圆带 round belt
; _) N U7 C+ [. Y8 G圆带传动 round belt drive! @& A) u# I7 N6 e, f% S6 [
圆弧齿厚 circular thickness
8 _7 N, A* C' K5 o圆弧圆柱蜗杆 hollow flank worm
/ q9 Y$ O3 x- I. a3 D" w; ]: ~1 K圆角半径 fillet radius3 z: Y; t+ n( m5 i- Y d2 |- H
圆盘摩擦离合器 disc friction clutch& h+ T( c S; k6 y1 Q1 h
圆盘制动器 disc brake
8 K m$ O' J, |( v原动机 prime mover
4 d9 b0 Y" U$ X原始机构 original mechanism9 w2 s; M8 P. l, ~0 t7 E4 U) c3 e
圆形齿轮 circular gear: x R1 f: x% y3 c9 c! V/ j
圆柱滚子 cylindrical roller7 a2 j5 {- [0 L
圆柱滚子轴承 cylindrical roller bearing
4 o" p* e* u- e+ J圆柱副 cylindric pair1 q$ {& ~' ^' x
圆柱式凸轮步进运动机构 barrel (cylindric) cam
E. Y1 s& S8 O' Y$ Y圆柱螺旋拉伸弹簧 cylindroid helical-coil extension spring
: C) R; T6 ]# i( H! ^, u1 z5 t圆柱螺旋扭转弹簧 cylindroid helical-coil torsion spring, V& Q5 A* z! r7 j
圆柱螺旋压缩弹簧 cylindroid helical-coil compression spring3 M1 B4 x1 C0 z4 L& J& L/ I$ B
圆柱凸轮 cylindrical cam
, w. S4 D5 A; Z7 ~4 [圆柱蜗杆 cylindrical worm
! I0 V% E/ p5 I圆柱坐标操作器 cylindrical coordinate manipulator
' F L) J8 _1 C' k) Z圆锥螺旋扭转弹簧 conoid helical-coil compression spring
1 z9 T2 x! k- f) l圆锥滚子 tapered roller
. e; s$ P0 X5 q% _! _+ j* Y圆锥滚子轴承 tapered roller bearing$ e0 }# X) u8 D$ F7 K
圆锥齿轮机构 bevel gears
; H5 X# `5 v2 ~' C圆锥角 cone angle
5 j' \! s3 V7 V$ t( s2 k' q4 N原动件 driving link
& y8 a5 u' E( Z) r f2 G% I约束 constraint
4 w$ V" H' Q6 O) }$ f( u9 o9 a# e约束条件 constraint condition% x* S( F% O {) ~; i4 W
约束反力 constraining force
3 ~+ L4 `) A3 ?7 e# D7 L$ L# y: a5 Y跃度 jerk
6 P, i Z: ], {7 P7 }! m+ g跃度曲线 jerk diagram' z R' w+ }3 U: c% P) I( c1 w
运动倒置 kinematic inversion, D5 { A4 y# H
运动方案设计 kinematic precept design! Q, u' I! }7 }1 x/ M M
运动分析 kinematic analysis- V0 l+ a7 l- w0 M
运动副 kinematic pair* y2 }/ ?- s$ X" @# e0 y& I
运动构件 moving link
9 ~* \- T0 J/ C运动简图 kinematic sketch
) L" X% m$ q& g& A7 S5 z运动链 kinematic chain M# `) J& E6 I+ j: @) G
运动失真 undercutting
( c' |) L3 Y. s& m; [( S$ u5 l运动设计 kinematic design, u0 p2 h w* |8 F/ I9 Y4 u
运动周期 cycle of motion
7 Y4 X# D( [% R: a: i# }运动综合 kinematic synthesis9 X/ A }4 c2 G( }
运转不均匀系数 coefficient of velocity fluctuation7 H; n: Z1 e, | ^2 Q
运动粘度 kenematic viscosity
5 y+ Q- Q: c; U9 {3 v1 z: U载荷 load 4 x: u6 ~7 S d3 o0 I1 y! b
载荷 — 变形曲线 load—deformation curve # D0 w7 {: V/ a1 ]% y5 y
载荷 — 变形图 load—deformation diagram
7 y7 j' w$ _2 y$ {窄 V 带 narrow V belt- R7 A. b: U8 [+ ]7 R$ n
毡圈密封 felt ring seal6 b- Q$ F/ |7 `! g; u3 g) o
展成法 generating
