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标题: 机械设计名词术语中英文对照表(2) [打印本页]
作者: 闪电惊虹    时间: 2008-2-21 11:37
标题: 机械设计名词术语中英文对照表(2)
对称循环应力 symmetry circulating stress
6 S7 _* P' a$ u: ^对心滚子从动件 radial (or in-line ) roller follower. {, {! v/ s+ i1 ~3 o- E  I( \
对心直动从动件 radial (or in-line ) translating follower5 |% `. ?) n1 r1 h9 q
对心移动从动件 radial reciprocating follower
3 i. c, J' r: j9 G对心曲柄滑块机构 in-line slider-crank (or crank-slider) mechanism
1 g1 B/ F* P7 g6 a. P1 Y! ]多列轴承 multi-row bearing
+ I* B3 u3 ]- `8 N8 o% h多楔带 poly V-belt( z. U1 u4 u- I6 s
多项式运动规律 polynomial motion
- t8 N& S& q; w4 X; o: ]多质量转子 rotor with several masses
2 x7 r% g2 v1 k1 U6 w8 j惰轮 idle gear
# g2 {% X: @9 d5 @" d3 X0 W4 Z额定寿命 rating life
) w! v" V. B% K/ X5 C额定载荷 load rating) Y! l# d5 n& ~5 @; X! h
II 级杆组 dyad
& X4 f( c$ w; c/ }发生线 generating line
- ]( h7 [% A- p+ h* M4 N发生面 generating plane
" [+ y, \* v( x$ l6 A$ k1 q法面 normal plane
3 m4 P( _/ F/ e# p* r" _4 P# q' v法面参数 normal parameters
" W9 j& ?4 e4 E. x& u( D& E法面齿距 normal circular pitch
# c* p/ ]( ]4 Z8 ?* Q3 W法面模数 normal module
9 I' [* s3 @4 y: o$ D法面压力角 normal pressure angle
0 v/ D; [  b; y; L" u0 J. W法向齿距 normal pitch- z  J% M5 v3 u  i8 W% ~1 E! f: m
法向齿廓 normal tooth profile
, Y& o% t: h4 p5 g# k. A法向直廓蜗杆 straight sided normal worm. M2 h* h' q4 g/ a1 i
法向力 normal force! T9 J! t! E1 q& f# T7 P  z
反馈式组合 feedback combining
8 F; |8 t% g. I5 J6 @反向运动学 inverse ( or backward) kinematics- e! k5 X0 j, f& E7 ^. q! h
反转法 kinematic inversion7 _  k* }8 V, c& r4 v
反正切 Arctan
. _9 s3 j" o& Z范成法 generating cutting: f7 Y# X  L. ]) L" z" E
仿形法 form cutting
/ J! B) `( F( B: a& a3 R) [方案设计、概念设计 concept design, CD
6 ]/ H) R5 B. D/ H2 o防振装置 shockproof device
" s7 M  G) w  J( {: c6 {飞轮 flywheel
* R1 U7 t9 ?/ g3 U' l9 U飞轮矩 moment of flywheel
; |. E/ n) f1 h0 f2 `非标准齿轮 nonstandard gear
6 S9 m3 X( p+ v非接触式密封 non-contact seal
# g" \1 K& ~9 K非周期性速度波动 aperiodic speed fluctuation
4 ~, d4 z, H/ ?$ d* D非圆齿轮 non-circular gear# g( z2 L+ g8 R
粉末合金 powder metallurgy2 U0 v: l! C0 f5 x0 r: O4 \+ p) s9 W$ j
分度线 reference line; standard pitch line; U6 r9 `5 o3 |' \8 R+ J9 U
分度圆 reference circle; standard (cutting) pitch circle
; t- {- Q2 U1 l分度圆柱导程角 lead angle at reference cylinder; h5 p1 X, V; Y9 X, k9 U
分度圆柱螺旋角 helix angle at reference cylinder
7 W1 p+ n/ ~) d+ g3 H% F* a分母 denominator
3 n1 i7 m* R( U0 I  S) A, @分子 numerator  s- o- M* }( Z/ @" q& E
分度圆锥 reference cone; standard pitch cone
) s/ t4 [* b5 \  `* h, C3 q1 D分析法 analytical method6 e, V9 i' ^8 B$ k: }. y
封闭差动轮系 planetary differential6 q$ f# Q; ?  {* |
复合铰链 compound hinge
) P3 t$ u# W" i- e8 U: q2 b& L复合式组合 compound combining" U! [$ `* u4 `8 }2 F( ]/ L9 `- N
复合轮系 compound (or combined) gear train
; b) K* R: N& x  i8 ^+ Z% e% q% ^复合平带 compound flat belt
5 R) e( e; K* ^5 g* r复合应力 combined stress, X& s4 q+ j+ j' e, Z
复式螺旋机构 Compound screw mechanism
. g: N. F' h% F复杂机构   complex mechanism8 a9 ?5 ^4 A4 J3 w: D5 ?
