CN2255528Y - Multi-throw crank inside engaged planetary driving mechanism - Google Patents
Multi-throw crank inside engaged planetary driving mechanism Download PDFInfo
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- CN2255528Y CN2255528Y CN 96231781 CN96231781U CN2255528Y CN 2255528 Y CN2255528 Y CN 2255528Y CN 96231781 CN96231781 CN 96231781 CN 96231781 U CN96231781 U CN 96231781U CN 2255528 Y CN2255528 Y CN 2255528Y
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- China
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- crank
- gear
- crankshafts
- planetary gearing
- internal
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Abstract
The utility model provides a multi-throw crank inside engaged planetary driving mechanism, the inertial force and the moment of inertia of which are completely balanced. The utility model is characterized in that a high speed shaft gearwheel 1 is simultaneously meshed with two intermediate wheels 2, the intermediate wheels 2 are respectively meshed with an end gearwheel 3, and the high speed shaft gearwheel 1, the two intermediate wheels 2 and the end gearwheel 3 are positioned at the front end of the mechanism; four segments (or six segments), etc. of eccentric cranks in a central antisymmetric geometric shape are respectively arranged on two roots of crank shafts 6, the two roots of crank shafts 6 and four (or six) ring sheet 4 form four (or six) parallel crank link mechanisms in space, and the parallel crank link mechanisms conduct planetary motion orderly. The utility model has the advantages of high reliability, high accuracy and low noise. A single stage i max is 80 to 150 and eta is 92 to 98%.
Description
The utility model belongs to mechanical subject Gear Planet Transmission technical field.According to International Patent Classification (IPC) IPC
5Regulation can be summarized in F16H
1/ 00 or F16H
21/
00Classification position.
The application's background technique is the basic theory of mechanical subject---" planar linkage " and " interior engagement planetary gear train " these two academic problems.Gear Planet Transmission is the mediator mechanism of power engine and actuator.Its superior performance, just in a lot of fields, particularly big retarding replaces traditional approachs such as conventional gear, worm gear than in the transmission, and development prospect is long-range.
But the Gear Planet Transmission technology waits perfect.On long terms to there being following problem:
1. the inertial force and the moment of inertia that are produced when turning round, dynamic unbalance is difficult to high speed operation;
2. tie-rod connecting lever bearing is positioned at cardia, and stressed very big, the life-span is not long;
3.W output mechanism is undesirable, a lot of types adopt the overhang general layout, often damage;
4. most model structure complexity, particularly cycloidal-pin wheel transmission, there are many holes, Xiao, cover in the border, the more difficult processing of flute profile, the technological design level is not high;
5. Gear Planet Transmission must mesh how much calculating and strength calculation method in the obligato involute less tooth difference, lacks unified standard, and many tame theories are diverse and confused, unable to decide which is right, in fact respectively have length partially.Design with data in addition and plagiarize mutually, cause the plant design personnel of basic unit to be difficult to follow, more need use computer program, promote difficulty.
So for many years we are fermenting the concrete scheme that solves above problem always.
Browsed Soviet Union's books and periodicals of publishing the eighties in recent years, saw the data of " engagement Gear Planet Transmission in the monocycle ", and, assert that " monocycle machine " solved above big portion problem, and opened up the path for handling a dynamic balancing difficult problem through great deal of calculation and analysis.
Finding Britain's improvement " monocycle machine " in 1991 again is the information of " three ring machines ", is inspired.On above-mentioned basis, we study for many years, design and advanced development, have proposed " multi-turn crank internal engagement planetary gearing mechanism " patent application (hereinafter to be referred as the PS machine).
We think that the patent No. is " 85106692 ", and denomination of invention is that " three-ring type deceleration (or speedup) transmission device " advantage is a lot, but the subject matter that exists is and the dynamic balancing of unresolved inertial force and moment of inertia.The mechanical model of " three-ring type slow down (or speedup) transmission device " interior two bent axles, with the Sun Huan of Northwestern Polytechnical University professor the 547th page of Figure 13-6 of " Der Grundsatz der Maschinen " book of showing identical.The conclusion of this book is: " ... be the stiffness rotor of dynamic unbalance ... need add counterweight, just get complete equilibrium ".(in March, 1989, Higher Education Publishing House's version).All " Der Grundsatz der Maschinen " university teaching materials all are these viewpoints, therefore needn't prove again.
