對稱循環應力 symmetry circulating stress
1 ^5 G' @6 P7 X" Y2 u對心滾子從動件 radial (or in-line ) roller follower
0 r: o1 M' Q5 ]4 c7 Z# }- Z對心直動從動件 radial (or in-line ) translating follower- h; u) A! w) N0 F* Y' \
對心移動從動件 radial reciprocating follower: N9 D" U4 Q/ ^+ a( P
對心曲柄滑塊機構 in-line slider-crank (or crank-slider) mechanism
. r0 i$ Z4 Z( }1 Y5 r5 \多列軸承 multi-row bearing1 r: P& a/ \% A) a
多楔帶 poly V-belt( l4 e* M' ^6 o8 W% b& Y
多項式運動規律 polynomial motion
4 p" w) i* B6 q# Z I% |6 z多質量轉子 rotor with several masses6 ^! m! U4 p! S- x" l
惰輪 idle gear7 H, S2 G( j0 d2 K9 g! J
額定壽命 rating life
6 L" \$ j: h, H$ z4 ~8 I額定載荷 load rating
0 d3 ]& X( }! S: X- S* Q+ FII 級桿組 dyad
0 L4 g6 H, p; B3 J發生線 generating line ! y9 r: M* n8 u: @* J; T
發生面 generating plane 9 y' N3 O- @& A: Z! R1 ]0 f
法面 normal plane6 e ^9 J' x5 F! w; i. D
法面參數 normal parameters( k& A/ Y w+ T4 M
法面齒距 normal circular pitch/ ?$ Z0 G& p D5 `$ T
法面模數 normal module( O+ Y/ n3 V# P, K; p0 i
法面壓力角 normal pressure angle
; X8 {6 V$ i2 e X5 M法向齒距 normal pitch
1 E0 o( [ p$ O法向齒廓 normal tooth profile
: q6 J9 H3 N( ?% X' l; E! c7 p4 T法向直廓蝸桿 straight sided normal worm
' t5 J' L; Z' h Y& v法向力 normal force j6 p) F9 U0 _
反饋式組合 feedback combining
) Z4 h6 K O# B; g. }$ O& ^) v8 s反向運動學 inverse ( or backward) kinematics
+ w/ e; i' i: S- |9 ?( S) F反轉法 kinematic inversion
! U* o+ `0 y+ ^+ }. c7 b反正切 Arctan# z) I( y! w( m: d0 i
范成法 generating cutting
3 J- q: F: _3 o o* k8 Z9 A仿形法 form cutting
2 w2 Z" f/ n. m6 a* g0 d方案設計、概念設計 concept design, CD* |2 t. q0 {$ c" s6 b' ?
防振裝置 shockproof device: _# q9 u4 N: X
飛輪 flywheel
: E2 B7 }+ A8 j1 u飛輪矩 moment of flywheel
' N; T2 k5 A3 {+ |非標準齒輪 nonstandard gear
/ _: \0 U4 w1 [1 R" j$ e" u* o! H非接觸式密封 non-contact seal
4 Y9 X# }' C |4 @+ ?. A6 ]非周期性速度波動 aperiodic speed fluctuation9 H0 N* n( X$ f+ \# G# O3 g' _
非圓齒輪 non-circular gear
i3 B1 h- u9 `% z; T粉末合金 powder metallurgy8 b3 ^7 R1 \4 Q- ^8 @0 K9 y; V
分度線 reference line; standard pitch line
% \- _) s9 m2 S6 t% {+ j分度圓 reference circle; standard (cutting) pitch circle
5 d4 t$ X% v) {' L" y( I4 O0 W* Y/ O9 O分度圓柱導程角 lead angle at reference cylinder
) M7 h: ~ a# Z: I: O! o( o分度圓柱螺旋角 helix angle at reference cylinder
' _( E. N. k- R. X3 y( @; M分母 denominator
- A/ u& x) y( U/ L分子 numerator& K% o3 t) U# ?$ [
分度圓錐 reference cone; standard pitch cone8 s! c7 x3 w, L9 T
分析法 analytical method7 J' L+ I0 \+ _9 w
封閉差動輪系 planetary differential
+ {6 Z0 o2 e3 {4 e9 f: K復合鉸鏈 compound hinge+ l N/ \7 V& A% \( X6 P
復合式組合 compound combining: C; o2 C1 R" F( P7 w5 y& O+ y8 f
復合輪系 compound (or combined) gear train8 Z) Z6 ~0 P) A' u8 m7 G& W8 |
復合平帶 compound flat belt2 P% Q. O; ] t2 I" w
復合應力 combined stress" Y' L" e, W4 p
復式螺旋機構 Compound screw mechanism
$ `0 \4 C$ r% u0 s. V* D! R2 ]9 p" P復雜機構 complex mechanism1 W# B/ R0 M* `