/ D& V( S8 g% N* ^8 X& m3 U张紧力 tension
% [( u$ V2 R8 S0 [7 g张紧轮 tension pulley3 }8 C& ~$ W9 S
振动 vibration2 ]6 ~/ i; R8 H2 K% Y
振动力矩 shaking couple
. c9 }2 S) y. @8 B振动频率 frequency of vibration
3 ?/ n1 F% M3 {3 |振幅 amplitude of vibration3 S* ]3 u1 A: U7 y
正切机构 tangent mechanism
8 p8 }- H: [8 o! i6 z: y正向运动学 direct (forward) kinematics
, O. {: ~2 e5 b8 [- J正弦机构 sine generator, scotch yoke
, X* T/ }" n2 Q$ q8 G织布机 loom
, O* v' H9 m! X6 j/ Q8 g正应力、法向应力 normal stress
- Z/ O, I, f$ \制动器 brake- m# G: ~( |; s4 U% S- o8 Y8 u4 H
直齿圆柱齿轮 spur gear% s; }$ {5 f0 R. V- ]2 W( t
直齿锥齿轮 straight bevel gear
# Q! Q& J) Q. a! U, u, O0 S直角三角形 right triangle% \3 h& s3 ?. g! w
直角坐标操作器 Cartesian coordinate manipulator4 _: |" y/ Z8 B& ^; O( [5 Z9 F& ^
直径系数 diametral quotient" n O o l7 T+ N( p; ]
直径系列 diameter series
: p! B7 ~% M, g, T+ }! _, x/ a2 c) h直廓环面蜗杆 hindley worm
, g2 y' i) b# \4 ?$ x. r( p9 E! Z直线运动 linear motion5 Q$ o( f Q: r* @
直轴 straight shaft
$ [6 `! e! K5 i/ | e. b质量 mass
" b2 t( I& _3 S7 l" j6 k; o质心 center of mass* n( J# S! ^) k6 Z i9 Y7 J
执行构件 executive link; working link
' W( w+ u6 Y4 \% @! B% l质径积 mass-radius product. y+ \2 d$ G/ F& H" t8 e$ Z
智能化设计 intelligent design, ID8 c ^6 I1 U2 J4 z8 W: D" }1 s
中间平面 mid-plane! @5 a9 _5 f3 P( O0 L! o; s
中心距 center distance% z! _) b0 v; ?) A
中心距变动 center distance change
$ S% \' `4 L4 y4 r中心轮 central gear
( o% k0 m7 f2 @0 {中径 mean diameter
/ t" Y1 C* ]# K终止啮合点 final contact, end of contact
! X: c1 T% K6 |% J0 [周节 pitch- ~6 n% b2 Q9 } @: X+ U+ A2 r0 C
周期性速度波动 periodic speed fluctuation
, O5 O0 x- X# T7 P2 l周转轮系 epicyclic gear train
- S) y1 z" A ^( X+ m& T肘形机构 toggle mechanism) f' G0 |0 |* D: Y; |
轴 shaft
( m1 O/ g5 h& N2 y7 W% b轴承盖 bearing cup
5 P* m3 f) c& ?' i& e3 L9 @% Z% D轴承合金 bearing alloy
% V% o6 J8 X, Z, H" c! E" H轴承座 bearing block
' V- g9 D( ?# S& H; l轴承高度 bearing height2 K) T9 j3 d) F8 Q7 K2 R0 H
轴承宽度 bearing width
( t% _8 M; f+ a+ b8 }+ J0 x! J轴承内径 bearing bore diameter
! Q+ z* Z' h" P) C轴承寿命 bearing life1 \ r% r' Z1 A% d
轴承套圈 bearing ring
6 u7 r/ h8 |" }轴承外径 bearing outside diameter( J0 p4 m9 N; b: d6 s# X
轴颈 journal! Q, W1 b' Y1 M
轴瓦、轴承衬 bearing bush/ W- t6 R! \' z5 _& c, a9 b
轴端挡圈 shaft end ring
8 \9 ~4 h$ g. R' ~$ {$ B轴环 shaft collar, \. A" \" b% g# y8 i2 n. s* C7 b
轴肩 shaft shoulder
7 R1 i" ^% S$ x) R) U1 a轴角 shaft angle
6 k z: R" Z/ |轴向 axial direction
+ h- h8 |7 w3 e8 @) Z. O" }轴向齿廓 axial tooth profile
