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标题:
机械设计名词术语中英文对照表(4)
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作者:
闪电惊虹
时间:
2008-2-21 11:42
标题:
机械设计名词术语中英文对照表(4)
曲柄滑块机构 slider-crank (or crank-slider) mechanism
A+ |+ T! V5 w* [/ W6 O: c
曲柄摇杆机构 crank-rocker mechanism
. @1 d3 }5 m; U0 v& y- V. k# d5 P! U
曲齿锥齿轮 spiral bevel gear
! S+ D1 N0 H& V0 C$ j. h
曲率 curvature
" K/ G4 L* F v$ _
曲率半径 radius of curvature
% I# c) g0 H6 ~9 w4 F
曲面从动件 curved-shoe follower
6 g! Q! d' ]3 d# V' V
曲线拼接 curve matching
. P# {* n: @/ l5 c3 m
曲线运动 curvilinear motion
4 j. ^1 {- X+ C0 ~
曲轴 crank shaft
3 Q i' A4 D* N9 E% N+ T
驱动力 driving force
& T q' g3 M" E {0 e, _
驱动力矩 driving moment (torque)
1 ^& r# R% H" O; X
全齿高 whole depth
* t3 c; a7 _) i
权重集 weight sets
- z' g# [& D7 N! d
球 ball
- v9 ] e2 \- `$ j
球面滚子 convex roller
% \% @4 j0 ^" o% Z5 r% o
球轴承 ball bearing
2 K' Y8 [& v) B) l
球面副 spheric pair
3 C+ g& G. l) Q" y- v
球面渐开线 spherical involute
9 r6 P: G5 C% P# u. R" B
球面运动 spherical motion
# z* k- {0 Y8 x! o# S
球销副 sphere-pin pair
" G8 E, K- w% z9 \
球坐标操作器 polar coordinate manipulator
( L W4 ^* E" c9 ~
燃点 spontaneous ignition
# r: U4 f0 N, A
热平衡 heat balance; thermal equilibrium
0 C! \, O; d( I' O' g! X
人字齿轮 herringbone gear
; V* p5 ~" g5 \- F( W& ~
冗余自由度 redundant degree of freedom
' B) G/ L7 j0 y. ]3 W' C
柔轮 flexspline
% j" K1 X |. M2 J* c: C
柔性冲击 flexible impulse; soft shock
9 o. w2 N& V4 K. X a
柔性制造系统 flexible manufacturing system; FMS
2 u3 q. e, i5 s. h4 @; C3 O) ^: E$ e
柔性自动化 flexible automation
/ n4 @% G8 S7 O. M+ u: g" @
润滑油膜 lubricant film
8 R0 m( b+ v4 q) x9 l, g
润滑装置 lubrication device
$ u+ q( K( G# |& i+ ]% C
润滑 lubrication
4 r j/ M& \( i3 k* p0 Z0 F. ?$ l( Z
润滑剂 lubricant
$ K( q# q: `+ D0 }
三角形花键 serration spline
( S$ f( s1 }# ~9 b
三角形螺纹 V thread screw
2 A) Q- T* z% e8 h6 {$ o, Y q
三维凸轮 three-dimensional cam
( u0 y4 f0 _; g) K9 W
三心定理 Kennedy`s theorem
2 ~% b; k* J9 c0 I
砂轮越程槽 grinding wheel groove
4 g i9 ^) \/ X3 O. ~& D
砂漏 hour-glass
, O- Y7 t' H: C: j' c3 R. O
少齿差行星传动 planetary drive with small teeth difference
% ]' }* P5 d5 A( D. E1 {8 u
设计方法学 design methodology
4 M; g; e# r3 t
设计变量 design variable
8 R/ v8 g; ]7 H/ b0 R
设计约束 design constraints
4 u" P' k" F4 R+ e
深沟球轴承 deep groove ball bearing
6 H2 i% Y1 O8 q
生产阻力 productive resistance
* r/ u7 a+ R7 j
升程 rise
2 l5 a; Y+ }2 K0 e$ \
升距 lift
" G: p! d/ u Q4 P
实际廓线 cam profile
( H2 \- k! o1 t/ `, K
十字滑块联轴器 double slider coupling; Oldham‘s coupling
0 S, [( } G: v+ H5 [3 K9 B
矢量 vector
9 C+ |2 \& | S
输出功 output work
2 R7 ?3 G2 A* ]* U, t
输出构件 output link