杆组 Assur group 9 i: T+ T" K1 ~$ ^4 K' n# m
干涉 interference
% a  h) I: S3 V! H* y. p- z刚度系数 stiffness coefficient; P) g) ^$ W0 Y* F0 E
刚轮 rigid circular spline6 I) O9 b# A- Y5 C
钢丝软轴 wire soft shaft
6 K- H' U0 E+ |+ U5 Z3 g- o刚体导引机构 body guidance mechanism
# ]+ @3 h1 Z4 g) t* b% O" K! E刚性冲击 rigid impulse (shock)  O1 L+ n5 P& a. ?
刚性转子 rigid rotor
( l" c2 O: R7 E  B1 u刚性轴承 rigid bearing; o, z: O' M% i, ^3 i; Q
刚性联轴器 rigid coupling4 q4 l/ a% n8 v
高度系列 height series
4 w& O. k* j6 W8 L7 B2 ^2 ^, r! P3 t高速带 high speed belt
8 `* z% q" C' m/ Z% q+ i( X2 A5 J高副 higher pair2 O  K; ~' e, K( J8 H, M9 P" p
格拉晓夫定理 Grashoff`s law( n$ e/ a9 r: w7 Q2 |0 ^
根切 undercutting
! M/ ]( m+ o7 A3 x* Y/ U# T3 D公称直径 nominal diameter/ b8 G6 G, L; ^
高度系列 height series
8 z. B* ^+ c. p3 X! p功 work) z* R. L: I+ ^( V7 D
工况系数 application factor5 ]& f) U. V. s% c( Z& Z; ^+ O2 [
工艺设计 technological design, U2 C5 v7 E9 g; s4 _' u  p
工作循环图 working cycle diagram
  O% Z& c2 U. X4 e' V- g1 B工作机构 operation mechanism
# o2 @' |! |4 F. }- S- y. X工作载荷 external loads
# W. L! K* w& j- A! _工作空间 working space
2 p, t* ^4 W0 u# s  x工作应力 working stress
6 `" b9 L0 L8 a8 W9 M1 H% i1 ]; t/ [工作阻力 effective resistance
' y+ c7 ^% X, @工作阻力矩 effective resistance moment7 N: J: z# g) C2 g* e
公法线 common normal line
8 u/ _  J+ Q! b3 y3 Y8 ?公共约束 general constraint
6 k6 A: B) j7 m  e公制齿轮 metric gears- u" Y% u, p( H, M. d8 g- H! E
功率 power
+ G$ C4 n2 k- @) {功能分析设计 function analyses design2 V! Z9 |' x  f: E; `; e
共轭齿廓 conjugate profiles
" i. t# v( K1 z# V共轭凸轮 conjugate cam. P/ ~* w  t6 p5 `) Y* x) X
构件 link; ^7 P! C0 U3 g
鼓风机 blower
$ G% `7 Z  m" ]! K) s. z# D固定构件 fixed link; frame
: Z  G. m3 {; i# B固体润滑剂 solid lubricant5 d0 \- S: |1 `+ m
关节型操作器 jointed manipulator
$ ?4 y% I/ s/ V& G! ~0 A惯性力 inertia force
6 B  F! R6 C- h' Z  w+ z6 A惯性力矩 moment of inertia ,shaking moment) |" E+ y3 W" T, q
