对称循环应力 symmetry circulating stress
1 W- Q$ B8 O( C/ @- p0 ~, G对心滚子从动件 radial (or in-line ) roller follower0 e$ }# R! h6 X: ?1 K& D3 Y
对心直动从动件 radial (or in-line ) translating follower q: Y# c: Z* }- y; d: N: n/ c' j
对心移动从动件 radial reciprocating follower5 R V: r& {' j" I+ g+ f2 @
对心曲柄滑块机构 in-line slider-crank (or crank-slider) mechanism
! q. c/ t, V) m/ P多列轴承 multi-row bearing
- j& S7 ^0 P6 ?+ O g" Q多楔带 poly V-belt" ]: {2 U" u4 w( ?7 `
多项式运动规律 polynomial motion
. S4 L2 q% H. D多质量转子 rotor with several masses% E) r" X8 B. b8 a; E- I S
惰轮 idle gear
) ^1 R s( s) [8 E5 H1 x额定寿命 rating life8 F U, K! u: I' d3 g' u. o
额定载荷 load rating
* u3 \7 n3 K# lII 级杆组 dyad5 ^+ j5 _' R. P: Y* C' P! G8 l" p
发生线 generating line # t3 p; R; }) ^
发生面 generating plane 8 o& A0 n+ L# i- V2 x
法面 normal plane
6 h/ w2 m' ^. P, w法面参数 normal parameters
# D8 }* H' K0 ]; g% v, a8 ?/ k8 t法面齿距 normal circular pitch
) K& e. D" R* C0 q: i8 J法面模数 normal module7 y. H4 {4 q! s! ]; r; d$ {
法面压力角 normal pressure angle" Z5 x0 \) j# B" H2 G
法向齿距 normal pitch) B2 @8 R F/ R$ J8 T7 d
法向齿廓 normal tooth profile1 B3 d" i1 E- R% P0 o# i% h; B
法向直廓蜗杆 straight sided normal worm, q* V7 K3 b" L9 M% ]2 `% z4 f
法向力 normal force* S: e `8 L7 Q0 S7 G/ u0 T1 l2 b
反馈式组合 feedback combining
) o; j2 I' ^9 L0 U$ ^反向运动学 inverse ( or backward) kinematics4 b# J* h7 `+ A/ c2 G/ {; k9 x
反转法 kinematic inversion
1 l7 A# |: z) o2 H; q8 B9 m- f* x反正切 Arctan
/ L0 h r( Z+ u8 h范成法 generating cutting
, h4 Q: [* x. f5 s仿形法 form cutting4 ?7 [* p9 y7 _* K+ W7 \
方案设计、概念设计 concept design, CD! D" W) j. i; A) V/ ]. o
防振装置 shockproof device
( w& A9 g) K+ R) M8 d飞轮 flywheel
g6 \3 h9 ], n, a9 n- C飞轮矩 moment of flywheel3 |8 u* S5 F- M9 ~$ E
非标准齿轮 nonstandard gear
. H/ X4 a4 S; ?非接触式密封 non-contact seal& S. r1 I4 z7 x/ {
非周期性速度波动 aperiodic speed fluctuation
7 @( P9 X1 X9 E, ]' y非圆齿轮 non-circular gear& N) X$ P4 D/ h! l6 h
粉末合金 powder metallurgy2 y* M' Z" P& p9 i3 _. c
分度线 reference line; standard pitch line
: C( q: d: @ B0 O分度圆 reference circle; standard (cutting) pitch circle
& e& l. w! b% g分度圆柱导程角 lead angle at reference cylinder* c: r" O0 K9 o5 L$ [" Z- ~9 p
分度圆柱螺旋角 helix angle at reference cylinder; E7 y6 ~: ]2 [; ]# I
分母 denominator
, s/ A |- l" @. ^分子 numerator
2 {* @8 t3 i! x* l. u8 ]- V分度圆锥 reference cone; standard pitch cone
! X n; {7 r% p- h5 U分析法 analytical method
$ i/ X. q& X% Q! _" v' z1 u封闭差动轮系 planetary differential) a9 t. v3 R! P
复合铰链 compound hinge
7 o$ E0 c. r8 L4 h7 N复合式组合 compound combining
. j2 c6 t7 }5 J/ G复合轮系 compound (or combined) gear train$ z; s& }& m7 }
复合平带 compound flat belt
0 a/ z J" @* _. N复合应力 combined stress# r! X+ Q5 ?; } p# _( }; ^2 U
复式螺旋机构 Compound screw mechanism
+ {1 |2 c" C3 ]3 V# v复杂机构 complex mechanism
; c1 n ^9 a5 P. E- D/ h杆组 Assur group
! P* a. x( y9 I6 m干涉 interference
