圓帶 round belt
( C& O" y) n- C, c# U: A圓帶傳動 round belt drive
1 u- C M4 |. b0 K6 P圓弧齒厚 circular thickness
- q& t) \* d. z( k0 ~6 `; I$ j6 r圓弧圓柱蝸桿 hollow flank worm
3 p" o4 j5 c* Y+ j圓角半徑 fillet radius
4 p u& y/ T- @' w圓盤摩擦離合器 disc friction clutch, Q( `: F) s0 s
圓盤制動器 disc brake
) }9 D4 O% \& _6 m9 v) Y6 V原動機 prime mover& c: X: A3 s4 q U1 P7 c
原始機構 original mechanism/ _- m7 n9 J- d$ E3 [3 R& _4 K
圓形齒輪 circular gear
( t, ^( I* G6 M1 e( i1 o圓柱滾子 cylindrical roller4 K$ O( o5 D& P( [9 |
圓柱滾子軸承 cylindrical roller bearing
$ a. g* E0 [4 f5 Y8 `; v圓柱副 cylindric pair( r( d% m! ^! a( J- D' B
圓柱式凸輪步進運動機構 barrel (cylindric) cam
0 i' u# R3 M! ] }& A6 g( Y圓柱螺旋拉伸彈簧 cylindroid helical-coil extension spring
- K+ W/ {7 V5 K) d% c# ~圓柱螺旋扭轉彈簧 cylindroid helical-coil torsion spring
) A- x' l5 x& Y; y% x圓柱螺旋壓縮彈簧 cylindroid helical-coil compression spring; ]" R7 x9 r+ `) q7 o
圓柱凸輪 cylindrical cam" \1 U. ~! l4 Z* F1 N1 X# S
圓柱蝸桿 cylindrical worm; E& E/ o% v& b6 l
圓柱坐標操作器 cylindrical coordinate manipulator
/ a% C; V' s5 d/ G% w2 }. C圓錐螺旋扭轉彈簧 conoid helical-coil compression spring
" n" Y) M# j& j7 @圓錐滾子 tapered roller
g$ _! ~; ?! [+ n) z圓錐滾子軸承 tapered roller bearing
8 ~/ I/ n1 \' ]! W4 F. u8 ~圓錐齒輪機構 bevel gears+ A; P/ }' e1 @! w* L: D) V
圓錐角 cone angle! T: ]. _# n4 L% G* M
原動件 driving link
! I" V& [) [2 z2 H+ `+ P2 \/ w$ u約束 constraint$ ?4 t9 X* a. D1 b8 x
約束條件 constraint condition# J. t. i. \ @& Y' M3 c
約束反力 constraining force
/ y& n, A: |( |9 W+ f w7 G躍度 jerk
. K) c5 I9 I- {; m躍度曲線 jerk diagram
" r: a4 M O; }; t- _運動倒置 kinematic inversion
& R( b; |6 r) r6 m* _運動方案設計 kinematic precept design
. R: T1 t3 [; Z7 G+ j" M' C+ v9 r# a運動分析 kinematic analysis
* j4 t; H" a J, h7 P運動副 kinematic pair% \5 n( C8 _* D7 {
運動構件 moving link. o! r o# b" X9 A! ~) c! b5 A
運動簡圖 kinematic sketch/ a# f* b8 R3 n, y
運動鏈 kinematic chain. Z5 A) f. I; A, N! Z
運動失真 undercutting
, t9 |0 L& j% g/ \- O運動設計 kinematic design
1 B7 g; R' }: I& K( N0 j& v運動周期 cycle of motion/ ?- I5 e9 W3 h
運動綜合 kinematic synthesis
6 s5 h+ y( ]$ H3 ~) j7 x運轉不均勻系數 coefficient of velocity fluctuation9 Q7 {5 Q% d2 N: w+ _ }& ^0 s
運動粘度 kenematic viscosity; k/ i: J$ c k: W- ]
載荷 load 2 l& k; ]7 _+ |6 V& y
載荷 — 變形曲線 load—deformation curve & C2 r* m5 n6 _$ [+ X3 `/ \3 E7 {' U
載荷 — 變形圖 load—deformation diagram
- }5 T. g: i A, O窄 V 帶 narrow V belt& ~* [" \" M0 S2 S/ {
氈圈密封 felt ring seal
% d* ^ M: a: A5 S展成法 generating
) `2 m8 g# _+ d* P張緊力 tension