桿組 Assur group 3 n4 D1 S) j+ I$ ~ p+ R
干涉 interference ) M1 y5 }1 ^* E
剛度系數 stiffness coefficient
6 r- \1 p, {$ R剛輪 rigid circular spline3 }0 I, b2 x7 c% [) G' v
鋼絲軟軸 wire soft shaft
* i3 o9 L& ~& |1 |9 n剛體導引機構 body guidance mechanism
8 T/ Q N' w- f# `8 v剛性沖擊 rigid impulse (shock)
# `6 m8 c+ W0 L* n剛性轉子 rigid rotor9 E0 b8 k- r" W5 e8 R5 D
剛性軸承 rigid bearing
& V0 M b5 i) z8 N) U7 G! m0 p剛性聯軸器 rigid coupling
1 q9 C* F0 H- R高度系列 height series
- h) F- o' Q0 t7 i. q高速帶 high speed belt2 N& F9 u; a% W$ {) W% M
高副 higher pair
) U/ t6 S, |9 w, B7 N格拉曉夫定理 Grashoff`s law. F* x" }+ @1 l* U+ v
根切 undercutting% F( H8 G" E5 n4 D6 Q4 b% W4 w9 j
公稱直徑 nominal diameter" U) H5 ?( \* m
高度系列 height series" i! d" i# h* p0 I+ H5 C
功 work! n$ V# }0 Z3 V% \
工況系數 application factor* `3 u& J- j! m. x2 x! z
工藝設計 technological design
+ l2 s. h+ q/ _, k U工作循環圖 working cycle diagram/ ]. R! J( f# F
工作機構 operation mechanism6 O. w; t5 \7 b
工作載荷 external loads
, d0 q7 d9 l% y' W! w# T8 b工作空間 working space
: u; C0 ?& ?6 c6 ?9 J; h% g! A工作應力 working stress$ p9 l/ ]0 c/ F! R# d# M- [
工作阻力 effective resistance. f1 x: q6 |: L* `
工作阻力矩 effective resistance moment; t, J2 F( D' V* u8 W' S
公法線 common normal line
& I- W9 ^0 I( N; y; y公共約束 general constraint
3 o# k$ T5 q3 Z+ T( D5 {$ ]公制齒輪 metric gears
" D2 q0 M5 S% o; j/ K' ?, A, a+ F7 V2 q功率 power
0 E3 x- ~, n% U" d6 g1 o: z$ T9 `功能分析設計 function analyses design( B! V. t$ L1 I2 V
共軛齒廓 conjugate profiles
3 W$ s. S7 q, p共軛凸輪 conjugate cam
# e d/ l3 X. e構件 link
/ c! i2 O; ~/ p- b6 |鼓風機 blower
2 {3 @( T- X- \; G) U: S固定構件 fixed link; frame& H+ ?+ i# Z1 Y+ t5 ? q/ ?
固體潤滑劑 solid lubricant
- l. V5 j" |8 S0 ]" i1 z% t7 m. a: s# E關節型操作器 jointed manipulator
& E+ f8 p5 P3 q" I4 i慣性力 inertia force5 c. Z- `" }+ p8 j! a7 H! Q/ p3 z
慣性力矩 moment of inertia ,shaking moment, i1 s3 ]+ `2 H Y1 f
慣性力平衡 balance of shaking force' J% L" ^% _4 O9 F( [/ M* F$ q
慣性力完全平衡 full balance of shaking force
. m" u+ K+ @+ m9 F" z) T4 I( i慣性力部分平衡 partial balance of shaking force2 r% e$ U/ t) H/ Q
慣性主矩 resultant moment of inertia2 X: H( d3 R7 o( Q7 K: i, `$ ^
慣性主失 resultant vector of inertia
4 g; ?+ }4 @* h. n" A. B' ^冠輪 crown gear4 \# [6 l& E9 j
廣義機構 generation mechanism
' z, d; S) G; E' u廣義坐標 generalized coordinate
& D3 m+ i! n- ^2 W* l) B! O4 `! y/ G軌跡生成 path generation
5 d0 R" b$ e" ]) x軌跡發生器 path generator5 Q' D* l+ N; V1 g' L3 L& s9 l
滾刀 hob
4 i# \: b% y7 q; ~# U3 q滾道 raceway* z* E3 }3 E7 v2 N2 M
滾動體 rolling element. T8 F: M! g8 K( q
滾動軸承 rolling bearing w U6 N8 N' v; M
滾動軸承代號 rolling bearing identification code
+ U, k& A3 x) k: u滾針 needle roller
1 K9 n( J/ L& D" C7 i5 @滾針軸承 needle roller bearing# x* h- l; q4 ^/ n2 v0 Q, h
滾子 roller
+ E$ W s: Z9 y: k4 q$ s8 N* G滾子軸承 roller bearing
/ \/ W0 L- N. L( S7 T滾子半徑 radius of roller
