对称循环应力 symmetry circulating stress8 d/ e8 F" e) L: k* a
对心滚子从动件 radial (or in-line ) roller follower8 R" i" F# r4 Z0 u4 i, S6 ]
对心直动从动件 radial (or in-line ) translating follower
3 W0 A& W( E# E对心移动从动件 radial reciprocating follower
: v; Z+ T9 ~: k+ [$ R, x- D* j对心曲柄滑块机构 in-line slider-crank (or crank-slider) mechanism
) Y0 ^2 k9 w* U& \6 h多列轴承 multi-row bearing; [2 x# h5 u; R% k& s. Y `
多楔带 poly V-belt5 D, L7 [( O6 q! R6 s
多项式运动规律 polynomial motion
+ z+ D7 ?0 i4 S v多质量转子 rotor with several masses$ b& U2 V! x" f1 X/ f
惰轮 idle gear& ]/ A# p3 s! w5 A) Z3 C' n" H
额定寿命 rating life4 `1 x; B1 ^5 T: A' w
额定载荷 load rating0 J" h8 Z* z: n8 S, j! X/ R
II 级杆组 dyad, T4 o( O) E1 y' A. P9 N6 K: Y c
发生线 generating line 4 z l6 l! p! N, I1 x. T; c
发生面 generating plane
$ h) n6 r- q6 q2 R; y法面 normal plane! ?% D/ G; R0 o$ a/ r. h; t- D
法面参数 normal parameters
0 ^' X: U f$ Y法面齿距 normal circular pitch5 a4 I/ o. p2 q( J( ]8 ]6 U3 M# B3 C
法面模数 normal module% W9 G4 z1 ~0 k) M; a1 i
法面压力角 normal pressure angle3 C/ T! M6 f) Q0 E8 {6 X' Z( O
法向齿距 normal pitch
1 u' T( x9 j5 P% C3 i法向齿廓 normal tooth profile
0 V2 x: G, g. _/ w: ~& y法向直廓蜗杆 straight sided normal worm8 u7 E4 l- W1 J+ R' @. b3 r
法向力 normal force
6 J A' F0 J8 S反馈式组合 feedback combining8 I0 O' s, C' [4 ^& h+ u& h
反向运动学 inverse ( or backward) kinematics
0 p4 Q0 @, q+ O: k- X7 I: x反转法 kinematic inversion
$ i4 \# H5 N+ D( a$ y( C反正切 Arctan
8 \/ L+ m. n% k; {% A范成法 generating cutting& V; A: g! H F8 D3 d
仿形法 form cutting
4 u- \- h$ N* |# t* P' p方案设计、概念设计 concept design, CD
' U! @. @. B6 G0 Y2 B防振装置 shockproof device
2 Q1 m( A8 r% e$ j飞轮 flywheel6 M% O* m( m, |0 ~( J8 d
飞轮矩 moment of flywheel! W+ L7 g; b2 d/ u4 P
非标准齿轮 nonstandard gear
' F- F) W! J: J$ h非接触式密封 non-contact seal
# ]% _4 u" k$ O4 e* a8 J1 m# Y: j非周期性速度波动 aperiodic speed fluctuation
. _& u; z* ]/ u) E) o4 K非圆齿轮 non-circular gear9 }1 g# |; N" d0 j
粉末合金 powder metallurgy
0 U! L- a$ p6 A分度线 reference line; standard pitch line
i) H2 [' e/ |: z# ?" w* l分度圆 reference circle; standard (cutting) pitch circle
2 y1 x+ b4 y+ \分度圆柱导程角 lead angle at reference cylinder* r# Z6 t" W) \' t
分度圆柱螺旋角 helix angle at reference cylinder
, n. i7 d* A2 Y6 W+ @: {分母 denominator& q( n9 Q1 ^- \# y+ d
分子 numerator. F$ l2 O7 Y1 V6 w. w
分度圆锥 reference cone; standard pitch cone
( Y/ }# B( ~7 t" Y5 t0 | t分析法 analytical method! K t$ V5 ~# k a1 ]7 w
封闭差动轮系 planetary differential1 f5 Q4 ^ p0 o% C
复合铰链 compound hinge( `+ l/ t% ~) S3 \' m2 `! ^
复合式组合 compound combining
; T* g) \ f$ O M复合轮系 compound (or combined) gear train
7 ^* P9 s( m& r8 U U( l复合平带 compound flat belt