3 v0 J4 C, Y% s- h
输出机构 output mechanism
& f) `1 q. t) x6 l' b
输出力矩 output torque
7 ~2 Q' m1 q9 M% |$ B0 y* u
输出轴 output shaft
) k! F' H7 _7 A: h
输入构件 input link
+ G2 w' J' ]8 i# d
数学模型 mathematic model
5 S* R9 x+ m; L/ [' ~
实际啮合线 actual line of action
* m9 B5 N, s; w$ u% `
双滑块机构 double-slider mechanism, ellipsograph
' j8 V% \, s! t0 k a, [) G
双曲柄机构 double crank mechanism
+ w# y# t: W [2 m! h' Y% e7 u
双曲面齿轮 hyperboloid gear
* g2 f8 g2 `. B5 n7 C# C5 E
双头螺柱 studs
% x+ ^: y. z# D. {
双万向联轴节 constant-velocity (or double) universal joint
1 f6 n7 P+ w9 g# T" `6 O3 {0 i
双摇杆机构 double rocker mechanism
, d- l! s8 H. P
双转块机构 Oldham coupling
2 e9 {- o5 N. b. y9 S8 y' E
双列轴承 double row bearing
; e& m" b, l9 M4 S4 x
双向推力轴承 double-direction thrust bearing
$ t/ w7 A( j6 L) l) h/ ~) F. Z) l7 T
松边 slack-side
" q9 G6 Z+ p/ e4 F0 C
顺时针 clockwise
) }5 Z# W9 p% e# C5 D' X
瞬心 instantaneous center
% U3 V# `7 p+ |% W9 d( I3 R
死点 dead point
9 |( v8 l2 \" c, n! F4 x9 O" ^
四杆机构 four-bar linkage
* V& \, F& m# k* N, r
速度 velocity
2 p+ d8 ^! Y1 o" `) x! n1 m. F3 E
速度不均匀 ( 波动 ) 系数 coefficient of speed fluctuation
% I9 Y2 ]# |. E/ f G9 p* h
速度波动 speed fluctuation
, P' l+ S1 x/ p
速度曲线 velocity diagram
j. ~" F, D, d6 K, B3 g% U1 w
速度瞬心 instantaneous center of velocity
7 i8 p7 [" x% r. Y/ F9 r
塔轮 step pulley
( g" M. g* j5 U( v- d0 r! G
踏板 pedal
* l* l7 X' Q/ n3 v1 ? M
台钳、虎钳 vice
; _7 C* U/ ~, v9 y& q: U- _/ H
太阳轮 sun gear
9 L [9 m1 P0 ]% b/ X# C! n7 T6 ]" S
弹性滑动 elasticity sliding motion
3 \ f, ]7 F! a5 y5 u- x
弹性联轴器 elastic coupling flexible coupling
# W' F2 S+ X# H4 L: N
弹性套柱销联轴器 rubber-cushioned sleeve bearing coupling
9 O- S) e M5 ~8 f7 {8 s5 U# u
套筒 sleeve
, D( Q5 t! ]% r5 D5 p9 o
梯形螺纹 acme thread form
3 H7 t& S- D3 c+ _ S& \% [
特殊运动链 special kinematic chain
# D0 D5 ^0 A6 B* {! Y. a& F$ h
特性 characteristics
" f( X. `" {, B X3 d
替代机构 equivalent mechanism
1 W! B/ e6 A, T# U- y4 p
调节 modulation, regulation
S# c; N8 K4 c1 d& ]& ]& Z
调心滚子轴承 self-aligning roller bearing
' v+ A4 X4 l7 h
调心球轴承 self-aligning ball bearing
0 B0 n2 m0 I. [3 u; L$ X R3 Y+ g9 q9 K
调心轴承 self-aligning bearing
: @3 f9 t; ]$ ~, S5 N
调速 speed governing
! d, i3 Y) C" R2 d5 U, n, e6 Y7 L5 u
调速电动机 adjustable speed motors
5 h4 ~: P& V6 H3 o! f# m% T/ h( i/ E
调速系统 speed control system
- s6 g' f5 w0 k
调压调速 variable voltage control
# p% n0 F, h$ O5 S
调速器 regulator, governor
9 u6 R# N! ] h; y& ~3 W4 y
铁磁流体密封 ferrofluid seal
/ f9 t5 E" q' z- M
停车阶段 stopping phase
: f% a% S: s' r( q
停歇 dwell
& w& S" ^9 q' }% I, Y/ W: L
同步带 synchronous belt
9 a, v) ]. J2 |& O/ p2 \