The purpose of this utility model is to avoid above-mentioned deficiency of the prior art and multi-turn crank internal engagement planetary gearing mechanism that a kind of inertial force and moment of inertia complete equilibrium are provided.
The purpose of this utility model can reach by following measure:
A kind of multi-turn crank internal engagement planetary gearing mechanism, it through slowing down, drives two crankshafts 6 and ring plate 4 by high speed shaft gear 1, makes internal gear 9 and central gear 5 engagements, spreads out of power through output shaft 7, it is characterized in that:
A. high speed shaft gear 1 meshes with two intermediary wheels 2 simultaneously, and intermediary wheel 2 meshes with end tooth wheel 3 respectively, and they are positioned at mechanism's leading portion;
B. on two crankshafts 6, respectively be provided with four sections isogonic innermost being handles that are center antisymmetry geometrical shape, these two crankshafts 6 and four ring plates 4 are at synthetic four the parallel crank connecting rod linking mechanisms of spatial group;
C. internal gear 9 is contained on the ring plate 4, and their geometry symmetry center overlaps.
The purpose of this utility model can also reach by following measure:
High speed shaft gear 1, intermediary wheel 2, end tooth wheel 3 can change the number of teeth and speed change;
On two crankshafts 6, respectively be provided with six sections cranks that are center antisymmetry geometrical shape, these two crankshafts 6 and six ring plates 4 are at synthetic six the parallel crank connecting rod linking mechanisms of spatial group;
Four sections cranks are at the phase angle difference in space: first section crank and second section crank are 90 °, and second section crank and the 3rd section crank are 180 °, and the 3rd section crank and the 4th section crank are 90 °;
Central gear 5 is involute or cycloidal tooth profile with the basic tooth profile of internal gear 9;
Between internal gear 9 and the ring plate 4 elastic buffer part 8 is housed.
Fig. 1 is transmission principle figure of the present utility model.
Fig. 2 is Fig. 1 drawing in side sectional elevation.
Among the figure: 1, high speed shaft gear 2, intermediary wheel
3, end tooth wheel 4, ring plate
5, central gear 6, crankshaft
7, output shaft 8, elastic buffer part
9, internal gear
Know by " theoretical mechanics ": a double-crank parallelogram linkage, when their crank is done the constant speed rotation, the motion of each point on the connecting rod, with the motion of crankpin end points, identical.The ring plate 4 of present patent application, being developed by above connecting rod exactly forms, and the center of internal gear 9 then is located at the connecting rod center.
So when double crank shaft by casing location during rotation, the center of internal gear 9 will rotate around the center of output shaft 7.
Known by " Der Grundsatz der Maschinen ": the length of double-crank, as isometric with the centre distance of interior engagement wheel set, when then double crank mechanism rotates, internal gear 9 will be made the planet gear motion around central gear 5, by central gear 5 outputting powers.
The rationale that Here it is " engagement Gear Planet Transmission in the monocycle "." monocycle " more than four string is gathered into folds, be contained on the central gear 5, identical with two again crankshaft connects (respectively making four sections isogonic innermost being handles that are center antisymmetry geometrical shape on the crankshaft) so just combine and be " four turn crank internal engagement planetary gearing mechanisms ".Four internal gears 9 will have sequentially around central gear 5 circulation engagements.
After the same method, " monocycle " more than six string is gathered into folds, be contained on the central gear 5, identical with two again crankshaft connects (respectively making six sections isogonic innermost being handles that are center antisymmetry geometrical shape on the crankshaft), is " six turn crank internal engagement planetary gearing mechanisms " so just combine.Six internal gears 9 will have sequentially around central gear 5 circulation engagements." six turn the PS machine " is used in the high-power and transmission angle error requirements occasion of strictness especially.
