圆带 round belt
6 U: K2 l+ x3 v5 j% y圆带传动 round belt drive
* I/ h" d7 r, `0 T5 b. t圆弧齿厚 circular thickness
& W2 V: ^& I' b7 ^圆弧圆柱蜗杆 hollow flank worm
, f2 C7 h: L' f+ t" x/ L圆角半径 fillet radius, M q/ n; B& m8 m
圆盘摩擦离合器 disc friction clutch
& L0 C% L! |# t3 Y$ K+ w2 A圆盘制动器 disc brake- U! h5 \5 ~# Q5 j
原动机 prime mover
. q9 g8 p; n8 U7 L' b o s原始机构 original mechanism) ^( j9 q& o' M8 u, P% o$ n
圆形齿轮 circular gear5 h) { J" A& A. o0 P0 F) u. _ R4 W
圆柱滚子 cylindrical roller
: N8 c0 j" r: {+ _圆柱滚子轴承 cylindrical roller bearing1 B. k6 R- X' C' U) Q2 N! k
圆柱副 cylindric pair9 Y$ b- a" D0 ]1 D: z% E
圆柱式凸轮步进运动机构 barrel (cylindric) cam
& I, v4 g) L; y ^) T圆柱螺旋拉伸弹簧 cylindroid helical-coil extension spring" a2 ]8 l0 ?9 h/ C* L# u0 M% d5 \' _
圆柱螺旋扭转弹簧 cylindroid helical-coil torsion spring+ a5 m9 P& x. o0 z4 ~
圆柱螺旋压缩弹簧 cylindroid helical-coil compression spring
: v0 ^( t; o6 I2 O3 T& C圆柱凸轮 cylindrical cam
: u* A, O8 c8 B- s* J& \0 I圆柱蜗杆 cylindrical worm/ [( M( I/ I" U8 Y# H
圆柱坐标操作器 cylindrical coordinate manipulator& K) W. W' s3 k
圆锥螺旋扭转弹簧 conoid helical-coil compression spring
5 f! F: n9 z2 B L" O' q# o/ x圆锥滚子 tapered roller% s6 a) L0 [- }9 [$ ~# u# a
圆锥滚子轴承 tapered roller bearing
# O$ b7 P- e5 ?- ?1 ~7 Q' r6 s8 i圆锥齿轮机构 bevel gears; a* ~' m! p% ^, p1 M+ U
圆锥角 cone angle
5 E1 p$ X o) q( f0 F( |7 l原动件 driving link* J! A0 z/ U0 g) Z) M' H
约束 constraint, H0 ~* |5 r/ h8 k0 _' g
约束条件 constraint condition3 d4 q7 Z- q, J9 A; O& Q
约束反力 constraining force
2 g+ f* C$ z7 l跃度 jerk
?7 a6 C# E+ {3 j m跃度曲线 jerk diagram
3 K- }& C! z- Z/ l. t4 [4 C) l运动倒置 kinematic inversion
; ^& V, y2 j9 y/ `) k' z1 m运动方案设计 kinematic precept design
: ]5 i# |# y! u运动分析 kinematic analysis
- J% d4 T( j/ K/ Z% N# D运动副 kinematic pair
9 ^0 r! r+ \$ e3 C" j运动构件 moving link( H+ A, F) s" w! V% a5 W
运动简图 kinematic sketch! P& m3 H% B! F. W
运动链 kinematic chain4 {) y) R* i1 E% G- ?! e! J
运动失真 undercutting# e0 n/ V' @9 p7 \' f( f5 \
运动设计 kinematic design2 A( |% r" J' Z$ {1 e5 c+ f
运动周期 cycle of motion1 X* i* ?1 O& e) v7 M; J
运动综合 kinematic synthesis/ q& b2 E1 k4 ~' P) U! L4 c& D
运转不均匀系数 coefficient of velocity fluctuation
+ `3 A; p( q) `2 x运动粘度 kenematic viscosity
; y e- l- ~, E2 a# X# F载荷 load 4 {7 q |" v! m$ p
载荷 — 变形曲线 load—deformation curve , I" ^: L4 k* b) H% y
载荷 — 变形图 load—deformation diagram$ X; j) D! k) I8 a6 D; M0 Y8 x% f1 C
窄 V 带 narrow V belt
6 x7 ]& J! v" v9 S0 d5 W3 e毡圈密封 felt ring seal
7 M, N( o' H4 {# N展成法 generating
. u8 ?/ V4 E) I3 f; O- F2 w9 Y张紧力 tension. R" ]* H, u* Y2 _- N7 o* M( n
