曲柄滑块机构 slider-crank (or crank-slider) mechanism
# C* j- B) f7 \% G, z曲柄摇杆机构 crank-rocker mechanism3 g7 J/ `0 p* ^' W1 U2 f6 _
曲齿锥齿轮 spiral bevel gear8 ^- x4 J% t/ O: ?& `5 K1 T+ j8 ]
曲率 curvature, s+ B4 E9 |8 d8 ?3 [9 ~
曲率半径 radius of curvature
8 D& p7 g, r( I曲面从动件 curved-shoe follower) @% E: ] c- F) f! E) @) J1 _/ _
曲线拼接 curve matching* O% ^( E& Q; f9 S& d$ Q) C) A( T
曲线运动 curvilinear motion
3 I! K$ A# ? M4 [; r* o3 [曲轴 crank shaft
+ n0 w9 ]9 s2 t) |, {+ I& i9 J驱动力 driving force
( O3 \, L& ~& p* S* N8 X: C驱动力矩 driving moment (torque)
( m8 F4 P @: R# R( a全齿高 whole depth
1 F- E( ?( h- N) V权重集 weight sets! Q. h/ `9 D& h; p
球 ball
! o* A( S, V3 k球面滚子 convex roller
3 Q0 p. f: O$ c9 f球轴承 ball bearing
k) c0 M. z$ K9 W- `+ W% x球面副 spheric pair5 r+ V4 r, P N* t, N
球面渐开线 spherical involute+ ^( J8 o. Q0 c
球面运动 spherical motion4 l3 [. |) r$ E2 r- Q3 w0 K
球销副 sphere-pin pair. F2 m6 I0 |7 @
球坐标操作器 polar coordinate manipulator- Q5 s) r, w7 ~+ A! K
燃点 spontaneous ignition
& H( O7 |) S! @" ]8 R热平衡 heat balance; thermal equilibrium ) ^- [# ], b6 ^% ?
人字齿轮 herringbone gear
& L' a$ V$ M2 M2 R冗余自由度 redundant degree of freedom; p9 I c5 T9 Y; O
柔轮 flexspline
( Q5 ]6 W1 Q: R柔性冲击 flexible impulse; soft shock
I" z& W _6 w# Q! o% B2 s; V柔性制造系统 flexible manufacturing system; FMS3 [) a/ ?2 e7 Z! W2 D- @1 u/ _& k
柔性自动化 flexible automation, ?- W" Y1 g# F" {5 O
润滑油膜 lubricant film
: v+ j K* p+ c- y. i% v% s( o0 `润滑装置 lubrication device
6 n/ d/ N" h0 }4 h, M6 r润滑 lubrication
9 ~; d, f; {5 _% |8 z6 A润滑剂 lubricant
H+ u+ [( e9 H# p三角形花键 serration spline
. L5 B- C# j: a ~- o6 V- x三角形螺纹 V thread screw 7 g6 ^ B: x+ H# U6 G6 B
三维凸轮 three-dimensional cam5 O+ O1 ^5 T3 r
三心定理 Kennedy`s theorem
- @1 Z; y# U ]% }砂轮越程槽 grinding wheel groove
0 [. o4 O! U5 N9 }0 `- i5 [砂漏 hour-glass
0 q: M% n: e7 d9 {* i5 o少齿差行星传动 planetary drive with small teeth difference
4 r- b; c; Z- ^设计方法学 design methodology, ~7 V+ i( m1 U+ a% m# C
设计变量 design variable) W, a( L# w* G' V) N
设计约束 design constraints
6 g/ q) j( X. T# P, [4 P7 ^深沟球轴承 deep groove ball bearing
/ W4 A I; x3 L6 K生产阻力 productive resistance
; E; |. J0 u+ ^5 L& I' n升程 rise
7 e' Z" V+ Q( N4 I K* t j3 E升距 lift
' i: O4 }+ i( r- ?% _6 p实际廓线 cam profile
