CN1048441A - Planetary transmission of circular arc gear engaged with pin gear - Google Patents
Planetary transmission of circular arc gear engaged with pin gear Download PDFInfo
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- CN1048441A CN1048441A CN 89104533 CN89104533A CN1048441A CN 1048441 A CN1048441 A CN 1048441A CN 89104533 CN89104533 CN 89104533 CN 89104533 A CN89104533 A CN 89104533A CN 1048441 A CN1048441 A CN 1048441A
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- gear
- tooth
- pin
- profile
- circular arc
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Abstract
Planetary transmission of circular arc gear engaged with pin gear of the present invention, its engagement driving pair is made of the pin tooth cylndrical surface of the circular tooth gear flank of tooth and pinwheel, the tooth curve of circular tooth gear is single profile of tooth arc toothed or that be made of tangent successively three-arc, during this planet engagement transmission mechanism running, pairing working pressure angle was 0 ° when mesh tooth face pressure was maximum, thereby can improve the bearing capacity and the transmission efficiency of mechanism effectively, under the operating conditions same case, the comparable cycloidal planetary gear speed reducer structure of volume and weight reduces 30%-35%.This driving mechanism can be at chemical industry, mine, metallurgy, national defence, industry light industry textile industry, food, pharmacy, extensive use in the industrial departments such as construction engineering.
Description
The invention belongs to the gear drive of conveying rotary motion, a kind of planet engagement transmission mechanism.
In the prior art field, be used for realizing that the planetary gear mechanism of big speed ratio gearing down mainly contains involute planetary gear gear mechanism and cycloidal-pin wheel planet engagement transmission mechanism.With regard to the involute planetary gear gear mechanism, interfere for fear of the overlapping of the gear teeth, must adopt angle correcting, thereby cause working pressure angle to increase.For example the working pressure angle of a differential teeth planetary gear mechanism is up to 56 °, and working pressure angle is 41 ° during two teeth difference.For cycloidal-pin wheel planet engagement transmission mechanism, cross for fear of the cycloidal gear flank profil and to cut, often getting the curtate ratio value is 0.75～0.5, Dui Ying minimum working pressure angle reaches 41.4 °～60 ° with it.When output torque one timing, because working pressure angle is excessive, will cause bigger flank of tooth pressure, the also corresponding increase of radial load in the mechanism in each supporting.Thereby the bearing capacity and the transmission efficiency of above-mentioned two class mechanisms have been limited.
In order further to improve the bearing capacity and the transmission efficiency of large transmission ratio planetary gear reduction driving mechanism, now be developed into a kind of planetary transmission of circular arc gear engaged with pin gear of being convenient to process, special proposition the present invention.
Description of drawings:
Fig. 1, first kind of engagement driving mode mechanism map;
Fig. 2, second kind of engagement driving mode mechanism map;
Fig. 3, the planetary profile of tooth of single circular arc;
The profile of tooth of Fig. 4, single center of arc wheel;
Fig. 5, the planetary profile of tooth of three-arc;
The profile of tooth of Fig. 6, three-arc central gear;
Fig. 7, be used for the organigram of heavy load gearing down.
Structure of the present invention is, shown in accompanying drawing 1, accompanying drawing 2, it is by at least one pivoted arm (namely be made up of rotating shaft (1) and eccentric bushing (2) or directly make eccentric shaft), in the little gear difference planetary driving mechanism of at least one planetary gear and a fixing center wheel formation, when pivoted arm during as input link, the spinning motion of planetary gear is realized the purpose of big speed ratio deceleration by pivot pin formula mechanism or the output of other forms of mechanism; When planetary gear as input link (by suitable leading input mechanism), and pivoted arm is realized the speedup transmission of big speed ratio during as output link.
First kind of planetary transmission of circular arc gear engaged with pin gear, as shown in Figure 1, rotating shaft (1) is connected (perhaps directly making eccentric shaft) with eccentric bushing (2) with key, (1) is input shaft, planetary pinion (3) is connected with revolute pair with eccentric bushing (2), and pin gear sleeve tube (4) is connected with revolute pair with pivot pin (5), and pivot pin (5) evenly distributes on circumference and is fixed on the pinwheel seat (is central gear, as follows) on (6), pinwheel seat (6) is fixedlyed connected with support.When rotating shaft (1) was turned round, planetary pinion (3) was done the turnover motion, and the cylndrical surface of the circular-arc tooth surface of planetary pinion (3) and pin gear sleeve tube (4) constitutes engagement pair.The axial pin type output mechanism output of the spinning motion of planetary pinion (3) by forming by planetary pinion (3), sleeve (7), pivot pin (8) and the flange plate of fixedlying connected (9) with output shaft.Also can adopt other forms of output mechanism, for example floating disc mechanism, involute zero-tooth-difference mechanism or universal shaft coupling etc.The profile of tooth of planetary pinion (3) can be single arc toothed, and as shown in Figure 3, the O point is planetary geometrical center among the figure, and OX is the symmetry axis of teeth groove, flank profil circular arc K
1K
2K
3Radius be r
Z, center of circle O
ZBe positioned on the OX axis, LOOZ is that planetary geometrical center O point is to flank profil circular arc K
1K
2K
3Center O
ZDistance, Outside radius is Ra, tooth top part flank profil is tangent with circular arc profile and parallel with OX axle straightway K
1K
4And K
3K
5The profile of tooth of planetary pinion (3) also can be the profile of tooth that tangent successively three-arc constitutes, and as shown in Figure 5, the O point is planetary geometrical center among the figure, and OX is the symmetry axis of teeth groove, flank profil circular arc K
11K
12And K
13K
14Radius r
Z1And r
Z3Equate that their center of circle is respectively O
1And O
3, circular arc K at the bottom of the tooth
12K
13Radius be r
Z2, center of circle O
2Be positioned on the OX axle, Outside radius is Ra, and tooth top part flank profil is tangent with circular arc profile and parallel with OX axle straightway K
11K
15And K
14K
16
Second kind of planetary transmission of circular arc gear engaged with pin gear, as shown in Figure 2, the difference of it and first kind of planet engagement transmission mechanism is, planet wheel (10) is connected with revolute pair with pivoted arm, the spinning motion of planet wheel (10) passes through by planet wheel (10), sleeve (7), pivot pin (8) is exported (perhaps input) with axial pin type mechanism or other forms of mechanism that the flange plate of fixedlying connected with output shaft (9) is formed, pin gear sleeve tube (4) is connected with revolute pair with pivot pin (5), pivot pin (5) is evenly distributing on the circumference and is being fixed on the planet wheel (10), circular arc profile face on the cylndrical surface of the pin gear sleeve tube (4) on the planet wheel (10) and the central gear (being arc inner gear, as follows) (11) constitutes engagement pair.Planet wheel (10) is done the turnover motion under the driving of rotating shaft (1).And central gear (11) maintains static.The profile of tooth of central gear (11) is single arc toothed, and as shown in Figure 4, the O point is the geometrical center of central gear among the figure, and OX is the symmetry axis of teeth groove, flank profil circular arc K
6K
7K
8Radius be r
Z, center of circle O
ZBe positioned on the OX axis, LOOZ is that the geometrical center O point of central gear is to flank profil circular arc K
6K
7K
8Center O
ZDistance, Outside radius is Ra, tooth top part flank profil is tangent with circular arc profile and parallel with OX axle straightway K
6K, and K
8K
10The profile of tooth of central gear (11) also can be the profile of tooth that tangent successively three-arc constitutes, and as shown in Figure 6, the O point is the geometrical center of central gear among the figure, and OX is the symmetry axis of teeth groove, flank profil circular arc K
17K
18And K
19K
20Radius r
Z4And r
Z6Equate that their center of circle is respectively O
4And O
6, circular arc K at the bottom of the tooth
18K
19Radius be r
Z5, center of circle O is positioned on the OX axle, and tooth top part flank profil is tangent with circular arc profile and parallel with OX axle straightway K
17K
22And K
20K
21
The theoretical error of single circular arc profile on less important carrying section is bigger, and the gear teeth logarithm of engagement is less simultaneously in the transmission, is applicable to the gearing down under the light load condition usually, as the transmission in clock and watch and other instrument mechanisms and the indexing mechanism; The theoretical error value of the flank profil of three-arc gear and correct flank profil is less than 0.01 millimeter, and direction of error is to make the transverse tooth thickness attenuate, avoids the interference of transmission.In the transmission, the carrying number of teeth can reach 1/7～1/5 of total number of teeth in the time of single planet wheel, thereby is applicable to the gearing down under the heavy load conditions.Under the operating conditions same case, the comparable cycloidal planetary gear speed reducer structure of volume and weight reduces 30%～35%.