张紧轮 tension pulley, ^6 e" k9 h' c8 B' o6 F
振动 vibration
4 A" N8 `5 {9 \' L) W- q! F. i振动力矩 shaking couple) S8 V* i" k6 k X2 P- _* q o
振动频率 frequency of vibration
8 p# B* H, n. K9 ]: |4 d1 p振幅 amplitude of vibration4 H1 s# L0 t0 C/ q( v
正切机构 tangent mechanism9 b0 o" a9 g) |8 R0 x
正向运动学 direct (forward) kinematics, b( J/ q! P, B/ u1 J2 L
正弦机构 sine generator, scotch yoke
; i& T6 b7 Y( V* i: N; g+ Y织布机 loom- a1 o! m$ h0 y
正应力、法向应力 normal stress+ k! S2 |7 {/ K/ D# D: W9 u
制动器 brake9 j% U- f; O# }) ^- ]
直齿圆柱齿轮 spur gear' p3 u# G' }9 C r7 I3 a0 I+ F
直齿锥齿轮 straight bevel gear
& r7 b* E! @" _直角三角形 right triangle2 X1 }. s% D* x, F3 O
直角坐标操作器 Cartesian coordinate manipulator/ h5 A$ X- I' z4 [; z, P
直径系数 diametral quotient6 _* w0 K2 y% L
直径系列 diameter series; c/ q) c2 n) w- S: q0 R% _
直廓环面蜗杆 hindley worm
' b- K; t% ]: e, U直线运动 linear motion
6 z1 C* m7 C! X' w, K直轴 straight shaft( x0 N" V8 }! F1 Z' M1 i) w
质量 mass
( k% m0 f8 o% v" L" t" i质心 center of mass
; |% n+ N# |2 P# D1 X3 ~! U. X执行构件 executive link; working link
5 j: _; A' {$ U' M) i5 s% [质径积 mass-radius product8 n5 F5 S, V% G. E' u1 A4 K
智能化设计 intelligent design, ID4 {9 Z9 C( }( f7 b+ [. \0 z+ v; @' K
中间平面 mid-plane: X8 K: f- a" ?5 [+ e: C
中心距 center distance9 u- o1 n' e5 i& W) \$ E
中心距变动 center distance change
5 I9 L" w6 _5 y: f7 q9 l3 x6 r' Q中心轮 central gear+ E% I8 z; q8 u2 z( x/ ^8 t1 s4 B
中径 mean diameter
0 _2 k3 w9 W6 v$ Q终止啮合点 final contact, end of contact
3 P% p) ? V1 x+ M% p! e周节 pitch1 K. l/ w# D5 I6 d4 B1 T
周期性速度波动 periodic speed fluctuation; I2 W. I4 I3 @& U" r2 M
周转轮系 epicyclic gear train4 z+ Q* D! A m: ]7 [: j9 G
肘形机构 toggle mechanism
4 t# s( b0 c& e _5 g1 {- ^, V8 d轴 shaft
+ ]" T( [3 }$ x/ B# T, y轴承盖 bearing cup1 J% `, l1 B+ `; f
轴承合金 bearing alloy
1 n1 Y* R4 u$ E1 u8 H2 U6 z轴承座 bearing block! e2 _" c7 m6 s1 N0 w! a
轴承高度 bearing height0 o* a) A1 j3 u `" p6 `7 k
轴承宽度 bearing width7 d2 @. }5 s$ W, Y
轴承内径 bearing bore diameter7 Y, g( H" d* Y% b, _! Y) ~
轴承寿命 bearing life2 z/ h$ v7 _& \$ H! U% f: Z5 y
轴承套圈 bearing ring* N& X# q6 {; @* t( v
轴承外径 bearing outside diameter
# v' _2 X1 V+ r" c轴颈 journal) {: A- u0 ?0 y1 \. w5 u* O' ~
轴瓦、轴承衬 bearing bush
% {2 f' ^( U) _ H/ i$ Y7 F轴端挡圈 shaft end ring
9 i8 t9 \ e, S( b' z0 _轴环 shaft collar" z9 ~! u# t5 ?6 ^. r
轴肩 shaft shoulder
6 T( G5 X' p- J$ }9 `# s" f轴角 shaft angle3 z! h6 Q2 W) C; d5 ^' I, ]
轴向 axial direction
) C1 r4 Y q7 V& ]8 ~轴向齿廓 axial tooth profile' R3 @2 w3 }) G* D/ r
