圆带 round belt; V$ c! H; Q7 [/ b
圆带传动 round belt drive E3 B( ^, s/ A, q: P6 {: O8 L
圆弧齿厚 circular thickness* _; S( H2 M: y. X/ ]$ e6 U
圆弧圆柱蜗杆 hollow flank worm2 u: k& D8 `5 Q& B+ v
圆角半径 fillet radius
' L& ^7 d9 M8 j2 ~9 Z圆盘摩擦离合器 disc friction clutch; |# T0 x# s4 a8 \3 n
圆盘制动器 disc brake
) o: V! H( O X2 q1 ^! h S原动机 prime mover
( U9 p/ Y3 j) j' N: e5 R原始机构 original mechanism/ G# V) u' @7 V: y- V/ D
圆形齿轮 circular gear' G" F1 K- d" |7 H& M7 m) B; o
圆柱滚子 cylindrical roller
6 l8 z" P! z, _圆柱滚子轴承 cylindrical roller bearing
+ T& h* \0 a' q7 l8 ^7 M圆柱副 cylindric pair# R1 w$ \0 L" u$ e8 w0 d
圆柱式凸轮步进运动机构 barrel (cylindric) cam
, B: M7 i& \: _0 _圆柱螺旋拉伸弹簧 cylindroid helical-coil extension spring
" Z4 r& F" C' e圆柱螺旋扭转弹簧 cylindroid helical-coil torsion spring J! d& U2 J k1 X
圆柱螺旋压缩弹簧 cylindroid helical-coil compression spring9 a6 u+ @5 a% b- @
圆柱凸轮 cylindrical cam
$ d0 o. L+ {- w; s8 r2 U, [+ }+ |圆柱蜗杆 cylindrical worm
1 l3 T1 y% Q( |6 ` z圆柱坐标操作器 cylindrical coordinate manipulator8 A, R& B6 v. z! i4 E
圆锥螺旋扭转弹簧 conoid helical-coil compression spring
4 e7 I! }2 e: n# u- |圆锥滚子 tapered roller
5 h, H. f$ @/ Q1 X圆锥滚子轴承 tapered roller bearing( w7 z2 g$ g1 O. p( _* Q* Y+ V' t
圆锥齿轮机构 bevel gears
' R) B1 A" e" v6 h; Q6 p圆锥角 cone angle
3 Y6 q* F' Q9 r6 @0 o原动件 driving link2 u7 @/ T5 S% j' t
约束 constraint5 j) e! l" P9 ]8 S# C5 x$ F! L
约束条件 constraint condition
/ c& e1 W' T" k+ p2 a约束反力 constraining force
* E! ?4 w5 _' l, u: D8 V+ {$ h跃度 jerk1 L; _: Y. s- Z
跃度曲线 jerk diagram) m7 Z8 u5 E2 ]8 n5 h
运动倒置 kinematic inversion
/ c Z. e7 p1 u+ l* h, \1 ]运动方案设计 kinematic precept design: k. E8 i) o# R, K' X/ G, F/ x. ?
运动分析 kinematic analysis
; x5 Q( E+ T5 M- c/ @0 {7 n运动副 kinematic pair7 M* y) p: a* D
运动构件 moving link+ R9 R: S( k3 `0 o I, j
运动简图 kinematic sketch
4 [" a4 H; F5 K) A4 U1 I* R( R运动链 kinematic chain
" }: G; ^! F' q! m运动失真 undercutting2 E3 k1 X1 k* n
运动设计 kinematic design
& T% l a) u9 m运动周期 cycle of motion) D5 A1 R8 q. f" G; ] q0 Z2 `
运动综合 kinematic synthesis4 M! j0 y- \ j" H$ @
运转不均匀系数 coefficient of velocity fluctuation
6 |4 g2 A4 h7 s4 G( O运动粘度 kenematic viscosity: z6 i' O9 P& R: t
载荷 load
$ V" K/ _5 }: a7 |/ k, l载荷 — 变形曲线 load—deformation curve + \( D: e- A }- A( H, w* I1 A9 L! C