; v7 n! L9 ^2 H2 ]$ ]% A. i复合应力 combined stress2 b. l' U' B& l! b* X# r
复式螺旋机构 Compound screw mechanism2 r8 p3 x/ n5 c( n0 q
复杂机构 complex mechanism; c4 u; ]0 U, ^9 I2 X5 S b
杆组 Assur group 2 l2 d* s& D& _1 D. m3 p
干涉 interference
s2 {/ u4 ~5 Y7 D刚度系数 stiffness coefficient8 x7 ^$ t( N, P' ^
刚轮 rigid circular spline1 m' E) @( n. k6 O) c- P) g
钢丝软轴 wire soft shaft4 u5 E; O* I4 B
刚体导引机构 body guidance mechanism
: ]% W. d: q/ N8 f) R刚性冲击 rigid impulse (shock)+ S) f( M3 ]! d
刚性转子 rigid rotor1 }2 b* e$ [6 V# u) e2 m+ P: c
刚性轴承 rigid bearing% q$ |$ D6 p l6 B- V
刚性联轴器 rigid coupling: z; U/ H2 d5 Z/ D" I( N" P& s! _" N+ _* F
高度系列 height series
) c& z& y6 W# a3 \# y9 U/ Q高速带 high speed belt
% [/ Q/ ~2 T! E8 m8 \! `高副 higher pair
2 x# z2 d+ F4 U# A% \1 |7 d2 C格拉晓夫定理 Grashoff`s law
( n! M) R+ b ?根切 undercutting! H, F) B4 E& j8 P: m- M. ~0 U* q1 ~
公称直径 nominal diameter
) g. q |3 ~3 j% R高度系列 height series" j; W1 |- |- c. G& C
功 work% O0 \9 R( `& s
工况系数 application factor
% ]9 c0 U% Y h+ q工艺设计 technological design, E! ~* _' U5 f0 h% r
工作循环图 working cycle diagram
6 ?: o3 j: |- v5 K工作机构 operation mechanism6 @6 q; ]% @$ q! K, p( p( @* [
工作载荷 external loads# B3 ~8 _6 ]- X# [
工作空间 working space
; m; Z6 w! ?% ]: T, Z工作应力 working stress
3 B# x. v/ G: B; J0 C% X8 t, z0 f( F工作阻力 effective resistance% W/ u: R& ~& F: b) N( Y. m
工作阻力矩 effective resistance moment
: E0 |6 `5 o* `# g# b1 j1 j+ {4 G公法线 common normal line
! C8 E+ H+ Q2 l公共约束 general constraint" K5 |& t5 I5 Y4 X
公制齿轮 metric gears
+ j# c7 C: _- O功率 power
. _# u- y6 g# F; h/ O m5 {% W功能分析设计 function analyses design
% c- e. r9 M ^" i* V1 M' T共轭齿廓 conjugate profiles
0 s# n5 B+ \ ~7 ~- `4 n共轭凸轮 conjugate cam
- G! @8 C; n, n构件 link1 H! s7 Q2 Z! e' G/ X8 ~" k3 L; d
鼓风机 blower
: @! k* G2 c- ]; E: X固定构件 fixed link; frame
" e* V! Z6 ^ k. T0 Q固体润滑剂 solid lubricant
N t8 [6 }) n关节型操作器 jointed manipulator
: F9 t4 |1 e! ~8 I惯性力 inertia force
& Q8 T, `3 R5 k: m6 t惯性力矩 moment of inertia ,shaking moment
8 F) X5 H* s% l$ T" T+ r惯性力平衡 balance of shaking force
4 v, h- K, r( V9 d; W惯性力完全平衡 full balance of shaking force
/ Q* E$ ?+ v( z" ^" ?9 h0 W惯性力部分平衡 partial balance of shaking force- L- I) R% }+ K. z/ u
惯性主矩 resultant moment of inertia4 I) B/ E3 T0 G* X0 T$ B. h$ k; ?1 I+ H
惯性主失 resultant vector of inertia' t6 c- B. q9 S) e) s/ B
冠轮 crown gear% W' I0 u8 b0 r# c. X9 W
广义机构 generation mechanism
. O9 i: ]) {2 v% T广义坐标 generalized coordinate
* [0 J9 j" o( N0 x轨迹生成 path generation7 V4 n [3 p; M& ]5 B( \
轨迹发生器 path generator
6 R! {' K0 W/ e1 d. X) X滚刀 hob$ C' N' s4 |9 C# A: i* S8 ~* z
滚道 raceway
2 g. {0 M4 p" x/ @# `滚动体 rolling element