6 k& o2 Z" n) ]; x' y4 n滾子從動件 roller follower
( C% g( A0 V, F2 e4 P0 K+ X滾子鏈 roller chain6 l( T0 @( z+ z [% i% Y7 l5 K3 `& f
滾子鏈聯軸器 double roller chain coupling3 N! B$ E6 X' t, U
滾珠絲桿 ball screw
) B1 Y* b0 d/ V+ o/ j- ~6 r- [滾柱式單向超越離合器 roller clutch+ T) y; J# X, {) }
過度切割 undercutting: m# `$ h) k3 ^
函數發生器 function generator ; t1 B3 i' V" i, ?1 T( h% b+ W
函數生成 function generation ) J+ L% ~! X$ _2 p& B
含油軸承 oil bearing; D) A# Z( T. U
耗油量 oil consumption4 P0 x0 `" ~ R% g$ @
耗油量系數 oil consumption factor$ @. x- F9 R% U. x
赫茲公式 H. Hertz equation
3 g, u6 A8 D* t9 x4 }) Q合成彎矩 resultant bending moment
, n4 O, H& V7 d合力 resultant force
5 g' \! d7 S X3 M6 w/ C! x合力矩 resultant moment of force6 ~! G$ D$ n. [) Z: V
黑箱 black box
8 U0 \ j& |! R% J3 {橫坐標 abscissa
3 `5 _5 M) i4 S% S互換性齒輪 interchangeable gears# f. `) Y9 E. t! j7 _, \
花鍵 spline
$ ]8 v. O' b3 Z- |8 ]滑鍵、導鍵 feather key; F! u3 S" \$ q2 v: z
滑動軸承 sliding bearing
3 _& {. M% O; R% _滑動率 sliding ratio
8 \$ x5 |6 n3 o滑塊 slider2 k( u) H, S' ?3 l, N) c
環面蝸桿 toroid helicoids worm
, Z+ {: f7 b' {5 g6 _1 R, q' d環形彈簧 annular spring
# l1 \# ]0 f1 v5 R, z9 c' |! }緩沖裝置 shocks; shock-absorber
' V y( D( Y2 n& {灰鑄鐵 grey cast iron; I4 y$ D4 W8 T/ A
回程 return3 u/ M8 p3 d) w9 @) V' }- k
回轉體平衡 balance of rotors
, u7 H$ l9 a, l( }/ C# U7 `混合輪系 compound gear train& L) C3 V, j5 K/ F3 x
積分 integrate " ~4 @, e j9 B; V- u0 n
機電一體化系統設計 mechanical-electrical integration system design
6 R1 H- ?+ V2 X X6 B6 k7 D機構 mechanism
. H) f% ^/ B. Q機構分析 analysis of mechanism
9 I) X1 L: L( S* Z機構平衡 balance of mechanism
% [7 ^* Z: E* f) r- A3 W機構學 mechanism
, W0 o0 }7 b9 P1 B& S; b, N機構運動設計 kinematic design of mechanism
6 G% D. m; ?1 Z4 e3 ]1 F機構運動簡圖 kinematic sketch of mechanism
4 W$ g- q' P( t/ d& b* u機構綜合 synthesis of mechanism
( s' ~- `/ ]+ M% i- Q) h$ l機構組成 constitution of mechanism; h) z- ?2 ~8 Q4 P; B
機架 frame, fixed link
2 s! K( d0 Z' k, O3 k' G機架變換 kinematic inversion
; t% i2 M/ p/ n# i: l0 ~機器 machine
5 v3 F! u K1 |4 }$ f6 h" M機器人 robot
: a, L5 t3 E- v) J0 t/ {. ]8 H機器人操作器 manipulator
9 `; E% D. N" z( U" T機器人學 robotics
- v8 q# E+ R% B# e! z" l! O' T8 K技術過程 technique process$ P& j; s/ B$ ~" F4 ` \( H
技術經濟評價 technical and economic evaluation/ Y4 B3 s: E; Y3 S& m) C7 |
技術系統 technique system. c& A( f K; {- `, m& x, @
機械 machinery
! ]4 G% J+ t( X- T9 W9 R$ ~6 O, o機械創新設計 mechanical creation design, MCD
2 ^4 x3 e* z) X* h機械系統設計 mechanical system design, MSD
8 O( b" e" ~: @+ w% a$ P機械動力分析 dynamic analysis of machinery
3 M: t% v$ L- [0 C. M# R機械動力設計 dynamic design of machinery: C J7 F0 T/ f* c0 D2 t
機械動力學 dynamics of machinery
3 a4 J2 |, V5 ?+ p機械的現代設計 modern machine design
_$ e2 W, ]6 B8 n: y機械系統 mechanical system" I0 B$ I( j& q$ U; J. c
機械利益 mechanical advantage: H& B! D9 a& ~' \3 J
機械平衡 balance of machinery3 J7 r$ n" L3 J m& e