. B* e+ |9 m# y& j* O7 d十字滑块联轴器 double slider coupling; Oldham‘s coupling2 Z$ D& `9 U8 w; {7 |: j8 e4 z
矢量 vector
. s4 q& ^% h4 ^" e) E( \7 c2 z& S$ D8 A输出功 output work
% L; q1 e& j; S ]. M9 f5 x* L& l输出构件 output link( K" @( B3 Q: `: i; c: Z/ M9 l
输出机构 output mechanism
' V( w- G2 ~( R c: G, Y输出力矩 output torque* O% o; h4 V3 B) G3 s3 F
输出轴 output shaft0 c# {8 I# u$ E9 C, F2 s* W% q0 j
输入构件 input link
8 S$ y2 _6 a8 t8 h数学模型 mathematic model
M8 S) O5 j4 E; k k实际啮合线 actual line of action
6 E5 u$ ]( I9 b, W1 r0 r双滑块机构 double-slider mechanism, ellipsograph V0 v& G3 [0 w1 K! P8 \
双曲柄机构 double crank mechanism" S: W8 J0 s1 ?4 [, D8 e( a, z0 G+ q8 t
双曲面齿轮 hyperboloid gear
/ M; k% i' [0 u- r双头螺柱 studs
7 ~2 U# {; `0 m% `: q1 p+ j: z0 S. B双万向联轴节 constant-velocity (or double) universal joint/ l4 r1 V0 \" f9 m3 D8 _. ~
双摇杆机构 double rocker mechanism
- E/ c9 ~+ K8 n, e9 H/ Y# D( X5 {双转块机构 Oldham coupling
% Q3 e2 S3 |/ c$ ^; v5 L双列轴承 double row bearing
; | A& k* }# h5 \1 q双向推力轴承 double-direction thrust bearing
/ g! y0 H/ l! _+ e' K9 W3 n9 p; l' u松边 slack-side: j; L6 K) k- w* n3 x* [' D7 b! p
顺时针 clockwise3 K1 Z/ {" A+ ?2 H
瞬心 instantaneous center
" T* O0 z1 z. S4 H* V: S死点 dead point% _6 i( i+ M: R" h
四杆机构 four-bar linkage3 J1 G2 t. h" E( @
速度 velocity' _( q* }; G% r+ i9 C: f( ?
速度不均匀 ( 波动 ) 系数 coefficient of speed fluctuation4 U8 \8 m; G2 y% x' C8 i4 L
速度波动 speed fluctuation
7 B1 p; ~; R7 k9 W. A: ~速度曲线 velocity diagram' g- n q; f) p& L1 Z. T; H! Q
速度瞬心 instantaneous center of velocity
7 ~! H2 C0 W6 C8 T: [9 T: n塔轮 step pulley / ~3 M2 r/ Q4 y7 e& m( U# ~
踏板 pedal
! W% m; C3 I ~* Y. c$ x( i9 ^台钳、虎钳 vice
7 n& W9 v% i5 o9 V太阳轮 sun gear! [1 ^; ^0 n2 u% ^$ m# R6 t
弹性滑动 elasticity sliding motion
) s" j4 C+ I7 R: M/ `( X弹性联轴器 elastic coupling flexible coupling) o% `+ C$ X6 p" s B0 ?% \6 T- n
弹性套柱销联轴器 rubber-cushioned sleeve bearing coupling
+ X* C, l( b/ ?- f套筒 sleeve7 \- U/ z* C P# e- z
梯形螺纹 acme thread form* a; Y7 S, \) ~. N
特殊运动链 special kinematic chain$ A; c. G5 x7 y$ [, D* c$ G
特性 characteristics4 {5 J) E- Z8 J- q0 ?" F! n
替代机构 equivalent mechanism
- `5 S8 V0 w7 u( T6 T1 Y& T调节 modulation, regulation4 b( `. B5 y. _% U1 i H6 t4 X
调心滚子轴承 self-aligning roller bearing