惯性力平衡 balance of shaking force5 w- l! k# H( H, j
惯性力完全平衡 full balance of shaking force
" X6 s! b; O' x  z- J2 U# m. N惯性力部分平衡 partial balance of shaking force+ a0 r& N& p+ z& f# c: Z* N  w
惯性主矩 resultant moment of inertia9 ^+ R* ^; k  m3 j
惯性主失 resultant vector of inertia' j( I8 F. b, C7 u! w9 T
冠轮 crown gear
8 f# M0 {0 w8 v( E0 [( J9 ]广义机构 generation mechanism2 v; U1 V3 |) z' _. K. a0 |
广义坐标 generalized coordinate
9 p1 u- t% j( W: Z$ s; p轨迹生成 path generation1 M9 D1 i; D  y# n: X, @1 g8 E# C
轨迹发生器 path generator
1 v) q0 w( g: M4 }滚刀 hob' w& e' T. Z/ c
滚道 raceway8 r5 {- a! w2 G. m8 b; y
滚动体 rolling element
4 B" s3 Q  w4 L' L8 X7 o滚动轴承 rolling bearing" q3 e9 P6 a) j* _  I& I4 a+ V( Z8 ^
滚动轴承代号 rolling bearing identification code
" E9 |# o$ o1 B- `% h4 Y: S滚针 needle roller
3 o% ]) l! z' O- h滚针轴承 needle roller bearing6 d4 P9 Y$ A4 M# t" ^% v/ E2 o
滚子 roller
3 l, p, t* C4 o滚子轴承 roller bearing& f% A1 R/ H% R  w4 J. ]3 ]
滚子半径 radius of roller
6 k1 Y3 K" L! W, a4 V滚子从动件 roller follower& d: D$ |: M' [& g
滚子链 roller chain
2 Q& q9 ~& Y% @滚子链联轴器 double roller chain coupling
3 O7 l  V! w0 t3 o0 w$ u滚珠丝杆 ball screw* E. w  v0 Y% a! j3 [
滚柱式单向超越离合器 roller clutch4 _5 c' Y% Q# I$ C7 G  C- I' }
过度切割 undercutting  J- o: T1 a& ^& ~3 \
函数发生器 function generator + s" d' ?9 ~6 [2 ?5 F# F" Y* L
函数生成 function generation & c7 I- z3 {. G
含油轴承 oil bearing
! I( R: A- U+ M% L  }, ]7 j耗油量 oil consumption
  `) H0 l" Q/ B9 Q( A' X耗油量系数 oil consumption factor
& J: K- F2 X  a, }) w) l# {赫兹公式 H. Hertz equation
5 o/ s# ^' H4 F9 p. Y合成弯矩 resultant bending moment( a( }! ^+ M1 G( }3 f4 q2 {
合力 resultant force) Z! O$ D; {  K: T4 U4 p! E: r
合力矩 resultant moment of force) ]2 f$ @4 @! _; _8 g0 u
黑箱 black box5 r8 m5 {* }$ `& F) o( b
横坐标 abscissa
8 j- m/ n$ n; d: G互换性齿轮 interchangeable gears( Q$ C. h1 P  s% `/ @7 ?