9 A# _0 S! s" V% A k: [張緊輪 tension pulley) W" [& {" F2 g/ \5 P+ Q
振動 vibration$ ~6 c. F3 y# G3 I( W, K* Z
振動力矩 shaking couple
5 _' `$ f& E0 T6 h; E. S振動頻率 frequency of vibration, F# S# m; `+ \5 w4 m
振幅 amplitude of vibration! X0 h0 T* l6 d6 N+ q7 L' M
正切機構 tangent mechanism4 X* G' q! \) `6 x: [
正向運動學 direct (forward) kinematics
3 A, K2 b. E5 V9 j/ A正弦機構 sine generator, scotch yoke
9 A+ q; P* Z! |! j7 A織布機 loom
- c4 G3 i) k2 n+ t8 B# J. ?- b正應力、法向應力 normal stress& t, }- o) x1 V
制動器 brake* s7 c( C$ n* Z) X4 M
直齒圓柱齒輪 spur gear$ m ^8 C1 ~+ j# i
直齒錐齒輪 straight bevel gear
0 \" T0 ]4 w$ m! ^6 I* j5 {直角三角形 right triangle
) B8 X: h6 d8 z6 n7 B/ T( x直角坐標操作器 Cartesian coordinate manipulator
9 L0 j) {7 y* t( E3 P直徑系數 diametral quotient7 o7 I6 J0 C2 e+ K
直徑系列 diameter series3 {" b. t5 W6 U5 X7 I# f
直廓環(huán)面蝸桿 hindley worm
% T, H+ C3 f/ m- C! z- Z0 f直線運動 linear motion
* E* ?; `; T4 x直軸 straight shaft
: \9 u7 e/ s2 h4 W質量 mass
* N6 n( ]; a( c$ q8 |2 o/ s質心 center of mass4 X& h; c" R) X s4 w
執(zhí)行構件 executive link; working link/ e& _6 b' [" N% E4 @
質徑積 mass-radius product8 W/ L/ X) ^% X
智能化設計 intelligent design, ID
5 s6 d7 }: P7 c( x中間平面 mid-plane
3 c& p, g9 b; E' k中心距 center distance6 T' R ?. B5 s9 B" T
中心距變動 center distance change
. S) t9 {7 t: M8 Q4 i. h0 l中心輪 central gear
2 r& @" W* E4 ]& n' a; f* l中徑 mean diameter( A( X2 t9 L4 o- l) _
終止嚙合點 final contact, end of contact- N: {& b0 g" c) I9 v( @# j6 Z' k' w
周節(jié) pitch
; B2 ~/ J! v+ T: O5 P* y3 S周期性速度波動 periodic speed fluctuation
) d9 f9 [4 }/ N d Z& l周轉輪系 epicyclic gear train
6 A/ {( {) }! d l肘形機構 toggle mechanism
' |7 a7 \- [) R: d7 U2 `' n軸 shaft m/ h( m' ~$ @' [& M7 ]
軸承蓋 bearing cup
, ~4 P5 m# k& _0 x( R3 R軸承合金 bearing alloy
' i. S# c& o# V) z: T# h c軸承座 bearing block
' s6 _2 b9 _9 B5 q. R2 w軸承高度 bearing height
1 w4 x2 n6 @7 {( I軸承寬度 bearing width
8 A- z# p( i [% x# s* l3 H: t$ ]軸承內徑 bearing bore diameter- q2 p" d% [# T; @; J$ |/ q
軸承壽命 bearing life& s; L8 Z1 ]3 Z( ^' ]$ V8 s( _
軸承套圈 bearing ring! t! A4 P) I2 r8 \ v1 G' d6 B
軸承外徑 bearing outside diameter Z3 ]% K% R* q0 G- n
軸頸 journal
* @& `3 X; P! b軸瓦、軸承襯 bearing bush) s( J- c5 V1 ?, u6 b8 L& t
軸端擋圈 shaft end ring
+ L0 t0 {& s4 ^% f軸環(huán) shaft collar" q: p) e! h" L `3 o
軸肩 shaft shoulder
: P- J D' V7 Z. \) F$ b5 @軸角 shaft angle
( D! Y. `7 C3 k) D* G6 k% ~& s6 `1 _軸向 axial direction
: V3 u1 P% ~, n: L* D7 k; F6 s/ @軸向齒廓 axial tooth profile' V0 n) L M, s