- f# z! _) t# @ u调心球轴承 self-aligning ball bearing
" `: d; D: a. ]" ~( }调心轴承 self-aligning bearing/ H) M4 v& t: x H* [1 ~
调速 speed governing3 L3 [8 W' I9 M+ a$ b" `( b% f% v5 |9 C
调速电动机 adjustable speed motors6 X6 S1 F' p( t0 i, v6 D3 G
调速系统 speed control system- x0 {0 y# q& w2 A: T! }
调压调速 variable voltage control
M/ ~4 F) C4 H% I1 e调速器 regulator, governor& i+ e; o5 v( E0 e( v3 s/ ]8 B B
铁磁流体密封 ferrofluid seal* D/ g$ f% {2 V! |$ I
停车阶段 stopping phase
. f+ k% Z7 }, W; a停歇 dwell" u7 V% U, b1 m* o1 s; [
同步带 synchronous belt4 p `5 C: M9 ]/ y. T
同步带传动 synchronous belt drive
, M) [8 d6 X) V( ]3 ^, }2 O凸的，凸面体 convex5 Y5 h) X( i% i/ o
凸轮 cam
( D |/ ? A, n4 P3 V# A7 F3 C凸轮倒置机构 inverse cam mechanism- c; {2 X, w3 A+ K, m
凸轮机构 cam , cam mechanism% R, g; H2 O: s9 v
凸轮廓线 cam profile
+ M" z5 Q" A8 j% O凸轮廓线绘制 layout of cam profile @! p( e; C% k% p$ U6 ^
凸轮理论廓线 pitch curve4 \6 d- p0 y' y6 \
凸缘联轴器 flange coupling4 L4 O( T5 X7 a( X) i) ]/ A8 l
图册、图谱 atlas" n) o# k2 T2 [& D/ m; r
图解法 graphical method8 d/ V' B8 _& u* k: B
推程 rise* G$ T. L6 _6 O4 O
推力球轴承 thrust ball bearing
( {. X% V9 j/ L( j推力轴承 thrust bearing) v8 U7 n, g. ?& {7 L0 z# b
退刀槽 tool withdrawal groove
4 C: M8 _/ X! Z退火 anneal; r% Q+ j2 F& e7 ? y4 c( _/ A
陀螺仪 gyroscope+ C/ l. u( |% a' G0 K4 D( j
V 带 V belt9 ~/ I" W; S8 H, g
外力 external force
, B+ v1 k+ Y( t+ n& g C/ W0 E: `外圈 outer ring
( U3 \, {+ `$ Q5 g' A外形尺寸 boundary dimension. K6 x* q+ @/ c4 x/ _- Q
万向联轴器 Hooks coupling universal coupling7 b! Y+ E8 B. C
外齿轮 external gear
2 L8 R$ t, I3 Q v0 f" E弯曲应力 beading stress
, h. x. L5 S# q+ f# X& ~弯矩 bending moment
; ?5 s! Y7 X A9 P( n# ~8 n/ z4 R腕部 wrist9 E3 M( _8 |2 C# \# }
往复移动 reciprocating motion
+ n( Q# D( m$ c+ V4 o' }$ N6 Q往复式密封 reciprocating seal
: H, P; B, }. ]% [ ^2 t1 v0 V- m网上设计 on-net design, OND
s) y, N* Y# a$ s微动螺旋机构 differential screw mechanism
7 K4 e+ l6 ^" P Q9 x& K- Q7 R位移 displacement5 X6 d, L) u2 y4 k2 I# }
位移曲线 displacement diagram
9 N+ ?" g. [/ w( p9 F* j位姿 pose , position and orientation
* o6 ~# P& a6 A) h. m8 M0 D稳定运转阶段 steady motion period
9 K+ s2 b! f7 K0 W稳健设计 robust design, ?, d/ H/ z2 G% r, w
蜗杆 worm
! g0 j I6 w m蜗杆传动机构 worm gearing
+ H' q4 f5 [ t/ ]+ C蜗杆头数 number of threads
: y2 v( j( K2 R W- W6 s2 c! u- ]蜗杆直径系数 diametral quotient