If the planet wheel number of teeth is Z
2(being meant the number of teeth of circular tooth gear in accompanying drawing 1 mechanism, is the pin number of teeth of pointer wheel in accompanying drawing 2 mechanisms), the number of teeth of central gear is Z
3(be the pin number of teeth of pointer wheel in accompanying drawing 1 mechanism, be meant the number of teeth of arc inner gear in accompanying drawing 2 mechanisms), then the velocity ratio of mechanism is:
In the formula: ω
1The angular velocity of-input shaft
ω
2The angular velocity of-output shaft
With involute planetary gear gear mechanism and cycloidal-pin wheel planetary gearing mechanism relatively, the present invention also has the advantage of following uniqueness except realizing big speed ratio gearing down and many tooth the carrying simultaneously the characteristics such as engagement:
1. pairing working pressure angle was 0 ° when mesh tooth face pressure was maximum, thereby when load one timing, flank of tooth pressure is little, and the sliding ratio between the engagement element is low, and the bearing capacity of mechanism and transmission efficiency improve;
2. the geometrical shape of engagement pair element is containment, is beneficial to the reduction contact stress;
3. the engagement pair element is positioned in the instantaneous Center circle, and the distribution circle radius at pin tooth center is less than (i
12+ 1) e(e is the throw of eccentric of eccentric bushing (2)), therefore under the condition of given tooth depth, can obtain littler mechanism size;
4. the inner concavity circular arc profile is easily manufactured.
This driving mechanism can extensive use in industrial departments such as chemical industry, mine, metallurgy, national defence, light industry, weaving, food, pharmacy, construction engineering.
Accompanying drawing 7 is embodiment's organigrams that are used for the heavy load gearing down of the present invention.Among the figure, two eccentric bushings (13) are with input shaft (12) revolution, and circle-arc tooth planetary pinion (15), (16) are installed on the eccentric bushing (13) with 180 ° of opposite directions, make mechanism keep in a basic balance.Multiple tooth engagement is simultaneously realized with pin gear sleeve (17) in planetary pinion (15), (16).Member (14), sleeve (18), driving pin (19), flange (20) and output shaft (21) are formed output mechanism.
Engagement driving mode shown in 2 also can adopt two opposite pinwheels of installing to make planetary pinion with reference to the accompanying drawings, and this moment, central gear adopted arc inner gear.When being used for light load transmission such as instrument mechanism or indexing mechanism, only need a planetary pinion and pinwheel engagement driving to realize the purpose of big speed ratio deceleration usually.
Claims (4)
1, a kind of planetary transmission of circular arc gear engaged with pin gear, it comprises that at least one is made up of rotating shaft [1] and eccentric bushing [2] or the pivoted arm of directly making eccentric shaft is input link (perhaps being output link), at least one planet wheel and the little gear difference planetary driving mechanism that fixing central gear constitutes, planetary pinion [3] is connected with revolute pair with pivoted arm, the spinning motion of planetary pinion [3] is by planetary pinion [3], sleeve [7], pivot pin [8] is exported (perhaps input) with axial pin type mechanism or other forms of mechanism that the flange plate of fixedlying connected with output shaft [9] is formed, feature of the present invention is: pin gear sleeve tube [4] is connected with revolute pair with pivot pin [5], pivot pin [5] is evenly distributing on the circumference and is being fixed on the pinwheel seat [6], pinwheel seat [6] is fixedlyed connected with support, and the cylndrical surface of the circular arc profile face of planetary pinion [3] and pin gear sleeve tube [4] constitutes engagement pair.