轴向当量动载荷 dynamic equivalent axial load4 n8 i' R& r, w
轴向当量静载荷 static equivalent axial load
" R0 Z9 Q% ^. a) P$ f m! r轴向基本额定动载荷 basic dynamic axial load rating
! c; V- ]" X+ v: V2 N轴向基本额定静载荷 basic static axial load rating! W6 I" ]; w, t, `
轴向接触轴承 axial contact bearing- H/ P% B+ Q4 c4 d4 d5 z+ _
轴向平面 axial plane
3 Q# {# ~4 w/ r1 \! O: u轴向游隙 axial internal clearance! h3 B5 _0 ?4 W" l) i+ T
轴向载荷 axial load
8 G" Q8 S- ^8 ~: t& z+ g轴向载荷系数 axial load factor |1 S+ M/ J, m2 u5 p
轴向分力 axial thrust load3 y- B9 N1 Z* Q, S2 p
主动件 driving link1 }7 t& X; Z; k4 [% [5 |
主动齿轮 driving gear
/ E( u2 E; v% z1 ]; H; @( t主动带轮 driving pulley
3 v) ]3 e& |; ?# `转动导杆机构 whitworth mechanism
1 \- @! v9 {9 j4 y U转动副 revolute (turning) pair
4 p: J! Y5 E# D' O" u( b转速 swiveling speed rotating speed/ N9 m5 k) i; I5 x+ Z
转动关节 revolute joint
8 W( ]/ I# P* m: X' z6 A* W转轴 revolving shaft* ?% Y* t- W1 U
转子 rotor
* h; I/ f U% ~转子平衡 balance of rotor
& m! I2 O% o( l6 y* w5 d0 Z装配条件 assembly condition
5 X- H+ A# c$ g1 J5 C锥齿轮 bevel gear
% z0 g% a1 ~0 D a5 l锥顶 common apex of cone3 F' J+ D0 A4 J6 C3 A5 B4 Y
锥距 cone distance( z0 E; b) U7 i9 S' ~
锥轮 bevel pulley; bevel wheel8 V0 S, m* C. g1 s3 t* t
锥齿轮的当量直齿轮 equivalent spur gear of the bevel gear& A4 C, C5 A r5 V
锥面包络圆柱蜗杆 milled helicoids worm2 _6 B! }" E0 k! ] Y6 E0 U
准双曲面齿轮 hypoid gear/ E$ Q# C% r; K/ ], z: D2 ~
子程序 subroutine1 a- e: E/ d7 E# U, C/ e6 C# O, B
子机构 sub-mechanism
( u5 t2 E% @0 ~$ ~, j' P自动化 automation( R! A: a. Q0 u) y% m$ O0 ~& {
自锁 self-locking" U$ o- Y+ Y! {
自锁条件 condition of self-locking
' |& R" I- e1 y$ L! ?0 G# I' C* c6 E0 M自由度 degree of freedom, mobility
" M$ J2 y* @; m( Q+ w总重合度 total contact ratio2 p) `5 H2 D: s& O; o2 O1 A/ e# Z
总反力 resultant force: Q( r. u: x9 T6 x+ H+ J+ {$ O
总效率 combined efficiency; overall efficiency+ J; t6 q9 a8 t- }+ _! \1 y7 C8 e
组成原理 theory of constitution
& q) k, H% i1 Q- H% y1 O) {组合齿形 composite tooth form, L& C, q& w2 j8 n
组合安装 stack mounting
4 Y9 G( c: o- q" M) P4 M: T. S组合机构 combined mechanism! t# D* j" `) j2 E2 D
阻抗力 resistance7 x# A: T; J% }* ^6 n& u4 {
最大盈亏功 maximum difference work between plus and minus work
2 T3 |$ m1 I$ u& c O7 N( B) b( K% X1 p1 b纵向重合度 overlap contact ratio
0 t8 t. r, d- Z/ X9 R纵坐标 ordinate
5 Y% g8 y" u$ M组合机构 combined mechanism
9 g. ~- H. q! H6 X' j最少齿数 minimum teeth number
% y! F/ K+ [/ ?4 t8 e$ b- t# ~( c最小向径 minimum radius$ s* {2 `7 Z, N( V- z
作用力 applied force$ y F; m4 B( F5 e4 T) z4 G9 U
坐标系 coordinate frame |
发表于 2008-2-21 11:45:15
