圆带 round belt
& M; x0 E0 n" t6 ^圆带传动 round belt drive
- z P2 `( W( P* A; r& T2 W: c$ z圆弧齿厚 circular thickness2 h: Z/ g9 w, r: ?
圆弧圆柱蜗杆 hollow flank worm" H9 C9 z5 k% ~* w, P' }
圆角半径 fillet radius
: E6 e/ d( E# \圆盘摩擦离合器 disc friction clutch2 _5 f {7 S; G7 V# L
圆盘制动器 disc brake. V) H3 A) s0 X- d( h2 o5 _
原动机 prime mover) @% \$ X4 b: |
原始机构 original mechanism
# ^0 [, Q* x, M( C3 i3 E圆形齿轮 circular gear
; s5 M& ^3 N2 `3 \8 Q2 y圆柱滚子 cylindrical roller
; q& E0 j, ?9 V+ U3 j圆柱滚子轴承 cylindrical roller bearing- U$ e" v8 Q, b" Y
圆柱副 cylindric pair
+ \9 N q9 O* g; m) F' Q圆柱式凸轮步进运动机构 barrel (cylindric) cam
( b$ F1 T% I9 r# s. z5 ?圆柱螺旋拉伸弹簧 cylindroid helical-coil extension spring% u, f3 C7 I0 d. i" E
圆柱螺旋扭转弹簧 cylindroid helical-coil torsion spring
9 D) P: d* D& d圆柱螺旋压缩弹簧 cylindroid helical-coil compression spring
) Z. J+ F/ [' o/ h( h, }: O" @圆柱凸轮 cylindrical cam
1 Q+ W, S, o0 J5 r4 ~! ^7 M圆柱蜗杆 cylindrical worm$ X" I$ p, T2 L
圆柱坐标操作器 cylindrical coordinate manipulator0 N+ v( \8 w. W/ q& [
圆锥螺旋扭转弹簧 conoid helical-coil compression spring1 c6 _5 K, M4 c; G
圆锥滚子 tapered roller
7 U9 t E' F! V& y4 e) J圆锥滚子轴承 tapered roller bearing2 x6 C/ T }2 P2 d2 T8 S
圆锥齿轮机构 bevel gears/ m: m( f& r& ^9 Y4 P
圆锥角 cone angle
O5 e% T; ?0 N5 j& R+ r" z原动件 driving link& T6 |+ r6 Z* A* }1 t
约束 constraint
( \9 |& w' A' h0 K约束条件 constraint condition, c# t8 \" T4 [, H4 I
约束反力 constraining force
' n: H# e1 r3 V9 g# d1 j' b c跃度 jerk/ U1 M2 s: _0 r# r( H1 ~
跃度曲线 jerk diagram
4 B4 m! C! {- x. E1 m4 Y) N* H5 m% ^运动倒置 kinematic inversion1 O% M1 @; R2 R6 g/ z/ D4 Z
运动方案设计 kinematic precept design
% B1 z5 F: ?3 B6 Q8 m运动分析 kinematic analysis! Y& E" {$ n- E; ^1 C# U9 q
运动副 kinematic pair
) ], h" J. a* a9 T8 Y0 V' e运动构件 moving link8 r1 h, [, i2 h5 P
运动简图 kinematic sketch1 Q; T) G* p4 `" X9 A
运动链 kinematic chain- b; r9 ~: u$ {4 E6 k
运动失真 undercutting
; h4 }: s& c% G! Y" D4 [( T运动设计 kinematic design* |' r4 B7 n4 c% ~2 y
运动周期 cycle of motion
( @. u& P4 U, j- C8 W运动综合 kinematic synthesis+ i1 [. P6 u, |% F# d: y
运转不均匀系数 coefficient of velocity fluctuation
- V0 M+ E G" k G5 T" v运动粘度 kenematic viscosity
$ O6 {) X+ O( g# }/ A' n" X3 s. X载荷 load , K* D' P6 Y! {$ P4 ^, ^
载荷 — 变形曲线 load—deformation curve
* b' n6 w9 Q4 l/ Q* g c载荷 — 变形图 load—deformation diagram
# \5 v# R0 v; f1 g/ ^/ |6 ?; p: I. ?窄 V 带 narrow V belt7 M# b) \0 t, a! ]8 O# L: k* {
毡圈密封 felt ring seal; z9 t; r& x+ Q' `! ~) a! E- x, ^
展成法 generating( F/ Q' z" }8 R/ n
张紧力 tension
