8 z4 ?- R8 t旋转力矩 running torque6 v' n( e8 j: Q$ K5 W# W |9 F
旋转式密封 rotating seal
0 h2 K! W7 M/ M$ r5 G. N6 M" i旋转运动 rotary motion5 l4 z5 C6 k9 z9 Z
选型 type selection
# `$ W9 |4 a8 M' |) {压力 pressure
+ h! E% b! p% H* ^压力中心 center of pressure 0 \3 g8 F8 [% S4 o5 X
压缩机 compressor, s6 T% ^& q5 H5 p
压应力 compressive stress2 r$ F, R7 T; x' F" T9 n
压力角 pressure angle4 U- Z: i9 R8 {& N% m% x
牙嵌式联轴器 jaw (teeth) positive-contact coupling+ q1 n' ?5 y1 k @$ }- w
雅可比矩阵 Jacobi matrix
; [6 q/ Y; b" Z, C' V/ ?摇杆 rocker9 ]! Q7 I5 G+ r# O6 `
液力传动 hydrodynamic drive0 I6 o3 v: H% k3 E. u0 O% q
液力耦合器 hydraulic couplers+ j( V' ~# F7 l1 m
液体弹簧 liquid spring( w& d2 O" f: h" W! w3 r* @
液压无级变速 hydraulic stepless speed changes
9 c6 y3 h N* p# _! k( j! T液压机构 hydraulic mechanism4 ], D% v) G; }* M
一般化运动链 generalized kinematic chain
) k- A" y: j4 n1 M移动从动件 reciprocating follower
. X/ T& I/ d' E! v2 l4 J移动副 prismatic pair, sliding pair
8 x* j& @! N. v* f1 ~* }% a. Q移动关节 prismatic joint
* M: y$ y; j, u- i7 V移动凸轮 wedge cam. g: W& F! v* V
盈亏功 increment or decrement work
1 u3 z+ j! G1 k3 ]应力幅 stress amplitude
% ?0 e8 B. m6 x' T8 a" N: V" Z$ v应力集中 stress concentration8 K, v- p: D6 D( m- ~) R* Y/ K3 U X- L
应力集中系数 factor of stress concentration
" |& q- n2 N. f7 m( T% t3 K应力图 stress diagram
0 x0 v( \8 p1 c; H# Q0 C应力 — 应变图 stress-strain diagram) t) K# V! s! J
优化设计 optimal design
) E. b/ a$ h* G. C; R3 ?油杯 oil bottle
3 k, R4 n0 U E+ G, }6 u8 G油壶 oil can
h2 f4 |! H, G. G油沟密封 oily ditch seal* W- {) r* M* y; k, f+ C2 o
有害阻力 useless resistance! f$ ?/ ]! v! ~$ n! d+ E
有益阻力 useful resistance
. }' I' n y, v5 x2 L D有效拉力 effective tension
. M: m0 a, b9 M2 q6 c有效圆周力 effective circle force+ x8 Q) ^% E1 @3 k% U3 y0 ]4 C
有害阻力 detrimental resistance" N1 l+ `9 M, c/ W0 l% j6 j
余弦加速度运动 cosine acceleration (or simple harmonic) motion3 B( ?4 T9 z5 M- h) ]/ d
预紧力 preload0 y1 e2 D0 T8 C9 ^
原动机 primer mover |
发表于 2008-2-21 11:42:15