花键 spline
" P6 D8 ]& Y9 Z; W滑键、导键 feather key# u) [# X6 X1 q0 r# R
滑动轴承 sliding bearing
! ?: Q. r3 x% B8 y滑动率 sliding ratio
8 o; F/ x: u: L滑块 slider# r2 P+ c# _4 u# A; ~, U/ ~
环面蜗杆 toroid helicoids worm
" m1 x; v. f: {环形弹簧 annular spring: g" H7 |5 l6 ]# B& k1 ~
缓冲装置 shocks; shock-absorber3 J  |( {( G5 m* g0 K
灰铸铁 grey cast iron
5 c" @* b0 d- M, m回程 return
  r2 W) p1 U& h! G# W+ F回转体平衡 balance of rotors; b4 r! t) S  |% y' v" Q2 i
混合轮系   compound gear train
& @) {! ~( \- N积分 integrate
- q2 C* t+ P; h( l+ p5 `机电一体化系统设计 mechanical-electrical integration system design
0 p; t6 y2 N% c& \机构 mechanism5 K! c8 v0 X" r7 D* L
机构分析 analysis of mechanism
6 b/ X$ y, w+ C6 C* u机构平衡 balance of mechanism/ n9 |) ?3 _  L; a4 Y) k8 J
机构学 mechanism
# S8 W2 ?: S" a- d1 z$ X机构运动设计 kinematic design of mechanism
6 U! D$ @. Z, J; L* w机构运动简图 kinematic sketch of mechanism% {! a- T) r( d3 W% E- c
机构综合 synthesis of mechanism. f% ^, _  v' U" o& ^( [
机构组成 constitution of mechanism
6 H1 S3 X3 R* r/ e6 V# [5 C机架 frame, fixed link
! \- n' H3 X8 v% C机架变换 kinematic inversion
" j- x: q. h* y0 k' ?机器 machine
# I7 `4 H! `. r- j# M! y9 Q2 l机器人 robot
# S4 E' Q5 A5 g机器人操作器 manipulator' r" F6 ^) {- ?+ a
机器人学 robotics
6 i  V- l* J; e技术过程 technique process
7 W6 ?% [( j7 G5 S/ J& Y# Z4 y技术经济评价 technical and economic evaluation1 W+ I, x- M2 x" P7 V' p5 r: t. u3 j
技术系统 technique system6 R0 B' }0 M0 L( J4 v
机械 machinery& g) E1 U4 m( J6 Q, s
机械创新设计 mechanical creation design, MCD
  v+ g  [+ |' e5 w( B6 T3 Y机械系统设计 mechanical system design, MSD
2 y( Z- f4 C  z3 U0 X: X/ s机械动力分析 dynamic analysis of machinery
6 s% X' Z- p) V! b5 W+ O9 D6 C机械动力设计 dynamic design of machinery
2 {( H- b- K* k: `, P机械动力学 dynamics of machinery1 e3 ^" o* H& [9 m. H6 j
机械的现代设计 modern machine design: `# P! P+ C8 q* l# W9 L7 k
机械系统 mechanical system
/ x) G* O* I9 u3 K机械利益 mechanical advantage' s9 Q1 c' ^, }: [
机械平衡 balance of machinery9 z6 [( u- u5 h8 ^6 {
机械手 manipulator+ V! k6 k5 ]. C) z+ G* f
机械设计 machine design; mechanical design
* Z9 m2 a6 Z' ^! ?! ^机械特性 mechanical behavior) H7 R) N7 K+ e  y& g
机械调速 mechanical speed governors8 V; o, P/ C9 {- R  `% Y) p  V4 o
机械效率 mechanical efficiency
0 ~  f1 Y1 x" h4 R( l7 m; H5 d机械原理 theory of machines and mechanisms
6 N, _0 z) b$ d- h机械运转不均匀系数 coefficient of speed fluctuation
4 r1 P6 [, S' m机械无级变速 mechanical stepless speed changes8 V( W6 ]* @1 _% p$ W
基础机构 fundamental mechanism) J, a9 Y# E5 J2 m" A/ A
基本额定寿命 basic rating life