) g+ n2 |0 s: v6 f0 j9 z刚度系数 stiffness coefficient
! t! h5 @' h. u2 @刚轮 rigid circular spline4 g1 n6 B' r# Q6 u$ ]
钢丝软轴 wire soft shaft
J; B4 E: M" o刚体导引机构 body guidance mechanism
# v# C6 U4 \% P+ S刚性冲击 rigid impulse (shock)
* D. e! M! D. t9 j' i刚性转子 rigid rotor1 }5 u; |6 M8 ~4 q
刚性轴承 rigid bearing3 ]) w3 a. j7 f$ [: m
刚性联轴器 rigid coupling' m( n. U% w5 g
高度系列 height series# ]1 S* g2 P: ~) }9 l M' G$ O9 W
高速带 high speed belt
: \6 [/ p- p" M/ J/ ]高副 higher pair7 ]4 ~. M- Y$ s, T+ X! Z" \* z
格拉晓夫定理 Grashoff`s law$ P4 X( O" r/ L
根切 undercutting- w) J4 l$ e& e* | b% B
公称直径 nominal diameter
. e R# K- f9 |8 u高度系列 height series
! D7 s9 T4 D* ]- f5 X0 s; P功 work) Q6 m1 D) m1 r" |1 p0 n
工况系数 application factor
; }" r! W/ g+ t工艺设计 technological design
& C% M6 [7 |- G8 w' f工作循环图 working cycle diagram
! b' R6 m/ y" H8 O工作机构 operation mechanism
& |) |/ A+ L( {4 J8 e" R" p工作载荷 external loads; z2 |5 D, X! u4 U/ f# ~! O7 f' R0 }
工作空间 working space0 o2 B# |5 e: q @, f1 b9 K1 h
工作应力 working stress+ d, A: M$ _ o4 i/ Q9 a" \
工作阻力 effective resistance
# U$ [. {; r: c; r( I1 x工作阻力矩 effective resistance moment
Y0 f+ B. m- A8 x公法线 common normal line
; L" N) ]& Z6 ~! E公共约束 general constraint2 m0 b5 }; K9 M/ p k, S# I, Z5 R# c+ [
公制齿轮 metric gears
1 X1 H: @) {* u' y' p功率 power+ F0 M7 ^% A2 B
功能分析设计 function analyses design, C' Z9 {/ K0 |' }8 q0 ~
共轭齿廓 conjugate profiles
, D- \. k! E6 G/ Q共轭凸轮 conjugate cam
4 C7 S- Q# m3 d6 U* J! t$ @. J构件 link
6 N1 O1 t0 |' \9 q2 s2 s( Z% l鼓风机 blower- Q- a0 F8 K1 X1 I
固定构件 fixed link; frame
4 u+ m2 s, q# Z. l. d t! q3 v固体润滑剂 solid lubricant
2 ~; F# M5 {; D9 X! ~" e; f3 X3 Q/ G3 h关节型操作器 jointed manipulator
' r8 g; o: H1 L4 W7 H7 ]5 q惯性力 inertia force
|9 Z3 x, ?+ q& Q2 i惯性力矩 moment of inertia ,shaking moment
2 I+ x7 }- ?+ y3 p0 Z惯性力平衡 balance of shaking force
5 W. [) r/ d+ _2 }. U9 Z3 U. X# l5 ?惯性力完全平衡 full balance of shaking force" i5 D% s1 w, K. p7 D) @
惯性力部分平衡 partial balance of shaking force$ S: K( P V; J; d0 U: W2 O
惯性主矩 resultant moment of inertia
6 K$ `5 W$ O* E: y惯性主失 resultant vector of inertia( L+ j9 E$ i: e! z3 ?7 W
冠轮 crown gear
6 T5 ^& Y% L- S3 _% j, ]广义机构 generation mechanism
) j# O) [. T6 I0 G* K广义坐标 generalized coordinate8 z& X* i, W( l& I5 a
轨迹生成 path generation) B5 k+ \+ v+ x0 l' o. r0 e- W1 C
轨迹发生器 path generator
5 A" S+ f7 ] ~: `& u滚刀 hob" e+ s" Y7 E6 w0 \
滚道 raceway
* }4 h+ x2 b0 n" q9 N滚动体 rolling element& ?/ w3 E: I; M! ~6 i: L8 c
滚动轴承 rolling bearing3 K' t1 v" \0 | Z5 ^7 L4 s
滚动轴承代号 rolling bearing identification code- N1 j; c; `9 i/ j3 F9 y
滚针 needle roller) ?8 H+ b8 t+ w% W3 z2 X) P5 |" _& Q
滚针轴承 needle roller bearing& j. y: m% m( R4 {
滚子 roller
( Z6 [+ N$ L1 r5 F滚子轴承 roller bearing) m5 n1 W& W0 [) @7 V6 I8 k9 h( H0 F
滚子半径 radius of roller& u8 T7 T3 v% R: t t2 t