5 I# B1 i* q L# c5 ^& Q' E蜗杆蜗轮机构 worm and worm gear
6 l; B7 q2 M% P8 c蜗杆形凸轮步进机构 worm cam interval mechanism i% Q, k4 Y3 y5 b3 G& }4 k
蜗杆旋向 hands of worm" d o; f0 t L' Z
蜗轮 worm gear6 y+ V! s- P9 l* u! g/ C/ y" }
涡圈形盘簧 power spring% T) }+ S2 u! a
无级变速装置 stepless speed changes devices+ ?$ e) v+ O4 D" C% m0 ~1 j& m# L
无穷大 infinite2 t7 r# @5 @' v& |3 l. [$ P- V- O
系杆 crank arm, planet carrier
: F; q2 P) D( z) E现场平衡 field balancing
8 e5 f/ h) y2 R/ e向心轴承 radial bearing
. s' h1 |. ^7 Z* n( y. J: y0 X向心力 centrifugal force* _ N! F' U% Q6 O1 l: L! Q. W
相对速度 relative velocity9 r/ r& A) L% N
相对运动 relative motion
% Z1 s! G9 l7 d& t6 A0 R相对间隙 relative gap
5 V% Q+ v8 J& { g* H7 x4 [$ T象限 quadrant! I/ w' i0 J& \
橡皮泥 plasticine T9 O# S8 S e& ~ B8 p
细牙螺纹 fine threads
& m. Z& l( t, o0 ~2 b' }/ A8 k销 pin
" @: l6 ?2 C. N4 e) P7 A9 T; W/ ~5 G消耗 consumption; u. w* M( b% v( A4 u6 f: ^, I& e
小齿轮 pinion
, `6 u: Z, N0 d( H& l$ t小径 minor diameter
& O/ M" s: s8 z9 N- f橡胶弹簧 balata spring$ ]" R% B- H D" l
修正梯形加速度运动规律 modified trapezoidal acceleration motion* K7 @5 e' o9 Q" y- M6 S1 f
修正正弦加速度运动规律 modified sine acceleration motion
1 E" Q3 f! H! ?: R斜齿圆柱齿轮 helical gear
# R! g$ P3 l+ h9 p/ n斜键、钩头楔键 taper key# c! ^8 g- \9 j) ]# f. r) a7 Y
泄漏 leakage
" N# n. @# R, P3 \/ W谐波齿轮 harmonic gear9 A( @6 m. \; L; Q
谐波传动 harmonic driving
' O6 J2 Y! I# K/ H7 B+ x谐波发生器 harmonic generator
% m9 j7 O+ t2 c+ Q斜齿轮的当量直齿轮 equivalent spur gear of the helical gear/ }/ X7 e2 f- O, h+ b( b2 Y
心轴 spindle" I* M1 s5 @5 i* S
行程速度变化系数 coefficient of travel speed variation
2 @6 H+ [/ l; T* G- _& D9 Q行程速比系数 advance-to return-time ratio/ t6 {" w# m* W6 ]; J+ ~
行星齿轮装置 planetary transmission8 ~0 p$ d" P; r9 Z5 V
行星轮 planet gear8 B) U* G7 k5 I. O3 E
行星轮变速装置 planetary speed changing devices
+ ?5 U" ~6 M. m. w( g7 b2 z行星轮系 planetary gear train; e9 n' F: t2 J* K
形封闭凸轮机构 positive-drive (or form-closed) cam mechanism/ i* J5 r& ^7 L8 y: U7 g
虚拟现实 virtual reality
7 W; o0 ]+ l: I# a$ c虚拟现实技术 virtual reality technology, VRT+ [1 b" v6 Y& e- x/ B/ a8 z/ [. ]
虚拟现实设计 virtual reality design, VRD
4 O0 d% [# W; g- y* u虚约束 redundant (or passive) constraint
4 I' [$ D, \2 z/ c! _许用不平衡量 allowable amount of unbalance