4 a$ V9 \; ^1 v; _8 G; L7 @# w3 O滚动轴承 rolling bearing( x# \4 A/ {9 I1 D# f" C Q) h
滚动轴承代号 rolling bearing identification code. E# T9 F6 {, ^! F4 b" Z
滚针 needle roller
, |6 F2 Q1 b* T2 m$ ?& w滚针轴承 needle roller bearing" `) `; i" Z9 L. W0 ~ `" s
滚子 roller
3 C: z3 \8 y+ |滚子轴承 roller bearing3 T" O, }6 i1 G8 `) ]
滚子半径 radius of roller, K& H# `9 k) i. d
滚子从动件 roller follower ~6 } j: D3 }& F& h7 P
滚子链 roller chain! ?( a$ h" C5 t% Y9 c
滚子链联轴器 double roller chain coupling
5 n0 d d/ f% L9 q, d滚珠丝杆 ball screw
6 R1 r1 D n, c. e, a滚柱式单向超越离合器 roller clutch
! i: j% K$ i& r; I$ E' h过度切割 undercutting/ s) g. D$ M. i5 h; ~- `
函数发生器 function generator 4 N9 i, h% W$ x/ O! v
函数生成 function generation
) E" b# X0 V, r5 k+ `/ w含油轴承 oil bearing) P' f* `: |( i; s* u4 u S
耗油量 oil consumption
; I, V: ]. C* U5 p* S* X( s耗油量系数 oil consumption factor8 f( w5 w g) t, Q& [: x
赫兹公式 H. Hertz equation9 B5 v- v+ |$ _2 O: }, m
合成弯矩 resultant bending moment1 T& d5 b, f- f; S+ Y) C3 b
合力 resultant force
# H6 ^2 R. X* f2 n$ R! |9 k5 S8 J合力矩 resultant moment of force7 K$ U6 @; C7 l
黑箱 black box: X3 ]# }, z, a) R- x$ |8 M2 v
横坐标 abscissa9 y0 K* M0 E9 _3 \3 ]6 a" N; o
互换性齿轮 interchangeable gears9 Q' J$ [9 C3 u. M7 v: X
花键 spline# A p3 t4 x" o3 t
滑键、导键 feather key( `" d# J# Q2 y; {! y
滑动轴承 sliding bearing/ x! [* Y9 k$ m6 ~* W- `% j4 e1 ^& @; @
滑动率 sliding ratio/ ^+ [0 o0 ^% E& F ]6 S
滑块 slider
' T1 _1 Y! Q, m环面蜗杆 toroid helicoids worm5 w$ h( p0 n3 g9 q
环形弹簧 annular spring
h: O5 {& W2 d9 l' L b- \# J缓冲装置 shocks; shock-absorber
' @! g* C! h I1 P4 p! f灰铸铁 grey cast iron
- S9 ^; o/ a1 ?. ~; Z! ?; s回程 return
3 M- T* u2 d+ M f% d) T回转体平衡 balance of rotors
3 z7 d" T8 z5 l- ~3 b0 F1 D9 m混合轮系 compound gear train
I- K; ^. P% P" Q积分 integrate
; ?+ A) D8 V) \. f8 ^机电一体化系统设计 mechanical-electrical integration system design # D6 k" z; T( ~8 s
机构 mechanism& s* g: z& k+ R# c
机构分析 analysis of mechanism3 S5 B% c( _, W9 X- C4 h
机构平衡 balance of mechanism1 {8 E: e) \% k& @7 m+ C
机构学 mechanism+ i; g* F7 R4 ~* r
机构运动设计 kinematic design of mechanism
2 |7 O/ @* T) T& ~机构运动简图 kinematic sketch of mechanism
6 \5 I8 g3 v! t/ e2 f6 D$ Q机构综合 synthesis of mechanism
/ ~; R5 k6 P" b, ]; B8 y4 G机构组成 constitution of mechanism; }& G8 e$ X* {6 m5 b
机架 frame, fixed link
0 R/ h+ K$ {7 s机架变换 kinematic inversion8 K5 l, g$ A5 l( u
机器 machine
, o; u! `: F- g机器人 robot* [6 G/ S* M( u$ k
机器人操作器 manipulator
/ d& s; Q) \# ?* m% F7 g9 Z机器人学 robotics
' f. R8 x3 c* J; i技术过程 technique process5 Y0 \) b& _% y* O( r; t/ T- T
技术经济评价 technical and economic evaluation' _, {7 M3 O4 [, u7 b$ C
技术系统 technique system" Q2 E5 y. L! M7 X. u6 m! } G* Q. n7 l) ?