滚子从动件 roller follower4 Y" y5 T, R6 w* Z: Z& }
滚子链 roller chain% O4 O% z/ v- }, t% e4 Z
滚子链联轴器 double roller chain coupling
( `$ A8 ]( B# ^0 q4 T$ b滚珠丝杆 ball screw
$ J9 G# \) d: w2 B& w( I" ~& o$ P( `滚柱式单向超越离合器 roller clutch
+ L& I/ \, Y$ J: G) U* G% ?过度切割 undercutting
; U) o* o' t4 }函数发生器 function generator % C" G0 s8 X. J; K
函数生成 function generation
, P2 ?' H( [' i% G" M1 H* D: s& e a含油轴承 oil bearing
) R, m0 b- W& ]/ z) m6 U耗油量 oil consumption
0 J5 [& K5 W5 F4 }+ C" t耗油量系数 oil consumption factor; u3 r% x5 J; W. U" \4 {
赫兹公式 H. Hertz equation+ k, c- {$ A# q& e4 }0 G/ b# B
合成弯矩 resultant bending moment" ]9 U! B3 i w1 I; C
合力 resultant force# ^5 C' R& X" Z8 [3 L8 f; c
合力矩 resultant moment of force
. ~9 K V) X5 K9 L6 F7 H黑箱 black box8 J7 ^7 d) i: y5 Q0 A1 r
横坐标 abscissa2 D8 k7 z5 L' _% o3 n* v
互换性齿轮 interchangeable gears
: g0 n& [5 ?; p" x. D花键 spline
7 L Q( R3 c+ ?8 z" E% a滑键、导键 feather key- E& Y. w* n0 B% @8 L/ b! j
滑动轴承 sliding bearing5 ^2 R( P" ^( G4 H' M' p
滑动率 sliding ratio: q$ h1 p" z5 M) d* N& ]- G
滑块 slider4 e8 w: }9 \1 G
环面蜗杆 toroid helicoids worm) a6 J% w0 B9 i4 S( V N- L
环形弹簧 annular spring8 ^3 D. u, b+ w# Q; i3 C; [
缓冲装置 shocks; shock-absorber5 ]1 T" b0 ]& |/ ~
灰铸铁 grey cast iron9 n& V" Q4 I. [ v
回程 return* Z: a$ [6 H6 @& S: [2 z
回转体平衡 balance of rotors
+ T. A, {( C8 j+ s8 b7 V/ f混合轮系 compound gear train
! L8 I s0 ~% \" Q积分 integrate 7 A- I& Q2 K4 I& s. g: @* T
机电一体化系统设计 mechanical-electrical integration system design ; R7 z1 t; w0 F9 k& G
机构 mechanism
) t( P+ {, |* Z: h) @机构分析 analysis of mechanism
( n1 ^8 c1 m3 q( z3 {机构平衡 balance of mechanism3 ]5 v" x! ?; z# h; r0 {
机构学 mechanism
9 N5 p4 s L. F$ W机构运动设计 kinematic design of mechanism
; b4 ?$ \3 _* N& o+ y机构运动简图 kinematic sketch of mechanism6 @4 A4 M6 {4 l# b& f- X6 Q" l
机构综合 synthesis of mechanism
. @7 A( I2 g9 Z$ ~4 h* O2 ?6 [7 h机构组成 constitution of mechanism
8 T) X- {' q1 n2 ]0 P3 Y机架 frame, fixed link
# V0 j, o$ t2 ~$ @# ^机架变换 kinematic inversion; y- @6 h- i. O) s
机器 machine4 X( Y8 U. ] p' x3 ] k/ ~( j' |
机器人 robot
/ n& j0 X1 E% M机器人操作器 manipulator
! ^8 P! X4 X3 C+ m- G+ T机器人学 robotics
$ Y) U3 b- v! [& m; T技术过程 technique process
$ k1 n4 M% m0 U$ c3 Q2 e7 p* \技术经济评价 technical and economic evaluation
7 |( d7 Y6 J$ e技术系统 technique system
1 T% r5 K3 E, h' _机械 machinery7 v4 h- H0 o3 {# @5 K
机械创新设计 mechanical creation design, MCD
1 s- F0 @1 `/ X机械系统设计 mechanical system design, MSD8 w- j2 o4 R6 G& ?. w# _
机械动力分析 dynamic analysis of machinery
, d2 Z) o: S4 W+ \3 q) n机械动力设计 dynamic design of machinery
5 p/ K) y& c/ z; {0 Q机械动力学 dynamics of machinery' S% P* t0 B; W* x3 [# _; [
机械的现代设计 modern machine design$ J {* j( F7 y7 M; _) N
机械系统 mechanical system \% H& b/ `8 s& C
机械利益 mechanical advantage
* S5 {9 g0 x+ F机械平衡 balance of machinery
) F8 ]( e1 `& ^) U- ?& L机械手 manipulator4 o$ r2 ^7 V6 Y4 A) n& P