機械手 manipulator
2 L7 R; `7 v6 J機械設計 machine design; mechanical design
) n0 B5 j/ K9 s, |. Y& c機械特性 mechanical behavior
+ e3 ^3 P2 ~& ?8 C. ^- e機械調速 mechanical speed governors
; z9 b& C8 w( T/ l/ z機械效率 mechanical efficiency6 H$ n K' x% u- Z
機械原理 theory of machines and mechanisms; Y" |" B* y; r6 o- Y' ^7 d# O6 R( c
機械運轉不均勻系數 coefficient of speed fluctuation5 c* J/ S! a- b5 K; R# K3 ~, d
機械無級變速 mechanical stepless speed changes
6 |) J6 z1 k( W) P8 s基礎機構 fundamental mechanism6 T! r- h2 i: T# ^
基本額定壽命 basic rating life
1 u0 r4 p4 R0 ^! X基于實例設計 case-based design,CBD
7 ]" S7 _5 E9 U基圓 base circle
! c% @1 s! F V; u9 a8 E9 n基圓半徑 radius of base circle+ }5 L9 j1 j3 l
基圓齒距 base pitch: N4 ~. {( ^) {* k
基圓壓力角 pressure angle of base circle
+ V4 j* y" K6 q& D基圓柱 base cylinder
& ~& g" W4 e& j1 s基圓錐 base cone" b! D v6 R8 n9 M$ s9 a7 y
急回機構 quick-return mechanism! q& Z% H, p, c, p# q
急回特性 quick-return characteristics
8 c @% x7 S; }% u8 \急回系數 advance-to return-time ratio* U3 u1 O' S+ g! W f3 E \# b
急回運動 quick-return motion
1 A; t! M8 D; X8 ]棘輪 ratchet
+ T8 s- j R8 k棘輪機構 ratchet mechanism
; k% c7 g# }$ V棘爪 pawl+ F1 G/ B! s" S2 @9 f# \1 }# o" T. M, p% }
極限位置 extreme (or limiting) position5 o: Q; ~9 [( L/ _& Y! H9 x- y
極位夾角 crank angle between extreme (or limiting) positions
* m& l+ A. H+ I8 {. P5 q8 c計算機輔助設計 computer aided design, CAD* z; W# h U8 O0 I
計算機輔助制造 computer aided manufacturing, CAM
( V+ U' \# G7 D! r* F# a計算機集成制造系統 computer integrated manufacturing system, CIMS+ G+ k$ A# X- d/ Y# R" {* G
計算力矩 factored moment; calculation moment
! T% D% Q5 P/ P8 [3 n計算彎矩 calculated bending moment
$ O2 D9 {4 s2 [& J加權系數 weighting efficient
0 d9 m6 K$ j' ^加速度 acceleration3 J; E( A( {- n
加速度分析 acceleration analysis# j! A9 M7 ^! e' j% {
加速度曲線 acceleration diagram% S0 W% y& P7 Y1 K5 a; S( m
尖點 pointing; cusp( B) W& Y% W0 E! K3 _2 ?
尖底從動件 knife-edge follower
3 Q0 g/ R: P% E0 F: j" Z9 w間隙 backlash k3 }& v" [/ r( I; j
間歇運動機構 intermittent motion mechanism
$ ` f; m3 `' n" a7 m減速比 reduction ratio7 k. q" J, V1 U- d7 v9 d
減速齒輪、減速裝置 reduction gear
5 a/ T% p$ K. t3 s$ t減速器 speed reducer
2 Y( \' O2 u9 K' B! U; h# `, C) w減摩性 anti-friction quality& L9 A( L/ T5 u! m* Y( z+ \, S
漸開螺旋面 involute helicoid. w, z- X+ T# j# u, a1 @
漸開線 involute" T3 ~) S7 u; K" f' I
漸開線齒廓 involute profile
9 h6 B# w! A, M漸開線齒輪 involute gear
& e4 |( n* o+ E A! [/ }; Y漸開線發生線 generating line of involute
; L# }+ [ }" b% z9 l+ g/ l漸開線方程 involute equation
! C: R8 r0 M4 Y; ?, P3 J漸開線函數 involute function
( c# a+ l' G" y1 S# n& X漸開線蝸桿 involute worm4 W7 A' _' R# s* i- m6 r. `, C
漸開線壓力角 pressure angle of involute
3 A& p2 p9 ?: @2 I; j* n# E1 I. h漸開線花鍵 involute spline- B- l5 K8 ?* O d, A, \% w3 G+ s
簡諧運動 simple harmonic motion7 p: f. i s/ [ q( l
鍵 key |
發表于 2008-2-21 11:37:30
QQ好友和群
QQ空間