$ `! O" T/ s5 | k3 l) \; r轴向当量动载荷 dynamic equivalent axial load
% |( R- ]# c8 q( g: N3 m轴向当量静载荷 static equivalent axial load
2 b8 }5 k- J( O6 J4 ~轴向基本额定动载荷 basic dynamic axial load rating) w. c, {, K6 o8 _) v' }) {
轴向基本额定静载荷 basic static axial load rating
: d) z9 A* M# Z轴向接触轴承 axial contact bearing: G$ D% Q# Y5 u7 p* Z& z
轴向平面 axial plane$ C4 y/ a" |9 C4 ^
轴向游隙 axial internal clearance5 B1 h' C J: ^" j6 L
轴向载荷 axial load7 [8 V, M/ e' ]6 d, ^( E7 o
轴向载荷系数 axial load factor
7 u" W$ r' E0 S( A: u% J' Q轴向分力 axial thrust load( d6 O; y- [2 d% V5 o' b
主动件 driving link6 {9 y7 e2 m$ [
主动齿轮 driving gear/ S' j- }5 L) C/ S
主动带轮 driving pulley9 I1 ^9 i- f& t+ v( _% w
转动导杆机构 whitworth mechanism
' o5 {& t7 e* G; w. U* ?$ E转动副 revolute (turning) pair/ F2 ^1 p7 b9 T
转速 swiveling speed rotating speed3 q/ q8 x/ @, c# w- l1 b, l
转动关节 revolute joint' Z7 z# F0 Y/ A) B7 W
转轴 revolving shaft) n+ \8 B. M$ R- m6 T. l X3 e
转子 rotor! W. Y6 B: G3 U/ B4 Y
转子平衡 balance of rotor! ]0 S% w8 A+ q: H& F6 R8 Z
装配条件 assembly condition. _" I# h O: _
锥齿轮 bevel gear
1 h6 c; w( P% `' i锥顶 common apex of cone, c" Z/ s* e% G0 B7 _% {& v; S* _
锥距 cone distance; f9 t# h8 h* G/ C
锥轮 bevel pulley; bevel wheel7 Y$ p8 [$ E. }* @& E- C7 ]
锥齿轮的当量直齿轮 equivalent spur gear of the bevel gear9 t: c- o8 c3 s7 ?
锥面包络圆柱蜗杆 milled helicoids worm( T# \" j; N3 k% b+ D3 R# g
准双曲面齿轮 hypoid gear9 m! M+ O$ V8 Z* Z. z
子程序 subroutine
% G) f4 L7 }3 y3 X4 z7 d子机构 sub-mechanism
8 [+ L4 O0 K4 T+ q自动化 automation* i' t5 j4 b6 y) F6 F1 M2 F8 d
自锁 self-locking# N2 Y% ~) ?: r* |5 F
自锁条件 condition of self-locking
; `9 c. k- A. I$ W X' k自由度 degree of freedom, mobility5 i( z4 F! r6 l9 f
总重合度 total contact ratio
% ~$ @: I0 t! S7 {总反力 resultant force
& [. \8 Z7 {5 ]/ Z" j. i总效率 combined efficiency; overall efficiency( ?( I5 J5 R" B# M/ M. f
组成原理 theory of constitution# I/ ~. ~! C" i8 Z( S! T N- u/ s) u# ?
组合齿形 composite tooth form$ ]; l, ]! P. \- G7 O6 F8 @2 b
组合安装 stack mounting
7 [+ b( C' }+ G3 L* J+ g2 _5 `% o组合机构 combined mechanism
0 h, i6 t4 T0 ^ {阻抗力 resistance
9 f) M8 c, r! g最大盈亏功 maximum difference work between plus and minus work
4 }1 P- {: B4 F; g- I纵向重合度 overlap contact ratio
3 H( ]8 z4 V; D纵坐标 ordinate
3 q" s. I; z2 l1 r5 t; T组合机构 combined mechanism
+ h5 v5 r4 E5 \0 I5 z最少齿数 minimum teeth number, F. j6 a# W" u
最小向径 minimum radius
/ _; z; c& p& r1 o* b作用力 applied force
* J. u) O9 b% r: r# D坐标系 coordinate frame |
发表于 2008-2-21 11:45:15
