CN1024585C - Internally engaged planetary driving machanism with new structure - Google Patents
Internally engaged planetary driving machanism with new structure Download PDFInfo
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- CN1024585C CN1024585C CN 90106138 CN90106138A CN1024585C CN 1024585 C CN1024585 C CN 1024585C CN 90106138 CN90106138 CN 90106138 CN 90106138 A CN90106138 A CN 90106138A CN 1024585 C CN1024585 C CN 1024585C
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Abstract
The present invention relates to an internal engagement planet transmission device in a novel structure, which is used for speed reduction or speed increase. The internal engagement planet transmission device uses a multicrank rolling planet gear (10) as a rotation transmission mechanism, and support disks (4, 7) are arranged on the shaft extension of the multicrank rolling planet gear (10) and tightly fixed on the shaft extension of the multicrank rolling planet gear (10) to form a whole; a plurality of cranks (6) of an input shaft (3) are provided with a plurality of planet gears (2) which are staggered by an angle of 180 degrees and engaged with an internal gear (1) so as to form force division and balance, so that the bearing capacity is improved by about one half, wherein the structures and the technical parameters of the planet gears (2) are the same; in addition, the service life of the bearing is extended, and the internal engagement planet transmission device has stable operation and low noise. The present invention designs 21 types of devices whose central heights are from 80 to 1000 millimeters at present, the maximum transmission torsion moment is 100 tun. M, and the transmission power is more than 100 kilowatts.
Description
The present invention relates to gear drive, be specifically related to the internally engaged planetary driving machanism of multicrank rolling star-wheel as rotation transfer mechanism.
The inventor discloses with the less-tooth-difference planetary transmission of crank throw formula rolling star-wheel as rotation transfer mechanism in number of patent application is 88105740.1 file, it obviously is better than the bearing pin guide transfer mechanism that rotates, and keeps high working life when bearing heavy duty but the rolling bearing force-bearing situation on the crank throw still influences it; At US4,656, narrated rolling star-wheel with two double-cranks in No. 891 patent documentations as rotation transfer mechanism, this device is to be meshed with two external gears simultaneously by the central gear on the input shaft, and external gear is contained in respectively on the double-crank spider gear shaft, drives two planetary pinions simultaneously by the bearing on the crank, therefore this crank star-wheel transfer mechanism that not only rotates, also bear the radial component of gear pair simultaneously, load is too concentrated, and bearing capacity is restricted.
The present invention is intended to overcome above-mentioned deficiency, thereby a kind of internally engaged planetary driving machanism that can bear heavy duty and the comparatively ideal new structure of shaft strength is provided.
Transmission device of the present invention be adopt have shaft extension and at the multicrank rolling star-wheel that supporting disk is housed on the shaft extension as be meshed with an internal gear shunting of formation power and balanced realization of staggered 180 ° of whiles of a plurality of structures planetary pinion identical with technical parameter is housed on rotation transfer mechanism and the multicrank by input shaft.
Below in conjunction with accompanying drawing in detail the present invention is described in detail:
Fig. 1: adopt rotate transfer mechanism and have the planetary-gear speed reducer structure principle chart of balace weight of double-crank rolling star-wheel;
Fig. 2: adopt the rotate planetary-gear speed reducer structure principle chart of transfer mechanism of three-throw rolling star-wheel;
Fig. 3: adopt the rotate planetary-gear speed reducer structural drawing of transfer mechanism of double-crank rolling star-wheel;
Fig. 4: the K that is Fig. 3 is to sectional view.
Fig. 5: adopt the rotate side-mounted planetary-gear speed reducer structural drawing of transfer mechanism of double-crank rolling star-wheel.