载荷 — 变形图 load—deformation diagram2 N, d7 A9 S! c1 [" p% H
窄 V 带 narrow V belt
4 m, j% @: Z, S2 l- {' ]9 {毡圈密封 felt ring seal
9 w. c+ G( y* P% y' f展成法 generating4 i3 B$ U4 R& l9 b" [2 z7 N
张紧力 tension
- ]4 z8 O3 F7 P/ F张紧轮 tension pulley
# u" Z/ M& q. l振动 vibration& v' m' a! R' x0 \$ x" W( ?
振动力矩 shaking couple
0 v7 ^( @0 o4 u3 g/ u+ i振动频率 frequency of vibration1 Z9 L5 v- L+ H& t/ P2 ]1 a
振幅 amplitude of vibration7 b$ ^9 Z6 O7 c/ p
正切机构 tangent mechanism% a0 S" p' g9 Y% x* O
正向运动学 direct (forward) kinematics% k1 ?8 w Z* W# P x
正弦机构 sine generator, scotch yoke; l, ?$ m7 U: Z6 [
织布机 loom
) |8 {4 @ s% {3 h! m正应力、法向应力 normal stress
/ ^; p6 a! D) d6 q- m+ U制动器 brake
2 g6 O) d% i3 B9 _& E& c, u直齿圆柱齿轮 spur gear+ ^9 X* e0 r, V* D/ W. I
直齿锥齿轮 straight bevel gear
+ V8 t h' [2 D8 Z+ t直角三角形 right triangle
1 W* N* [$ b: l/ ~2 m ?直角坐标操作器 Cartesian coordinate manipulator
1 N; i3 M- i( g& M; \6 \直径系数 diametral quotient. q/ q! j6 W" }+ C. N* f
直径系列 diameter series9 x. x* j3 r* T" ?4 W! K
直廓环面蜗杆 hindley worm& _+ v+ \; M3 P# U& x- q
直线运动 linear motion; S' B) f5 u8 e5 a$ P
直轴 straight shaft: h2 ~% @2 Q8 ^5 e
质量 mass6 L8 ^) u- R: I/ c; Z0 w
质心 center of mass
' F% T. f: x) D7 M$ {4 M' k1 [执行构件 executive link; working link
5 B7 A5 S0 t5 l* g% U" i质径积 mass-radius product8 M8 U% q N$ s! x# E- n6 p
智能化设计 intelligent design, ID, H k. v$ K: I d9 c
中间平面 mid-plane1 F4 s/ M3 a [
中心距 center distance
- _1 t0 v4 w7 l, H9 F- z0 A$ R中心距变动 center distance change- h& ]! h/ }! O7 E6 L) i7 i' y" n
中心轮 central gear
4 Q+ C; E* o, q中径 mean diameter
; P2 r0 Q, u' j终止啮合点 final contact, end of contact
- O9 |3 u) c9 K9 p* n, K* ?周节 pitch
% r1 e2 I' U! s/ j8 t周期性速度波动 periodic speed fluctuation( O4 J/ g5 ^1 L7 ^6 |0 g; X
周转轮系 epicyclic gear train
9 @2 j y; L( g8 A' t2 k肘形机构 toggle mechanism/ ~4 I1 H5 ^: a6 z- a$ ^& W
轴 shaft
% q! {; e! k+ ]/ k0 o6 R' f轴承盖 bearing cup
! f* }, v0 `. f' c* d轴承合金 bearing alloy
' y8 J" h: e$ u0 M轴承座 bearing block2 O! y3 _, p b, B; R8 [! U
轴承高度 bearing height
& P# o: F( U9 _# M z4 H' U轴承宽度 bearing width+ F/ j6 w8 ~2 `+ `- Q; S6 ^
轴承内径 bearing bore diameter7 ]2 i: m* M+ z/ [- c
轴承寿命 bearing life
_- o1 x+ s, M9 I, ?- ~4 _轴承套圈 bearing ring% ^$ g# _8 i8 F! T
轴承外径 bearing outside diameter" i' { m+ x' `, e5 L& z) q
轴颈 journal
* ?0 q& ] L) Q; p3 j8 a- X轴瓦、轴承衬 bearing bush
# I, D' B8 U( x$ E轴端挡圈 shaft end ring6 }0 f- C" y1 U/ ]( B
轴环 shaft collar
/ b' m6 u- {& R' Y( h. |轴肩 shaft shoulder
! }8 N/ p9 @) {% W轴角 shaft angle( D2 V9 t0 F$ i* u
轴向 axial direction