机械设计 machine design; mechanical design9 I$ ?* [/ a' Y5 A; T5 `
机械特性 mechanical behavior, Z7 O1 o5 s1 E
机械调速 mechanical speed governors
) _9 c- h7 Z* ^ F机械效率 mechanical efficiency8 A0 C; _ y9 k. h
机械原理 theory of machines and mechanisms
- d t/ _6 q: p; H) u# j机械运转不均匀系数 coefficient of speed fluctuation
- N& t2 F) ^7 F$ \# R" k3 s3 h7 D# m1 G" s机械无级变速 mechanical stepless speed changes
# l Q6 @, R) H! K5 O* z1 R$ f6 x基础机构 fundamental mechanism
' X# o6 n6 W' {9 Z: K4 a基本额定寿命 basic rating life
. M7 y2 ~, s( h, h基于实例设计 case-based design,CBD8 v% Z. R* |3 F" Q
基圆 base circle
; Y* f# f: v0 [: M! s, S' C基圆半径 radius of base circle
8 T' R& s, E+ h4 z基圆齿距 base pitch
! Y4 f* O5 N, n3 k: ?# I( X基圆压力角 pressure angle of base circle
; v4 s' o! X9 y4 m: H基圆柱 base cylinder
# q& e/ a5 L9 v/ u b基圆锥 base cone) K8 U- z) [# b6 F8 [- H2 C7 J
急回机构 quick-return mechanism
9 ~8 X8 G/ G& S8 M% b. P6 K. X6 I急回特性 quick-return characteristics' j |. Q$ O7 Y" T
急回系数 advance-to return-time ratio8 S) G- m5 s; P+ i0 G& \1 N4 b
急回运动 quick-return motion2 Q; `8 V% T/ T
棘轮 ratchet
' G9 A m5 C' d. s& X" B/ d棘轮机构 ratchet mechanism
9 w8 P8 f( F" w$ n, u棘爪 pawl
# u! S% o8 x8 C. `# I6 [/ o极限位置 extreme (or limiting) position
4 }1 B' n+ H# Y6 Z0 g: {3 O极位夹角 crank angle between extreme (or limiting) positions
7 k) C+ N4 j- h! P9 ~. l/ z计算机辅助设计 computer aided design, CAD
; n. J, t$ n; E* {9 E N+ i$ B计算机辅助制造 computer aided manufacturing, CAM. d$ _/ f/ R* h Y' `* n2 k8 G: n
计算机集成制造系统 computer integrated manufacturing system, CIMS
0 z" T0 w1 Z5 m* R计算力矩 factored moment; calculation moment3 s9 [3 ] c, N8 v4 R* J/ m, u
计算弯矩 calculated bending moment$ I! `. _0 Q2 W: ]6 {* g# g
加权系数 weighting efficient
' }; a4 G4 i3 s- w) r加速度 acceleration
; d. X- x; C' @# }* R) A" M加速度分析 acceleration analysis2 T* E, Y6 y) y7 Q' g+ i
加速度曲线 acceleration diagram
9 }' i6 U" U# t2 k# [: L9 I# s尖点 pointing; cusp
3 P, t( r) @# ^ K) {" ?尖底从动件 knife-edge follower
8 Q! k2 {6 e/ J5 P, M, g& U间隙 backlash; k' v6 D+ Z5 i8 w3 ^* U
间歇运动机构 intermittent motion mechanism5 t# \) z, m+ N* c6 b; u) P
减速比 reduction ratio
; U' n/ I j3 T6 \* l减速齿轮、减速装置 reduction gear- f+ ? b4 j, G- n9 g6 x
减速器 speed reducer) L% c6 X8 L, j" I
减摩性 anti-friction quality
6 @0 T" y! n$ t! L" ] H渐开螺旋面 involute helicoid8 J: j7 w5 F/ ^; F5 e5 M
渐开线 involute
2 @3 ~9 g; y: o' N渐开线齿廓 involute profile
; q4 N( N* V' i6 t/ O渐开线齿轮 involute gear) g0 G% ~+ M" F1 A4 m, m* s
渐开线发生线 generating line of involute
$ T( \0 F" u$ N8 i& Z4 y渐开线方程 involute equation
: ^5 C2 w# }8 \渐开线函数 involute function
3 a+ S* s; e3 N5 r! j渐开线蜗杆 involute worm. @+ `- A1 h3 v" K6 i% S
渐开线压力角 pressure angle of involute% c5 \; j, u- g+ ?% f4 f V
渐开线花键 involute spline+ p; A- m, [4 H. p7 T( F
简谐运动 simple harmonic motion
. r3 h7 N z$ W键 key |
发表于 2008-2-21 11:37:30