机械 machinery2 }# E# o8 J" Z6 d
机械创新设计 mechanical creation design, MCD7 \9 M3 b8 i$ ~) a" l- V
机械系统设计 mechanical system design, MSD2 k; T5 ^0 r! F0 S5 F/ v9 @
机械动力分析 dynamic analysis of machinery
8 E* _1 b" X& w2 ^8 K! N机械动力设计 dynamic design of machinery* `/ P0 b. q. T7 R
机械动力学 dynamics of machinery
. p3 U# C; ]7 D$ e, q机械的现代设计 modern machine design
# T1 F, u9 R7 y8 h" y5 m V9 i; i机械系统 mechanical system' X& v6 s1 J$ K' h1 W
机械利益 mechanical advantage
* ^" S# B8 D) b6 [: X; V机械平衡 balance of machinery
! ]: Z7 }# E; u: {2 A2 Z( b机械手 manipulator
' O: x9 t O$ b, N( k/ S6 I2 k机械设计 machine design; mechanical design; `( a, h: Y5 ~0 x7 ^
机械特性 mechanical behavior
- q" x) m9 R0 i! [) B" S. K机械调速 mechanical speed governors" I* m, ^5 b1 p
机械效率 mechanical efficiency
) t: s% X L8 S( |) f i r机械原理 theory of machines and mechanisms
8 L, R6 j5 U6 h+ v( J0 |* f: R机械运转不均匀系数 coefficient of speed fluctuation* x* z% v5 W# N( V" z+ M
机械无级变速 mechanical stepless speed changes
" r! x) c' j# B3 G: Y# y基础机构 fundamental mechanism: z* v, \' c" | B) [
基本额定寿命 basic rating life
8 `6 m9 O: g ?, S基于实例设计 case-based design,CBD3 U* k5 a, j) ~, o6 j b* c% A( X
基圆 base circle4 Z2 K0 F' p! @% B. ^
基圆半径 radius of base circle2 t# p( Y. c5 _+ Q- |6 I
基圆齿距 base pitch& |( O" D5 E" }
基圆压力角 pressure angle of base circle
6 s, T" ~! w* k8 k! W1 j8 u8 O基圆柱 base cylinder$ |' I7 x; o/ ~# t7 X |
基圆锥 base cone7 y7 ^- i# j) r$ {( q& n0 y+ [
急回机构 quick-return mechanism
}' F) f! Q+ q' P/ C急回特性 quick-return characteristics$ w6 B" Y* X/ @
急回系数 advance-to return-time ratio
+ A8 E, M$ _+ g+ S7 i急回运动 quick-return motion
* T0 ]" Q3 U* |' ^! F2 T2 D# G W棘轮 ratchet
$ @5 b" \8 X. p棘轮机构 ratchet mechanism
Y* [ y2 P( P1 O' U. Z棘爪 pawl' x/ ~: t+ ?. O v
极限位置 extreme (or limiting) position* D0 ?0 ^- `9 a9 S; K
极位夹角 crank angle between extreme (or limiting) positions; T C8 s9 g9 f& r J
计算机辅助设计 computer aided design, CAD, ?8 ^( ^* i) c: P
计算机辅助制造 computer aided manufacturing, CAM& q6 D, I7 v" g
计算机集成制造系统 computer integrated manufacturing system, CIMS' D# l7 s5 n* z6 x0 ~
计算力矩 factored moment; calculation moment
1 L% z# K& J2 b8 F计算弯矩 calculated bending moment
" r9 ?! J# S- |% M- g' k g加权系数 weighting efficient$ ?, }- X; w* y; M) x$ L* R
加速度 acceleration: {) d' y/ ~+ P
加速度分析 acceleration analysis) C! m3 J' P+ V6 }7 ]8 [7 O t2 l4 d
加速度曲线 acceleration diagram
; b- ^* I/ P3 `4 T* u! r) ~尖点 pointing; cusp3 H, E' V, R1 S
尖底从动件 knife-edge follower
+ R: [' Z. I; D' d4 B" t间隙 backlash
6 I! X* b0 @" Y% H间歇运动机构 intermittent motion mechanism8 X& V1 P& ?$ E" Z" w6 @/ G
减速比 reduction ratio
K% ^$ T' Z1 H8 T6 F, ~" F+ D+ w& h减速齿轮、减速装置 reduction gear( Z6 {8 V, P, d* ~2 z G
减速器 speed reducer
9 T( }$ Q. Y4 B9 A" U" A! _; Z; o减摩性 anti-friction quality
. E! u1 i ?5 a6 y2 R渐开螺旋面 involute helicoid$ K) X! q6 @- c1 ^2 F5 d
渐开线 involute
% h- Y) ~ T( E0 } T! r$ U渐开线齿廓 involute profile
- r. M: P8 t8 I渐开线齿轮 involute gear
. c h* ~( a) L4 g渐开线发生线 generating line of involute
5 P6 w7 t* f8 m* j) x0 E" p: m渐开线方程 involute equation
6 m: x) k; D' T! U渐开线函数 involute function; [/ K( ? N! k
渐开线蜗杆 involute worm
) t+ {8 c' X& v1 K4 y7 }- f渐开线压力角 pressure angle of involute
3 D+ l; ?* V9 b- \2 Q% k" [渐开线花键 involute spline
0 y" F" [# p/ M% z简谐运动 simple harmonic motion( ` |, c+ h1 y
键 key |
发表于 2008-2-21 11:37:30