2, planet engagement transmission mechanism according to claim 1 is characterized in that: the profile of tooth of planetary pinion (3) is single arc toothed K
1K
2K
3, tooth top part flank profil is tangent with circular arc profile and parallel with OX axle straightway K
1K
4And K
3K
5Or the profile of tooth of planetary pinion (3) is the profile of tooth K that tangent successively three-arc constitutes
11K
12, K
12K
13, K
13K
14, tooth top part flank profil is tangent with circular arc profile and parallel with OX axle straightway K
11K
15And K
14K
16
3, a kind of planetary transmission of circular arc gear engaged with pin gear, it comprises that at least one is made of or directly makes the whirling arm mechanism input of eccentric shaft (perhaps output) rotating shaft (1) and eccentric bushing (2), the little gear difference planetary driving mechanism that at least one planet wheel (10) and a fixing central gear (11) constitute, planet wheel (10) is connected with revolute pair with pivoted arm, the spinning motion of planet wheel (10) passes through by planet wheel (10), sleeve (7), ship and sell the axial pin type mechanism of (8) and the flange plate of fixedlying connected (9) composition or mechanism's output (perhaps input) of other patterns with output shaft, feature of the present invention is: pin gear sleeve tube (4) is connected with revolute pair with pivot pin (5), pivot pin (5) is evenly distributing on the circumference and is being fixed on the planet wheel (10), and the cylndrical surface of the pin gear sleeve tube (4) on the planet wheel (10) and the circular arc profile face on the central gear (11) constitute engagement pair.
4, planet engagement transmission mechanism according to claim 3 is characterized in that: the profile of tooth of central gear (11) is single arc toothed K
6K
7K
8, tooth top part flank profil is tangent with circular arc profile and parallel with OX axle straightway K
6K
9And K
8K
10Or the profile of tooth of central gear (11) is the profile of tooth K that tangent successively three-arc constitutes
17K
18, K
18K
19And K
19K
20, tooth top part flank profil is tangent with circular arc profile and parallel with OX axle straightway K
17K
22And K
20K
21
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 89104533 CN1016523B (en) | 1989-06-30 | 1989-06-30 | Planetary transmission of circular arc gear engaged with pin gear |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 89104533 CN1016523B (en) | 1989-06-30 | 1989-06-30 | Planetary transmission of circular arc gear engaged with pin gear |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1048441A true CN1048441A (en) | 1991-01-09 |
| CN1016523B CN1016523B (en) | 1992-05-06 |
Family
ID=4855591
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 89104533 Expired CN1016523B (en) | 1989-06-30 | 1989-06-30 | Planetary transmission of circular arc gear engaged with pin gear |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1016523B (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101248302B (en) * | 2005-11-17 | 2010-05-26 | 丰田自动车株式会社 | Planetary gear device and drive device with the same |
| CN101666367B (en) * | 2009-09-25 | 2012-07-04 | 重庆大学 | Clearance-free planetary drive device |
| CN102797828A (en) * | 2012-08-23 | 2012-11-28 | 吴建林 | R-type gear and application thereof |
| CN108119613A (en) * | 2016-11-30 | 2018-06-05 | 比亚迪股份有限公司 | Planetary speed reducer with small tooth number difference, vehicle-mounted display screen device and vehicle |
| CN109114200A (en) * | 2018-10-25 | 2019-01-01 | 山东柳杭减速机有限公司 | Big registration internal messing Gear Planet Transmission speed reducer |
-
1989
- 1989-06-30 CN CN 89104533 patent/CN1016523B/en not_active Expired
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101248302B (en) * | 2005-11-17 | 2010-05-26 | 丰田自动车株式会社 | Planetary gear device and drive device with the same |
| CN101666367B (en) * | 2009-09-25 | 2012-07-04 | 重庆大学 | Clearance-free planetary drive device |
| CN102797828A (en) * | 2012-08-23 | 2012-11-28 | 吴建林 | R-type gear and application thereof |
| CN108119613A (en) * | 2016-11-30 | 2018-06-05 | 比亚迪股份有限公司 | Planetary speed reducer with small tooth number difference, vehicle-mounted display screen device and vehicle |
| WO2018099392A1 (en) * | 2016-11-30 | 2018-06-07 | 比亚迪股份有限公司 | Planetary speed reducer with small tooth difference, in-vehicle display, and vehicle |
| CN109114200A (en) * | 2018-10-25 | 2019-01-01 | 山东柳杭减速机有限公司 | Big registration internal messing Gear Planet Transmission speed reducer |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1016523B (en) | 1992-05-06 |
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