More than two kinds of situations, make initiatively two crankshafts 6 of rotation, be by high speed shaft gear 1, drive end teeth wheel 3 by intermediary wheel 2 and pass to crankshaft 6, at last by output shaft 7 outputting powers.
The velocity ratio computational methods of PS machine
i
15＝n
1/n
5＝i
13×i
47
i
13＝(Z
2/Z
1)×(Z
3/Z
2)＝Z
3/Z
1
i
45＝-Z
5/(Z
4-Z
5)
∴i
15＝-Z
3Z
5/Z
1(Z
4-Z
5)
n
7＝n
1/i
15
Z
1---the high speed shaft gear number of teeth
Z
2---the intermediary wheel number of teeth
Z
3---the end tooth wheel gear
Z
4---the internal gear number of teeth on the ring plate
Z
5---the central gear number of teeth
n
1---the high speed shaft rotating speed (rev/min)
n
7---defeated speed axle rotating speed (rev/min)
i
13---velocity ratio between the wheel from the high speed shaft to the end tooth
i
47---velocity ratio between internal gear and the central gear
i
15---high speed shaft is to velocity ratio between the output shaft
Through research for many years, trial-production, improvement, predetermined technical goal realizes basically.The present is made effect relatively with the example product relevant with background technique:
PS---160 speed reducers
Parameter is as follows: the high H in center
0=160, centre distance=150, output shaft diameter d
2=70, boundary dimension length * wide * high=560 * 310 * 330, im
Ax=99, when motor 1500rpm, output is changeed apart from T
2=2000Nm
A, contrast Chongqing three ring machine product samples: the high H in center
0=165, centre distance=175, output shaft diameter d
2=75, boundary dimension length * wide * high=585 * 200 * 433, i
Max=99, when motor 1500rpm, output is changeed apart from T
2=1424Nm
Conclusion: with H
0Be contrast base figure, the two boundary dimension and weight are approaching, the T of PS machine
2Value improves 1.4 times than three ring machines.The PS machine has solved dynamic balancing, allows with the 3000rpm power input to machine.
B, contrast Shanghai cycloid machine product sample: the high H in center
0=160, belong to No. 13 support, d
2=55, boundary dimension is 390 * 300 * 355, i
Max=87, when motor 1500rpm, T
2=800Nm
Conclusion: with H
0Be contrast base figure, PS machine width, but the PS machine improves 2.5 times than cycloid machine output torque, the motor-driven state property of PS can be good, shake for a short time, and noise is low, and permission is with the 3000rpm power input to machine.
C, contrast SJ type planet gear speed reducer with small tooth difference (Shanghai Institute of Nuclear Engineering's development)
The high H in center
0=160, belong to 80 types, d
2=55, boundary dimension is 320 * 330 * 438, i
Max=91 (single-stages) when motor 1500rpm, allowable torque T
2=800Nm
Conclusion: omit together with B, slightly
The utility model has following advantage compared to existing technology:
1. it has cancelled conventional W output mechanism, and the Gear Planet Transmission form is thoroughly simplified; It has realized many rings, leggy, multiple tooth circulation engagement, has given full play to that engagement driving bearing capacity in the gear is big, the strong point of stable performance.So possessed as condition huge, heavily loaded, high precision apparatus, transmitting torque is greater than 400 kilonewton meters, the transmission angle error less than 3 '～10 ', can be applicable to fields such as heavy duty industrials such as metallurgy, mine, lifting and precision machine tool, instrument, robot, miniature medicine instrument, chromatic printing machine.
2.＜and the PS machine〉inertial force and moment of inertia can not balances when having properly settled the running of conventional Gear Planet Transmission a difficult problem, so possessed as the high speed machine set condition, the commentaries on classics scooter 3000 of per minute input power changes more than～5000 commentaries on classics, can apply to Aeronautics and Astronautics, military science and speedup mechanical field.
