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楼主 |
发表于 2012-7-9 09:48
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选型 type selection- U, ?# g1 |, ?% n/ L
压力 pressure
4 d8 R5 B9 y2 @" i9 F( ^ Y/ d, A/ `压力中心 center of pressure + B0 d7 }$ R7 k' ]9 E+ P# K
压缩机 compressor: g2 D+ ]1 Q. x A/ k* ?
压应力 compressive stress" S& h+ c, ]- N* C/ R
压力角 pressure angle
( \# H# R/ Q' ~4 e5 R/ |牙嵌式联轴器 jaw (teeth) positive-contact coupling4 b. q$ W/ \1 k) p5 T6 C3 g
雅可比矩阵 Jacobi matrix
, A( {5 p8 }$ ]# c摇杆 rocker
$ a. R. C( y2 s" p液力传动 hydrodynamic drive
& g; Z3 L( a3 u8 h9 P* s2 A液力耦合器 hydraulic couplers+ p; n7 V! y# g* D- D: e2 u
液体弹簧 liquid spring& u, p4 s. V s) n2 r
液压无级变速 hydraulic stepless speed changes1 |! U, ?6 [3 f2 u9 {
液压机构 hydraulic mechanism1 ~$ M; q% D9 `) A
一般化运动链 generalized kinematic chain9 V4 G0 [& J7 @
移动从动件 reciprocating follower: \. {* l) Z3 h0 Z
移动副 prismatic pair, sliding pair7 `& O0 k( [( T0 X0 V% g
移动关节 prismatic joint4 F7 b) g% f* { w& s
移动凸轮 wedge cam2 E( K7 J: i3 M4 f
盈亏功 increment or decrement work
* {3 j6 {$ a9 k应力幅 stress amplitude
9 V4 {* i5 z, T4 y1 n7 o2 {+ b应力集中 stress concentration; G5 `8 ]8 _: |8 `
应力集中系数 factor of stress concentration; u+ U& g& q k8 `1 f- p$ [& P
应力图 stress diagram0 P$ z5 ^# n+ `$ F
应力 — 应变图 stress-strain diagram% q2 H V, F& y# P1 r
优化设计 optimal design
( f. b, b- I- {# S5 t油杯 oil bottle
2 s1 Z0 g$ l- B% }1 V2 ]油壶 oil can# a" s+ ?1 `2 C8 }
油沟密封 oily ditch seal
9 p& n! C" j; O Q! V ^6 h( v有害阻力 useless resistance/ U, O# B1 \( D5 e6 b, i
有益阻力 useful resistance
8 c" F* j/ ?5 U" T* A. V有效拉力 effective tension
4 h% X! R& F; U3 }, n1 ]有效圆周力 effective circle force" ` {; I4 Z8 n
有害阻力 detrimental resistance
6 |& J" g% Y- \" |# |" {余弦加速度运动 cosine acceleration (or simple harmonic) motion
9 x; | \3 x. t8 p$ r3 \* Y! [预紧力 preload8 [. Y" y$ O$ r9 V
原动机 primer mover
( B6 o' q+ x; u0 N7 c4 H: ]2 G8 t4 q6 ~圆带 round belt' g4 L* y( s9 t
圆带传动 round belt drive
0 O# v# \- W9 u q, P圆弧齿厚 circular thickness
! h: d+ ^* B4 F; b圆弧圆柱蜗杆 hollow flank worm
/ a0 e! a) s( |2 J) N圆角半径 fillet radius" W9 l; ], p1 \
圆盘摩擦离合器 disc friction clutch% x* V+ N+ b5 V E5 c
圆盘制动器 disc brake |
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