同步带传动 synchronous belt drive
" j5 W' x/ a- u' |
凸的，凸面体 convex
1 l: [3 _6 T4 o6 K
凸轮 cam
4 C; i( P2 `( c! g
凸轮倒置机构 inverse cam mechanism
6 F z' q- U; b- t! B6 ?2 u7 p6 O
凸轮机构 cam , cam mechanism
: P) E- x6 A8 J j; B
凸轮廓线 cam profile
) P$ E1 o6 ]1 a' [9 a$ x; w! c
凸轮廓线绘制 layout of cam profile
7 ` H6 c, W) @/ H$ ~& T
凸轮理论廓线 pitch curve
+ x8 E7 [- ]' V
凸缘联轴器 flange coupling
/ O c% o* ]# Y. E! h
图册、图谱 atlas
& C* \, M+ X4 a r
图解法 graphical method
o% U/ b" N, H, d4 u4 b
推程 rise
: X+ R; q4 {4 c7 `: X: e; T% H
推力球轴承 thrust ball bearing
9 r( e; \/ E- K8 }
推力轴承 thrust bearing
G8 a0 b: U4 m6 Q4 H0 e7 @
退刀槽 tool withdrawal groove
# l( C- l* o6 W# V1 W) F6 ]5 U1 Z D
退火 anneal
3 n: Y' T3 U& f w/ o/ w- ~. O
陀螺仪 gyroscope
/ D9 [/ C# q5 }& V N8 H3 J, M
V 带 V belt
9 \+ }6 V( h+ M" s5 V* B& l
外力 external force
: F6 B) y" ?5 x& o& f( E- v! i
外圈 outer ring
( j( D; N0 _+ B8 ~
外形尺寸 boundary dimension
+ b+ ~, F" t3 t- U/ B: r( W, `) j2 n
万向联轴器 Hooks coupling universal coupling
& A2 T% Q! ?( S5 C* ]0 X
外齿轮 external gear
! B+ b7 ~$ J- F% P9 m% g
弯曲应力 beading stress
% r! S) | ]( w( i- B( M
弯矩 bending moment
, w: f$ a' r! m) [* a# M
腕部 wrist
+ ] x0 F: _4 f# p" O) b
往复移动 reciprocating motion
) G/ L0 h0 Q) O( O, F6 L1 S- ^- y: v# ~
往复式密封 reciprocating seal
8 a3 w9 Y# G0 ^) F( a5 N
网上设计 on-net design, OND
" ?& U9 }3 J: e+ W; \$ Z
微动螺旋机构 differential screw mechanism
* K2 z' u- c7 V" k) t+ a Y. V8 }
位移 displacement
, K1 E: b: z$ i" B t9 w) B3 o1 J
位移曲线 displacement diagram
- |# O* j! X# x
位姿 pose , position and orientation
$ q, P" M# }' T: j& X
稳定运转阶段 steady motion period
* _# }# p T) N7 G# t$ N
稳健设计 robust design
$ E. F+ U5 \: D, k( r; Y: @
蜗杆 worm
+ W" M. l% J9 C5 E
蜗杆传动机构 worm gearing
" i" D& q# I7 b' B2 a
蜗杆头数 number of threads
, S H/ ], i) V! M" r1 g9 u. z
蜗杆直径系数 diametral quotient
3 |; a8 s% t" f- F5 _( E/ e+ e. n
蜗杆蜗轮机构 worm and worm gear
! E0 Z- C# E6 k- F
蜗杆形凸轮步进机构 worm cam interval mechanism
4 z8 I* U4 q l, L5 A
蜗杆旋向 hands of worm
. ]: x) e" E9 {3 P
蜗轮 worm gear
; ~: x4 c; h0 u
涡圈形盘簧 power spring
- ~; r; R, L2 [# H* _% y& p
无级变速装置 stepless speed changes devices
0 R; n7 k; c8 u' U" Y; ]+ \; _2 C
无穷大 infinite
$ K' j; v7 w$ P) V4 @; r$ ~
系杆 crank arm, planet carrier
" f. }% d+ i4 d, H# U
现场平衡 field balancing
/ x( K5 @! S2 Y# H0 y' u
向心轴承 radial bearing
1 K8 E" f8 O) |- U; ]
向心力 centrifugal force
9 O- V: y" Y6 r9 l- |
相对速度 relative velocity
6 A0 M# ~8 B3 o k5 ]1 E
相对运动 relative motion
8 `7 k M3 U5 T+ S! O
相对间隙 relative gap
( N9 ^$ T7 }! L- L4 @) w8 E6 {
象限 quadrant
: I9 q; G9 w% g i1 t+ ?
橡皮泥 plasticine
; S9 x0 A8 j/ T0 [ @5 a; ?
细牙螺纹 fine threads
, z6 I6 f5 K4 q) _9 d1 @% _( f
销 pin
! G0 k# a; i# X" f$ }# G
消耗 consumption
$ n4 b% \+ D1 b# }. A6 J
小齿轮 pinion
: o- H' A3 [- c3 t
小径 minor diameter
. W9 o- m8 G I+ l. j
橡胶弹簧 balata spring
6 R# F$ y' a# P, a
修正梯形加速度运动规律 modified trapezoidal acceleration motion
, f4 e ?( n: v* f6 g/ R
修正正弦加速度运动规律 modified sine acceleration motion
4 S+ _; _+ w) ]5 x, [& v1 \ c% U8 u
斜齿圆柱齿轮 helical gear
, _- X+ i5 M( h1 F5 Q/ w
斜键、钩头楔键 taper key
1 q" F* M4 [- |; C9 m O
泄漏 leakage
& z1 R: Y/ w$ B$ ]% _
谐波齿轮 harmonic gear
# H. ]/ U( h; m5 s1 X' z. M
谐波传动 harmonic driving
( Y4 Q' X4 W! O% t) i0 o0 n; o
谐波发生器 harmonic generator
' S' ^5 ? D6 K: o ~$ w) V
斜齿轮的当量直齿轮 equivalent spur gear of the helical gear
$ ]; s0 K6 S/ Q* C L; L# }+ g
心轴 spindle
5 b* E8 V0 g1 A! A$ j b4 I
行程速度变化系数 coefficient of travel speed variation
2 v/ [% K" I% u+ n
行程速比系数 advance-to return-time ratio
% S. \: m/ \; I! F0 Q- |
行星齿轮装置 planetary transmission
. t" `/ P% r" ` E. K& X2 g: X
行星轮 planet gear
2 f7 G- Q, d( [5 _1 `
行星轮变速装置 planetary speed changing devices
9 \2 L) Q" ~, X) y# l# B$ W( ` m
行星轮系 planetary gear train
3 z! x, G! B4 a
形封闭凸轮机构 positive-drive (or form-closed) cam mechanism
' \5 v. {9 K O6 Y( _
虚拟现实 virtual reality
: D% Y9 Z( T$ b4 {% p
虚拟现实技术 virtual reality technology, VRT
+ B, z: R" g5 O. x& n& h7 f/ B4 J
虚拟现实设计 virtual reality design, VRD
/ N8 H$ O: Z6 J) i
虚约束 redundant (or passive) constraint
: t4 u' m/ b: `+ `6 \0 b
许用不平衡量 allowable amount of unbalance
) S7 M. N% M+ p8 k
许用压力角 allowable pressure angle
/ a9 ?8 g. W( F' l4 M1 M
许用应力 allowable stress; permissible stress
% ~! o5 T h! H! @) t* F
悬臂结构 cantilever structure
8 b1 T4 h+ d. v3 X8 T
悬臂梁 cantilever beam
) @7 E j. `! _- W& h7 R$ h: t
循环功率流 circulating power load
1 s$ c+ e) H2 ~8 ~; O
旋转力矩 running torque
, s/ O4 g' S+ f# J5 f( d5 r
旋转式密封 rotating seal
+ s" H+ S/ t" s! o; u1 n$ a2 N