9 p) u. i; o9 B9 c2 x3 N轴向齿廓 axial tooth profile. j6 \4 B0 [% O
轴向当量动载荷 dynamic equivalent axial load* j4 s, h5 A3 L
轴向当量静载荷 static equivalent axial load
2 h2 O. r( n n% f- E0 ]( N: ?* ^轴向基本额定动载荷 basic dynamic axial load rating
3 d0 u b e0 H( L轴向基本额定静载荷 basic static axial load rating
8 T5 Y, Q! @% k2 q轴向接触轴承 axial contact bearing
# G& @% H# E: D轴向平面 axial plane
/ a# u" a! _9 b1 w |8 E/ K轴向游隙 axial internal clearance
3 v- O0 \/ U3 M7 H' x# T6 ^4 [轴向载荷 axial load
Z; ~) c8 Q. B0 R- z3 j轴向载荷系数 axial load factor% k& t" C5 T/ f+ r: f
轴向分力 axial thrust load
0 L/ R* w# M' d0 H+ K3 Z主动件 driving link
* f+ D* m; f9 N- E# R主动齿轮 driving gear- H' S. A$ [$ F7 a
主动带轮 driving pulley8 r$ Z3 X0 z" V) E$ k
转动导杆机构 whitworth mechanism/ X; ~0 E8 ?* x& M9 S( j
转动副 revolute (turning) pair
! {2 e3 V( { W A2 p转速 swiveling speed rotating speed
3 `( |$ \7 ^6 }2 o7 ]! I3 U8 ^转动关节 revolute joint
! L r) P- `) i& Q转轴 revolving shaft
3 q- H5 k3 t6 h4 S2 p转子 rotor
, [% O# t8 h# R7 P! W" t3 ^7 @转子平衡 balance of rotor
; s9 X. W# \ X- A! H9 j" ~装配条件 assembly condition$ w! {( J4 o3 E) L* o/ X* A
锥齿轮 bevel gear
* S, \5 Q+ R8 m/ s/ Q锥顶 common apex of cone
7 }% T) V M4 U6 s锥距 cone distance7 t- [* ]* ~& E4 Y
锥轮 bevel pulley; bevel wheel
* s c$ y# y p8 m: I" z锥齿轮的当量直齿轮 equivalent spur gear of the bevel gear7 @. A$ D% k8 ~( z% \! F$ s: a
锥面包络圆柱蜗杆 milled helicoids worm
8 `# W/ y# o0 k8 R- v4 ~准双曲面齿轮 hypoid gear: v2 t0 i% U3 X2 s0 f
子程序 subroutine
( S6 H2 x' m' u/ W! O8 Z& n子机构 sub-mechanism: \0 [5 i: k! q8 N# Z8 J' J# w
自动化 automation
3 h+ ?$ o) w2 C" R) l: N+ q/ w; _自锁 self-locking0 o- ?: s* r+ E4 R2 l ^) v2 c
自锁条件 condition of self-locking; j1 G9 Z4 k1 D ^ S( M: s; ], J0 A6 F
自由度 degree of freedom, mobility
3 A+ l- d$ Z5 X总重合度 total contact ratio' f& T E' r! G5 Z1 e. E- @
总反力 resultant force) Y# a0 K# M! A& v3 I
总效率 combined efficiency; overall efficiency
. z" D$ u/ ^- i组成原理 theory of constitution1 G6 T5 F6 v+ y$ T6 e- X
组合齿形 composite tooth form1 D; `$ k, G0 x. q$ L9 j$ x
组合安装 stack mounting
" t4 F% A5 R2 `! F0 I4 I3 _' _3 o组合机构 combined mechanism! B; W% L) r) a+ I
阻抗力 resistance8 ~& D g! U+ l2 W7 b4 o. x% ^
最大盈亏功 maximum difference work between plus and minus work0 c+ I' e% i/ Y% I0 Z; l/ \9 F
纵向重合度 overlap contact ratio7 w* \/ u( p4 z6 G# p% f1 U0 B
纵坐标 ordinate, ?/ ?$ ?) v# B: |# P
组合机构 combined mechanism# O. K3 u- F3 O/ g1 z7 _
最少齿数 minimum teeth number
5 o$ Z* |& A3 }8 L7 [4 i, l最小向径 minimum radius
' m" }( q, E4 t6 b8 V1 r2 M3 Q作用力 applied force
5 h1 x# a# k2 S) g% ]! s坐标系 coordinate frame |
发表于 2008-2-21 11:45:15