8 u4 l2 O: [7 I) A" G; X; L8 h张紧轮 tension pulley+ `7 R+ g& F D {7 |0 s* O
振动 vibration
) X& c0 J1 u( S' Z; l8 B振动力矩 shaking couple
! S$ N& ^% L! [/ @& A6 I9 b& x5 P振动频率 frequency of vibration
) I0 h7 N4 U# M* j2 Y7 y$ w* u振幅 amplitude of vibration
, I' ^. K. D+ a! h8 _# ?正切机构 tangent mechanism9 z @) o& Y' a# ^9 s8 |/ Z, A( Q
正向运动学 direct (forward) kinematics
$ L; E2 V* B4 h) P2 z正弦机构 sine generator, scotch yoke
{: q+ P6 V: I j) t织布机 loom' [9 q0 U8 ]* J, ]* d8 v
正应力、法向应力 normal stress
! [/ ?0 |! r1 [1 ~制动器 brake1 T, k" _3 w6 R: a3 _' F
直齿圆柱齿轮 spur gear
& U8 {: a. H, U5 b- i- X3 X直齿锥齿轮 straight bevel gear) G. e& F( x6 n: s: N
直角三角形 right triangle
( e, _( n0 v2 j+ Y2 d/ s, E' Q直角坐标操作器 Cartesian coordinate manipulator
. \+ U2 I4 b; J7 y+ r; H$ g1 j5 c直径系数 diametral quotient/ U" \+ d# v# ?* ]4 q
直径系列 diameter series5 R! a- Z4 P1 V% O) s
直廓环面蜗杆 hindley worm$ k* b# I1 s' E: G! G" G
直线运动 linear motion
; n2 k6 j' }+ ~6 k& S; q直轴 straight shaft
+ p9 Z+ e0 V$ {% X4 R3 p质量 mass4 M" X% a( v3 H' e
质心 center of mass
4 E. j1 W* J: e" n4 Y" G1 ]" p执行构件 executive link; working link# f' L0 E) U9 B, v. {" |
质径积 mass-radius product
4 x- h) C% B8 h' L7 n: ]智能化设计 intelligent design, ID
- J5 s1 l3 k) [2 x6 p9 L! _4 u中间平面 mid-plane
* k, W- h6 |" w/ r5 v9 i, {中心距 center distance
v! h; Z# X9 \9 f中心距变动 center distance change
2 ]/ P" W1 M7 C# @中心轮 central gear' w6 Y3 f5 `% e) n" A( a6 c
中径 mean diameter
5 h4 {' M7 e- Y; H& i终止啮合点 final contact, end of contact
% u2 _' _8 q9 W+ z- ?周节 pitch, [/ o$ i( i; k8 V- u
周期性速度波动 periodic speed fluctuation
: {' \' U, X+ u3 v/ t% o: y周转轮系 epicyclic gear train/ h) @9 q7 {" Z2 M- c; h
肘形机构 toggle mechanism; y( V% j! n/ w% p& p
轴 shaft( F' M7 H$ G# q, {
轴承盖 bearing cup
& }5 N' {7 O! L轴承合金 bearing alloy
: d9 P; O% w+ q. y0 S; r轴承座 bearing block
9 M! O# h- v* T% H# r: M2 Z轴承高度 bearing height
1 L* U3 z/ D( ?轴承宽度 bearing width5 Q L+ ~, f/ L: {7 U
轴承内径 bearing bore diameter" f% i0 G5 \, {% v3 m" Y
轴承寿命 bearing life! B" y7 v) @9 w2 O. \% u' O) w
轴承套圈 bearing ring
9 M, @2 i" j1 i8 ]' B8 W' q轴承外径 bearing outside diameter
' f) ^9 e0 t, x0 b5 T6 Y q轴颈 journal
* M+ j6 m4 ^! K4 _1 e% i轴瓦、轴承衬 bearing bush I5 V, m! a$ @
轴端挡圈 shaft end ring
- i Q7 G% B* E% l$ r8 y5 T- U6 h轴环 shaft collar
4 M3 G. M2 t5 l; L轴肩 shaft shoulder1 v- B- W- F6 u1 w, n5 f
轴角 shaft angle
+ d9 H: j9 E7 }7 ~ N! m7 u% h轴向 axial direction
9 c- Y. r e9 e( F" c轴向齿廓 axial tooth profile) j' [6 ~& S6 X* D1 k m
轴向当量动载荷 dynamic equivalent axial load