旋转运动 rotary motion
7 O! ^; D) G3 v; T+ q# N. n5 ?
选型 type selection
' c! `4 |2 N+ P9 k0 e1 Y
压力 pressure
. Z/ u6 f. A# m' a. g% }
压力中心 center of pressure
; v4 C7 T& A& A F+ ^# d
压缩机 compressor
# `6 \2 d- @/ l) H# u
压应力 compressive stress
5 B }: m8 }" h4 f5 N- S
压力角 pressure angle
0 l3 e. w* d9 W+ b; X
牙嵌式联轴器 jaw (teeth) positive-contact coupling
2 q3 b" ~; Y2 r7 C& B2 p
雅可比矩阵 Jacobi matrix
* T4 ]" G" [9 o% ^
摇杆 rocker
5 G7 R" H4 Y& ]8 N
液力传动 hydrodynamic drive
% k C; g" G2 }) \0 t- `
液力耦合器 hydraulic couplers
2 p3 a6 F0 v& R8 W* f+ |
液体弹簧 liquid spring
D( ]0 V6 u* \
液压无级变速 hydraulic stepless speed changes
2 h) V% o' N. `- F9 M- W" ^7 _' ?
液压机构 hydraulic mechanism
% G: r& t5 s5 `7 w
一般化运动链 generalized kinematic chain
& k! p$ Y5 J m( j/ a
移动从动件 reciprocating follower
$ t: S2 o, k: x5 I
移动副 prismatic pair, sliding pair
: V- s) Q' W- G: x0 P1 Q9 Y
移动关节 prismatic joint
' U+ l1 W; \: x4 G8 _& f' I! L
移动凸轮 wedge cam
6 d# c% e/ t4 d- p& V
盈亏功 increment or decrement work
" }% C, Z, n$ d- n6 |
应力幅 stress amplitude
9 A+ e5 D V& B* E) l ?
应力集中 stress concentration
2 K0 `' M3 B1 y4 p
应力集中系数 factor of stress concentration
8 \3 G1 ^7 }8 v& g @
应力图 stress diagram
" L8 P, e. @" l& g" E: ]7 g/ l
应力 — 应变图 stress-strain diagram
1 c0 y: {& [8 k
优化设计 optimal design
. W9 G, z' s2 ^9 X) T& v
油杯 oil bottle
6 x5 [4 d7 G5 m9 x+ Z% n) H: U$ B- S- D
油壶 oil can
( @# x4 X$ j. M
油沟密封 oily ditch seal
% l$ d: L" W' }: X* Y3 x6 {
有害阻力 useless resistance
) H) F8 Z' J8 P1 `. K# |
有益阻力 useful resistance
8 p; c) D: h3 G5 {. Y0 y+ G
有效拉力 effective tension
! R2 y6 }* n6 ]) @
有效圆周力 effective circle force
# [2 W* O w% d% H% S9 o' v7 C
有害阻力 detrimental resistance
# ~; `7 n6 k8 {" p
余弦加速度运动 cosine acceleration (or simple harmonic) motion
3 x; w% P5 {3 p3 f& C
预紧力 preload
& t! W! P5 p' d! T- C2 a
原动机 primer mover
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