軸向當量動載荷 dynamic equivalent axial load; A( X- t( i# \
軸向當量靜載荷 static equivalent axial load$ ?! X, [$ h2 O0 `6 M
軸向基本額定動載荷 basic dynamic axial load rating6 c/ [$ X1 d" W# E' s9 Z
軸向基本額定靜載荷 basic static axial load rating
6 x# T, q+ V, m6 a軸向接觸軸承 axial contact bearing
% A. x, H8 L5 n軸向平面 axial plane/ h$ C* k# ~7 T5 x1 R! F' D
軸向游隙 axial internal clearance3 _" e* ~; f( ]5 b) M
軸向載荷 axial load
# q) |! _# R" X8 x軸向載荷系數 axial load factor* g! |* `$ U# k
軸向分力 axial thrust load+ h/ n8 k0 f" i8 } f' o" u3 Y& V
主動件 driving link
' G/ v8 z. _; b* T1 g: ]主動齒輪 driving gear
% J' B- c2 u! H* j/ D主動帶輪 driving pulley
3 @) D' t' s( ?: W轉動導桿機構 whitworth mechanism
* h4 ]9 h/ [5 F: Y/ b, A轉動副 revolute (turning) pair
- N7 b, u% ?9 C7 k轉速 swiveling speed rotating speed
/ V5 z0 l, {. s: t/ z轉動關節(jié) revolute joint/ _8 I: g- W: K
轉軸 revolving shaft
* O, b) N" n) q! R+ R5 E轉子 rotor/ s8 C# @0 d# V1 ]: u
轉子平衡 balance of rotor
- Q5 ~# }+ y* V8 H0 _$ L2 B- R( b裝配條件 assembly condition
2 n$ I' M9 p4 s6 p- P錐齒輪 bevel gear' F. U" y1 x8 v
錐頂 common apex of cone0 z, ]0 l. V; B9 s+ R
錐距 cone distance9 h/ u: d$ `1 N
錐輪 bevel pulley; bevel wheel
( `. m# T; ^% o; T: K錐齒輪的當量直齒輪 equivalent spur gear of the bevel gear
7 z& Y/ y7 j+ A+ L4 H錐面包絡圓柱蝸桿 milled helicoids worm
/ @4 A; A/ T5 r( \3 }7 f' g& c準雙曲面齒輪 hypoid gear
" m7 T$ P$ S: b子程序 subroutine* P% ^! F) @) d" ^. V* M. B, w# z$ E
子機構 sub-mechanism
# [7 K! ]1 h0 T0 J9 k0 N! E6 C7 x自動化 automation
6 H9 v6 f8 r' }+ C自鎖 self-locking, f2 o- i L k% p! Y
自鎖條件 condition of self-locking
- d' j9 o: w6 p3 u/ L2 s$ {/ F自由度 degree of freedom, mobility) c! l+ a2 M3 Y: ]
總重合度 total contact ratio7 r# q1 T5 H% u* u, A ^
總反力 resultant force
( F6 t# t& N$ S- U# V8 c% N+ f總效率 combined efficiency; overall efficiency
6 m* F R2 m- N, x' @2 H: V組成原理 theory of constitution
6 e& f- i; U0 u4 e- g, h, B組合齒形 composite tooth form: C+ s k- h a$ k. O+ s8 Y6 g
組合安裝 stack mounting
' E8 f+ O$ I: y! {) R( i7 p組合機構 combined mechanism5 \ C% y* A0 o: W: B
阻抗力 resistance( ]0 W0 H9 `0 c: ^* T
最大盈虧功 maximum difference work between plus and minus work
8 G e/ P: B0 |- c% v縱向重合度 overlap contact ratio8 C5 M! T& J' w1 _) O
縱坐標 ordinate
( Z# q( A4 L c' m$ {組合機構 combined mechanism
% m3 {' _, \! M) j最少齒數 minimum teeth number
% X1 k/ _( H/ A最小向徑 minimum radius# w2 N$ Q) l& i0 M
作用力 applied force( u! ~. g4 b& R ^. a
坐標系 coordinate frame |
發(fā)表于 2008-2-21 11:45:15
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