& {) |! y6 d% `7 Q, l轴向当量静载荷 static equivalent axial load. q& s% R( t0 Q% K3 J, R' Q
轴向基本额定动载荷 basic dynamic axial load rating
1 ~* }1 n# m8 m) F2 z% P& `9 p. n# z轴向基本额定静载荷 basic static axial load rating
0 O7 m* M: g1 t轴向接触轴承 axial contact bearing5 d l8 ]" Z3 }; N9 K5 A
轴向平面 axial plane
0 D, @" G, c, o* l, Q) F5 J. I轴向游隙 axial internal clearance% K) m$ \4 x" E ]4 |' f
轴向载荷 axial load
2 j* j. c5 d7 W$ ]7 T! f: e轴向载荷系数 axial load factor
$ X9 W; }% m' Q; y+ H. x& z轴向分力 axial thrust load
% V! G1 T% a5 r- C3 n" `4 v主动件 driving link- Y, @1 i# U& v2 g; W
主动齿轮 driving gear h O% f+ v! R3 g! F& I/ H
主动带轮 driving pulley: F6 e! w5 N- k. W I
转动导杆机构 whitworth mechanism! G5 i5 {' s H2 a& t
转动副 revolute (turning) pair# A. |/ o- p8 x- ?1 i$ J1 a/ ?
转速 swiveling speed rotating speed
" ~; O' u O1 S$ t/ D转动关节 revolute joint+ j) m( ]/ U$ Z4 C0 \
转轴 revolving shaft
* F8 u; j1 Z, k4 a0 Y转子 rotor. p# s# I0 w5 C" f8 \' g4 b4 B1 L4 x7 z
转子平衡 balance of rotor7 b: M. D# Q9 L" K
装配条件 assembly condition3 X9 E9 @, D6 e# y7 d/ `
锥齿轮 bevel gear
5 q- Z u! y; y- B1 W锥顶 common apex of cone
7 J0 ? y8 `+ I8 V! s6 d) [: P锥距 cone distance$ `% {! b) g9 ^ b; h" }, f
锥轮 bevel pulley; bevel wheel
7 \4 K# k# N' z. h6 h锥齿轮的当量直齿轮 equivalent spur gear of the bevel gear6 h# c! K, {" o- ~% d1 B
锥面包络圆柱蜗杆 milled helicoids worm+ O ~$ {1 D) H: P0 S9 S( t, N
准双曲面齿轮 hypoid gear
& O3 L! A; Z! [. P子程序 subroutine1 l$ y3 ~' W3 B7 F3 {
子机构 sub-mechanism$ D+ j' n( a: I' w9 s- V
自动化 automation
) Z) ^: N9 u, [9 M: C; v自锁 self-locking
2 J- _/ \6 G. z( a" F4 C% M- B自锁条件 condition of self-locking: {. e3 |" _/ o
自由度 degree of freedom, mobility
8 u% ^( r9 B6 [& j; U总重合度 total contact ratio L4 z1 e$ ~% Y8 Q+ O
总反力 resultant force# G* e1 Z) m# n
总效率 combined efficiency; overall efficiency
) Y& l7 }% [% `& A* d' U' [. K) a组成原理 theory of constitution
1 j* k% m: I. h L* o9 E; J组合齿形 composite tooth form4 d. _. r7 F" |$ a
组合安装 stack mounting
" ]# @7 O% }# k0 w( t6 w组合机构 combined mechanism4 k6 I% @5 A u2 d N0 r
阻抗力 resistance
& y2 m0 {( g: Y- D5 p* j: F0 E最大盈亏功 maximum difference work between plus and minus work( R* c5 ^/ \/ p; v" Q4 c5 q
纵向重合度 overlap contact ratio
5 G0 H: I; n& m+ Q9 `: _纵坐标 ordinate
7 L6 M+ T* O0 `& n# e: ?+ R6 C& m组合机构 combined mechanism
, i+ Y8 j5 Q- W5 `" H最少齿数 minimum teeth number$ A* E5 G/ v% c7 a$ D, \7 u+ [: n
最小向径 minimum radius
* L7 F7 H6 X4 [1 P, L- N9 b作用力 applied force8 _" p) O! C2 b: u
坐标系 coordinate frame |
发表于 2008-2-21 11:45:15