' Q2 Y7 u! b3 B- x, {$ C" Y- D基于实例设计 case-based design,CBD# G$ [- D/ Q5 ^, M! f
基圆 base circle
, i# R9 T1 s  Y. D" ]/ E基圆半径 radius of base circle
8 f$ D0 n* s- H, H/ ?基圆齿距 base pitch$ X4 [- h6 m) w8 I! f% Y8 {& A
基圆压力角 pressure angle of base circle
' J! n: o# D9 Q  b' @1 n- b0 C基圆柱 base cylinder5 C5 i4 D# b( \" c$ [, m
基圆锥 base cone+ y6 t# [8 t; `/ ~+ n# D
急回机构 quick-return mechanism% V6 R5 Y) l5 c7 Y
急回特性 quick-return characteristics) b" }4 A8 f) z0 `% \
急回系数 advance-to return-time ratio& F. y/ A' D* }! R
急回运动 quick-return motion
3 }; Y# g$ V6 a9 @  H, w* L" C棘轮 ratchet* d" y$ K& A  j, [( z0 ^2 k5 s
棘轮机构 ratchet mechanism
; O9 e. S# R3 I3 f8 i& I; }棘爪 pawl
, J4 y$ q7 `% I: }0 C; n8 i极限位置 extreme (or limiting) position* g7 z- e& t  c' d& T9 P
极位夹角 crank angle between extreme (or limiting) positions
1 v# W4 t2 [8 C4 ~# j* R1 ~2 y8 X  |计算机辅助设计 computer aided design, CAD+ M, @, O$ c2 G7 x/ d  r
计算机辅助制造 computer aided manufacturing, CAM" L! G6 q2 Y6 w/ W8 U  T. W
计算机集成制造系统 computer integrated manufacturing system, CIMS4 ?) t( [  `! R& |! @: m
计算力矩 factored moment; calculation moment; y2 v' T) U& _* E6 R& ^
计算弯矩 calculated bending moment# J& R. S8 l# |$ M% U
加权系数 weighting efficient1 z# O/ W6 @0 S9 A
加速度 acceleration
4 J! g, Z+ Y. V! V! g" ^" B加速度分析 acceleration analysis3 |( U. l5 v) d# r" ], V: S( v
加速度曲线 acceleration diagram
- b* y1 ~5 i% B& W* _& }, W0 j# c  Y尖点 pointing; cusp7 P* s9 I/ d  ~8 e, h+ Z
尖底从动件 knife-edge follower
- X/ g1 a$ x) O+ g% D间隙 backlash, j- a. u) G6 }. A
间歇运动机构 intermittent motion mechanism9 y: x7 N3 h$ x# K
减速比 reduction ratio/ }# C5 }  f* ?' J9 @! P
减速齿轮、减速装置 reduction gear5 g# E" w9 t: m% d6 Z+ H+ Q; }* \
减速器 speed reducer+ a" S. r# k" W, x  ^2 L# G' `$ X
减摩性 anti-friction quality
% W2 V, e% Y) b: @' s6 w0 b, \7 g渐开螺旋面 involute helicoid
) ~; x1 P8 r( q9 _7 f0 c" q" ?渐开线 involute
- ~, `4 ~- f( i% ^. M渐开线齿廓 involute profile9 n+ d7 L- P2 N% H  l; V: r
渐开线齿轮 involute gear
" c- z" C5 S  j渐开线发生线 generating line of involute2 T- |; M& Y* G# _$ {
渐开线方程 involute equation
6 t( {# P! ?6 [* G7 [2 B& S渐开线函数 involute function" a$ b  r7 H+ m3 [
渐开线蜗杆 involute worm
- C' J% s- e) J0 L* D8 ?  p渐开线压力角 pressure angle of involute
$ c# W7 Q$ y, s8 _渐开线花键 involute spline
' n) p/ R1 |# h% Z: f! B0 d( r- `简谐运动 simple harmonic motion
' `! j& I6 _% Y; e- f键 key
作者: 超格闲人    时间: 2008-10-20 21:57
标题: 好东西一起分享
好就一个字啊，不啰嗦



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