Basic structure of the present invention shown in Figure 1 is mainly by internal gear [1], planetary gear [2], power shaft [3], right supporting disk [4], bolster [5], crank [6], left supporting disk [7], balancer [8], output shaft [9], crank star-wheel [10] and casing [11] consist of, power shaft [3] is for (Fig. 1 is two with a plurality of, Fig. 2 is three) axle of crank [6], a plurality of cranks [6] are by eccentric staggered 180 ° of settings, the eccentric throw a of a plurality of cranks [6] is identical, power shaft [3] is coaxial and be supported in the endoporus of casing [11] and bearing block (referring to Fig. 3 with rolling bearing respectively with output shaft [9], Fig. 5), on a plurality of cranks [6] of power shaft [3] respectively the rolling bearing (also claiming rotary arm bearing) by same size a plurality of structures are installed and technical parameter identical, the number of teeth is the planetary gear [2] of even number, so just, can make a plurality of planetary gears [2] with off-centre staggered 180 ° symmetrically be fastened on the casing [11], the number of teeth is that an internal gear [1] of even number meshes synchronously, reach the purpose of the radial load shunting on the power shaft [3], on the power shaft [3], two bidirectional balanced devices [8] are equipped with in two outsides of a plurality of planetary gears [2], so that it produces the axial tilting moment that a pair of couple comes the balance planetary gear set to produce when motion, the computing formula of design balance device [8] is:
Fo×L＝F×l
In the formula: the centrifugal force that the Fo-equalizer member produces;
The centrifugal force that each planetary gear set of F-is produced,
The distance of two equalizer member centers of gravity of L-,
The axial distance of l-planetary gear set center of gravity,
When a plurality of planetary pinions [2] are two when above (referring to Fig. 2), form bidirectional balanced system by a plurality of planetary gear sets; It is n the halving hole of Dz that the distribution circle diameter is arranged on the planetary pinion [2], the multicrank of n crank star-wheel [10] is contained in n the halving hole on a plurality of planetary pinions [2] by rolling bearing respectively, the eccentric staggered 180 ° of settings of crank on the crank star-wheel [10], the throw of eccentric a of the crank [6] on its throw of eccentric a and the input shaft [3] equates, crank star-wheel [10] two ends have shaft extension, two shaft extensions are in the uniform hole of Dz by the distribution circle diameter identical with planetary pinion [2] that rolling bearing is loaded on right supporting disk [4] and left supporting disk [7] respectively, the bore dia of the bearing of above-mentioned installation crank star-wheel [10] is identical, planetary pinion [2] and right supporting disk [4], left side supporting disk [7] go up to also have with the distribution circle diameter be n the hole that the staggered symmetrically arranged distribution circle diameter in hole of Dz is Dx, it is n the through hole of Dx that n supporting axle [5] passes the last distribution circle diameter of a plurality of planetary pinions [2] respectively, and the two ends axle journal of supporting axle [5] inserts right supporting disk [4] respectively and the last distribution circle diameter of left supporting disk [7] is in the hole of Dx, with two supporting disks fastening be whole, planetary pinion [2] and right supporting disk [4], left side supporting disk [7] is gone up the distribution circle diameter Dz of the distribution circle diameter Dx in the hole that n supporting axle [5] is installed greater than the hole that n crank star-wheel [10] is installed, for avoiding interfering, the diameter D that the last distribution circle diameter of planetary pinion [2] is n the hole of Dx should be greater than the diameter d and the twice throw of eccentric a sum of the supporting axle that passes above-mentioned hole [5], be that D＞d+2a(is referring to Fig. 4), said structure makes the shaft strength situation on the crank star-wheel [10] comparatively desirable.When transmission device of the present invention is worked, motion is imported from input shaft [3], promote planetary pinion [2] by eccentric mechanism [6] and the rolling bearing on it, planetary pinion [2] is meshed with internal gear [1], make planetary pinion [2] produce revolution and rotation, planetary pinion [2] drives crank star-wheel [10] again and does rotation and revolution, it passes to right supporting disk [4] and left supporting disk [7] by the rolling bearing on the shaft extension of two ends with spinning motion again, when right supporting disk [7] and output shaft [9] when being solidified as a whole, internal gear [1] is fixed tightly in casing [11], casing [11] is fixing, then the bearing on the supporting disk promotes output shaft [9] and makes spinning motion, thereby the output of the motion after will slowing down, this is planetary pinion output pattern; Otherwise if output shaft [9] is fixing, casing [11] is fixing, and then internal gear [1] drive casing [11] rotates together, and planetary pinion this moment [2] is only done revolution and do not done rotation, thus formation internal gear output pattern; Also internal gear [1] and output shaft [9] can be solidified as a whole in the transmission device of the present invention, and supporting disk [4] is fixed tightly in fixing casing [11], then forms the pattern of internal gear output.
Shown in Figure 2 is the planetary driving device structure principle chart of a kind of variation of Fig. 1, its crank star-wheel [15] has three sections cranks, three sections cranks are also arranged on the input shaft [12], middle one section crank is adorned two planetary pinions [2], about two sections cranks [6] respectively adorn a planetary pinion [2], also two between among four planetary pinions [2] can be merged into a width and equal former two planetary pinion, left side supporting disk [7] is tightened to integral body with right supporting disk [4] by supporting axle [14] and is solidified as a whole with output shaft [9], staggered 180 ° of whiles of four planetary pinions [2] are meshed with a internal gear [16] on being fixed in casing [13], and all the other are identical with Fig. 1.Can also be three above cranks according to using needs, star-wheel and a plurality of planetary structure of planetary a plurality of cranks more than four, its principle is with aforementioned.
Internal gear pair of the present invention can be an Involute Gear Pair, can also be cycloid tooth wheel set or circular-arc gear pair.
The power input shaft of transmission device of the present invention other member of connecting just can be formed the retarder or the speed increaser of various needs, then becomes motor direct-connection type gear motor as series electric motor; Series connection ting model planetary-gear speed reducer then becomes the planetary-gear speed reducer of twin-stage transmission; The NOW planetary mechanism that series connection is made up of sun gear, planetary pinion and internal gear then becomes the planetary-gear speed reducer of another kind of twin-stage transmission; The a pair of umbrella gear of connecting then becomes the planetary-gear speed reducer of vertical output; The a pair of worm gear pair of connecting then becomes the planetary-gear speed reducer of vertical output and energy self-locking; The a pair of cylindrical gears of connecting then becomes input output out-of-alignment planetary-gear speed reducer etc.
The present invention has designed the product center height at present from 21 types of 80～1000 millimeters, and its transmitting torque is 100 tons of rice to the maximum, and transmitted power is more than 1000 kilowatts.
Advantage of the present invention:
1. in the like product, the ability key of bearing heavy duty is stressed equilibrium, the present invention adopts supporting disk to make the shaft strength of rotation transfer mechanism obtain comparatively ideal equilibrium, balace weight is set on input shaft again or utilizes staggered 180 ° of whiles of a plurality of planetary pinions and an internal gear to mesh and reach power shunting and balanced, make the bearing capacity of this device improve about 1/2 than known technology;
2. owing to the equilibrium of power, corresponding bearing prolongs working life;
3. because the equilibrium of power, stable drive when this device is imported in high speed, noise are low;
4. planetary pinion and internal gear are the even number tooth, and technology capability is good in groups, are easy to guarantee transmission accuracy;
5. the hole of passing supporting axle on the planetary pinion is symmetrical arranged for staggered with the hole that the crank star-wheel is installed, and has made full use of planetary area, makes the radial dimension of device not increase, and axial dimension increases little.
Embodiment 1:(is referring to accompanying drawing 3 and 4)
Rolling bearing [18] is housed on two cranks of 6 double-crank star-wheels [19], the distribution circle diameter that they are inserted in respectively on two planetary pinions [42] is in 6 halving holes of Dz, the distribution circle diameter that the two axial ends of crank star-wheel [19] is equipped with rolling bearing [17] and is inserted in left supporting disk [39] and right supporting disk [43] is respectively used back-up ring [37], [21] to block bearing outer ring then and is made it axially locating also in the halving hole of Dz; Internal gear [41] uses bolton on casing [40]; Rolling bearing [20] all is housed in the center hole of two planetary pinions [42] and is installed in respectively on two staggered 180 ° the eccentric bushing [26] (being crank), the throw of eccentric of eccentric bushing [26] is a, with key [25] eccentric bushing [26] is sleeved on the axle journal of input shaft [24], an end of input shaft [24] is bearing in the hole of bearing support [28] with rolling bearing [23].The other end is bearing in the endoporus of output shaft [32] with rolling bearing [35], and balace weight [34] and Balance disc [22] also are equipped with in the outside of input shaft [24] upper planetary gear [42]; Output shaft [32] rolling bearing [33], [36] be bearing in two endoporus of casing [40] and axially locating carried out in bearing [36] outer ring with back-up ring [38], casing [40] is fixing, diameter is that the left end axle journal of the six roots of sensation supporting axle [29] of d is fastened on left supporting disk [39] respectively to go up the distribution circle diameter be in the halving hole of Dx, it is through hole D(Dx＞Dz of Dx that the right-hand member axle journal of supporting axle [29] passes the last distribution circle diameter of planetary pinion [42], D＞d+2a) use ringfeder [30] and right supporting disk [43] to be fastenedly connected again, ringfeder [30] is tightened with bolt [27], such two supporting disks [39], [43] be tightened to an integral body by six roots of sensation supporting axle [29], with left supporting disk [39] key [31] and the fastening connection of output shaft, this device just becomes the pattern of planetary pinion output; The staggered 180 ° of gear pairs with an internal gear [41] synchromesh of two planetary pinions [42] in the present embodiment are Involute Gear Pair.
Embodiment 2:(is referring to Fig. 5)
This practicality example is side-mounted transmission device, be with the difference of last example: the rolling bearing [33] on the output shaft [44] is installed in the endoporus of support [45], because supporting disk and output shaft [44] are tightened to integral body, support [45] is that the side dress is more firm in addition, so another bearing [36] on the output shaft [44] can be divided in the endoporus that is arranged in bearing support [28] on the right supporting disk [43], can shorten axial dimension significantly like this.
Claims (9)
1, a kind of internally engaged planetary driving machanism of new structure is mainly by internal gear [1], planetary pinion [2], input shaft [3], right supporting disk [4], supporting disk [5], crank [6], left side supporting disk [7], balace weight [8], output shaft [9], crank star-wheel [10] and casing [11] constitute, input shaft [3] is for having the axle of a plurality of cranks [6], input shaft [3] is coaxial and be supported in the endoporus of casing [11] and bearing support with rolling bearing respectively with output shaft [9], a plurality of planetary pinions [2] are contained on a plurality of cranks [6] of input shaft [3] with the rolling bearing of same size respectively, it is n the halving hole of Dz that the distribution circle diameter is arranged on a plurality of planetary pinions [2], a plurality of cranks of n crank star-wheel [10] are contained in n the halving hole of a plurality of planetary pinions [2] by rolling bearing respectively, internal gear [1] is solidified as a whole with casing [11], also but internal gear [1] is solidified as a whole with output shaft [9], planetary pinion [2] is meshed with internal gear [1], it is characterized in that:
The two ends of a:n crank star-wheel [10] all have shaft extension, the distribution circle diameter that two shaft extensions are loaded on right supporting disk [4] and left supporting disk [7] by rolling bearing respectively is in n the uniform hole of Dz, it is n the hole of Dx that the distribution circle diameter that also has with the staggered symmetric arrangement in a said n hole is gone up in planetary pinion [2] and left and right supporting disk [7], [4], and n the through hole that n supporting axle [5] passes respectively on a plurality of planetary pinions [2] is fastening for whole with left and right supporting disk [7], [4];
B: a plurality of cranks [6] on the input shaft [3] and a plurality of cranks on n the crank star-wheel [10] are all by eccentric staggered 180 ° of settings, and the throw of eccentric a of the crank on the throw of eccentric a of the crank [6] on the input shaft [3] and the crank star-wheel [10] equates;
C: the identical a plurality of planetary pinions [2] that make of the structure of a plurality of planetary pinions [2] and technical parameter mesh synchronously with an internal gear [1] for staggered 180 ° symmetrically with off-centre.
2, transmission device according to claim 1 is characterized in that internal gear [1] and planetary pinion [2] all adopt the even number tooth.
3, transmission device according to claim 1 is characterized in that the distribution circle diameter Dz of the distribution circle diameter Dx in the hole of n supporting axle of installation [5] on planetary pinion [2], right supporting disk [4] and the left supporting disk [7] greater than the hole that n crank star-wheel [10] is installed.
4, transmission device according to claim 1 is characterized in that the bore dia of the rolling bearing of installation crank star-wheel [10] on planetary pinion [2], right supporting disk [4] and the left supporting disk [7] is identical.
5,, it is characterized in that diameter d and twice throw of eccentric a sum, the i.e. D＞d+2a of the aperture D in n the hole that the last distribution circle diameter of planetary pinion [2] is Dx greater than the supporting axle that passes above-mentioned hole [5] according to claim 1 and 3 described transmission devices.
6, transmission device according to claim 1 when it is characterized in that a plurality of planetary pinions [2] are elected two as, is equipped with bidirectional balanced device [8] on the input shaft [3] in planetary two outsides.
7, transmission device according to claim 1 when it is characterized in that a plurality of planetary pinions [2] are elected three and four as, is then formed bidirectional balanced system by three and four planetary gear sets itself.
8, transmission device according to claim 1 is characterized in that internal gear [1] and casing [11] are fixed tightly in a time-out, and left supporting disk [7] is solidified as a whole with output shaft [9]; Also but internal gear [1] is solidified as a whole with output shaft [9], and right supporting disk [4] is fixed tightly in fixing casing [11].
9, transmission device according to claim 1 is characterized in that the gear pair that is meshed can be that Involute Gear Pair can also be cycloidal gear or circular-arc gear pair.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 90106138 CN1024585C (en) | 1990-12-15 | 1990-12-15 | Internally engaged planetary driving machanism with new structure |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 90106138 CN1024585C (en) | 1990-12-15 | 1990-12-15 | Internally engaged planetary driving machanism with new structure |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1062407A CN1062407A (en) | 1992-07-01 |
| CN1024585C true CN1024585C (en) | 1994-05-18 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 90106138 Expired - Fee Related CN1024585C (en) | 1990-12-15 | 1990-12-15 | Internally engaged planetary driving machanism with new structure |
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| Country | Link |
|---|---|
| CN (1) | CN1024585C (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100451384C (en) * | 2004-01-30 | 2009-01-14 | 纳博特斯克株式会社 | Eccentric swing type planetary gear device |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2007020999A1 (en) * | 2005-08-18 | 2007-02-22 | Ntn Corporation | Power transmission device |
| CN102996780A (en) * | 2012-10-09 | 2013-03-27 | 吴小杰 | Grease lubricated star wheel speed reducer for bearing |
| CN102996776B (en) * | 2012-10-09 | 2016-06-22 | 陈伟 | The large-scale star wheel gear box of bearing grease lubrication |
| CN104964000A (en) * | 2015-06-24 | 2015-10-07 | 常州市芯微电子有限公司 | Small-tooth-difference high-precision cycloid gear speed reducer |
| CN114263716A (en) * | 2021-12-28 | 2022-04-01 | 江苏中工高端装备研究院有限公司 | High-efficiency large-torque star wheel transmission device for brick making extruder |
-
1990
- 1990-12-15 CN CN 90106138 patent/CN1024585C/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100451384C (en) * | 2004-01-30 | 2009-01-14 | 纳博特斯克株式会社 | Eccentric swing type planetary gear device |
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| Publication number | Publication date |
|---|---|
| CN1062407A (en) | 1992-07-01 |
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