% l: A, W4 Q- V" m许用压力角 allowable pressure angle
" i. }# c, ? v( T% E* X' q许用应力 allowable stress; permissible stress
. ?3 q+ _' i6 K/ X悬臂结构 cantilever structure" z! Q5 s7 p9 R1 R! E- S
悬臂梁 cantilever beam1 J. J% L3 s( c$ b
循环功率流 circulating power load- H+ z( F- {1 P0 }6 y9 ?4 o
旋转力矩 running torque
0 T9 k- t: c! S R" f0 c旋转式密封 rotating seal
2 ?& U: n$ p7 d旋转运动 rotary motion5 K7 V! g$ p# \9 T' i" j; g7 U7 q! {. e
选型 type selection
7 D' {! [, y6 q" d! q: s! F% w压力 pressure
1 Q$ l3 ^" R# n! H* t5 i0 q2 G4 o压力中心 center of pressure
8 W5 x8 d; \& p! d6 t1 @压缩机 compressor2 Y. Z% i+ k/ e8 N
压应力 compressive stress
& m+ w' ~0 e0 w' h: T- {, e2 e压力角 pressure angle
, z/ ~+ b, }" L |; ^0 k牙嵌式联轴器 jaw (teeth) positive-contact coupling
6 _3 n0 |- W9 @雅可比矩阵 Jacobi matrix" O8 y) u" _3 C0 n
摇杆 rocker
5 c9 ?7 n+ e; X5 [液力传动 hydrodynamic drive6 a- }; R& g7 N8 k [
液力耦合器 hydraulic couplers V1 \/ X7 g! V6 r8 B# m) x2 e" h- x6 K
液体弹簧 liquid spring
$ [$ y' x* x: d( e% X液压无级变速 hydraulic stepless speed changes
% a6 b* ?4 e. w. W( h( g, Q7 q液压机构 hydraulic mechanism4 F9 n1 o% }8 F5 a4 y0 R
一般化运动链 generalized kinematic chain& p) v: d7 v, f! _8 G
移动从动件 reciprocating follower
1 X2 T3 d, b, E* |6 D# L! |移动副 prismatic pair, sliding pair2 s. f' i! I8 b$ u3 q
移动关节 prismatic joint
' ?" Q9 h. Y% X) {3 n移动凸轮 wedge cam
3 r; M; C4 d# U& J) o" p盈亏功 increment or decrement work* A( {- | Q: Y! f
应力幅 stress amplitude
1 F2 E. k. Y9 T9 {! }应力集中 stress concentration- o; @" m2 }. h2 w3 Y. E* @3 I% v
应力集中系数 factor of stress concentration8 n2 ?3 h6 K' H: r0 `# z) z
应力图 stress diagram
2 r% C% o5 J: Y应力 — 应变图 stress-strain diagram) u0 b; Q7 | S
优化设计 optimal design
e6 ?+ n8 y ]4 b油杯 oil bottle
! ?; a6 J0 F9 s7 Z% D油壶 oil can/ \3 c# H; C: D) d9 E8 k) B
油沟密封 oily ditch seal0 ]( \1 S4 D7 Q" b. \
有害阻力 useless resistance
$ ]+ x1 M' f1 j. p+ F2 R有益阻力 useful resistance0 o; ^- |% i& g8 n# }# f
有效拉力 effective tension. u1 v+ e6 n9 u4 K, Y4 I3 {( T7 x: }
有效圆周力 effective circle force
" P4 Y+ ? A' f9 F9 I- p有害阻力 detrimental resistance2 H$ u$ v( X/ T1 p% v
余弦加速度运动 cosine acceleration (or simple harmonic) motion
4 Y+ W! Y; C _5 b j# B+ |# r预紧力 preload
: a7 r) q$ n2 L) J& l, y5 K8 D原动机 primer mover |
发表于 2008-2-21 11:42:15