3.＜and the PS machine〉realized the power dividing principle, make the heavy load of conventional Gear Planet Transmission connecting lever bearing share 8 (or 12) crank throw necks; Because of all parts all are in the geometrical center symmetry status with respect to output shaft, so each fulcrum reaction power reduces because of supporting each other significantly, the optimum stressed general layout of full unit Weak link-free has appearred again.So＜PS machine〉stable prolongation of life-span, have high reliability, high degree of safety, can be applicable to fields such as high-altitude machinery, the transportation of cableway hawser, tourism, high risk operation, poisonous medium environment.Human life safety and the protection of valuables assets product had high safety factor.
4.＜and the PS machine〉be inside and outside two pairs of gear teeth meshing in essence, satisfy the abundant and necessary condition that conjugate profiles engagement theorem requires, sliding scale is little, various interference have been avoided again, and at each turning joint dress rolling bearing, the total transmission efficiency η of unit=92～98%, and η does not increase and sharply reduces with velocity ratio i.(η ≠ f (i
-1), efficient is not the inverse ratio function of velocity ratio i), so＜the PS machine〉be a kind of energy-conserving product, than the worm and gear transmission of routine, WW, N, NN, RV Gear Planet Transmission efficient height are a lot.
Claims (6)
1. multi-turn crank internal engagement planetary gearing mechanism, it through slowing down, drives two crankshafts (6) and ring plate (4) by high speed shaft gear (1), and internal gear (9) and central gear (5) are meshed, and spreads out of power through output shaft (7), it is characterized in that:
A. high speed shaft gear (1) meshes with two intermediary wheels (2) simultaneously, and intermediary wheel (2) meshes with end tooth wheel (3) respectively, and they are positioned at mechanism's leading portion;
B. on two crankshafts (6), respectively be provided with four sections isogonic innermost being handles that are center antisymmetry geometrical shape, these two crankshafts (6) synthesize four parallel crank connecting rod linking mechanisms with four ring plates (4) in spatial group;
C. internal gear (9) is contained on the ring plate (4), and their geometry symmetry center overlaps.
2. multi-turn crank internal engagement planetary gearing mechanism according to claim 1 is characterized in that high speed shaft gear (1), intermediary wheel (2), end tooth wheel (3) can change the number of teeth and speed change.
3. multi-turn crank internal engagement planetary gearing mechanism according to claim 1, it is characterized in that on two crankshafts (6), respectively be provided with six sections cranks that are center antisymmetry geometrical shape, these two crankshafts (6) synthesize six parallel crank connecting rod linking mechanisms with six ring plates (4) in spatial group.
4. multi-turn crank internal engagement planetary gearing mechanism according to claim 1, it is characterized in that the phase angle difference of four sections cranks in the space: first section crank and second section crank are 90 °, second section crank and the 3rd section crank are 180 °, and the 3rd section crank and the 4th section crank are 90 °.
5. multi-turn crank internal engagement planetary gearing mechanism according to claim 1 is characterized in that the central gear (5) and the basic tooth profile of internal gear (9) are involute or cycloidal tooth profile.
6. multi-turn crank internal engagement planetary gearing mechanism according to claim 1 is characterized in that between internal gear (9) and the ring plate (4) elastic buffer part (8) being housed.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 96231781 CN2255528Y (en) | 1996-05-03 | 1996-05-03 | Multi-throw crank inside engaged planetary driving mechanism |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 96231781 CN2255528Y (en) | 1996-05-03 | 1996-05-03 | Multi-throw crank inside engaged planetary driving mechanism |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN2255528Y true CN2255528Y (en) | 1997-06-04 |
Family
ID=33908869
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 96231781 Expired - Fee Related CN2255528Y (en) | 1996-05-03 | 1996-05-03 | Multi-throw crank inside engaged planetary driving mechanism |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN2255528Y (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105673795A (en) * | 2016-03-23 | 2016-06-15 | 刘有双 | Accelerator |
-
1996
- 1996-05-03 CN CN 96231781 patent/CN2255528Y/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105673795A (en) * | 2016-03-23 | 2016-06-15 | 刘有双 | Accelerator |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C19 | Lapse of patent right due to non-payment of the annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |