CN1865731A - Planetary balance-wheel speed reducer - Google Patents
Planetary balance-wheel speed reducer Download PDFInfo
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- CN1865731A CN1865731A CNA2006100543520A CN200610054352A CN1865731A CN 1865731 A CN1865731 A CN 1865731A CN A2006100543520 A CNA2006100543520 A CN A2006100543520A CN 200610054352 A CN200610054352 A CN 200610054352A CN 1865731 A CN1865731 A CN 1865731A
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- end cap
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
Abstract
The invention discloses a planet wobble wheel reducer, especially providing an inner-ring low-differential planet transmission reducer. Said invention comprises a tank, an end cover, an inner tooth ring, the first straight gear wheel or incline gear wheel reducing part, and the second planet wobble wheel reducing part; wherein, the first straight gear wheel or incline gear wheel reducing part is mainly formed by straight tooth or incline tooth input gear wheel axle, 2-8 straight tooth or incline tooth driven gear wheels; the second planet wobble wheel reducing part is mainly formed by one eccentric cranks that fixing straight tooth or incline tooth driven gear wheels, 1-4 wobble wheels, and the output axle. The invention has compact structure, large transmission rate, high carrying ability and high accuracy.
Description
Technical field:
The invention belongs to gear drive, particularly interior ring type little tooth difference Gear Planet Transmission speed reducer.
Background technique:
The ring type speed reduction gearing adopts few tooth difference transmission principle, have advantages such as compact structure, big, the multiple tooth engagement of velocity ratio, overload property are good, be widely used in the machinery of industries such as metallurgy, mine, chemical industry, building, agricultural, communications and transportation, generating, especially be widely used especially at heavy duty equipment.Therefore, the ring type speed reducer of development function admirable has significant role to the production of China's machinery industry, to promoting the promulgated by the State Council economic development significant.
Ring type little tooth difference planetary reduction gear in existing is " the interior three-ring gear reducer " of 200410046112.7 patent disclosures as application number, mainly comprises: ring flat-plate, two eccentric input shaft, output shaft, the ring gear that has internal tooth, support, end cap etc.Its ring flat-plate is equated and is all had two outer ring plates and an inner ring plate of external tooth and forms by weight and external diameter, and the angle of two outer ring plate symmetry axis and an inner ring plate symmetry axis is 180 °, and the external tooth of ring flat-plate and the internal tooth of ring gear are that the transmission of tooth difference is meshed less.The eccentric input of its pair bent axle comprises the input shaft of coaxial decentraction and three symmetry axis of ring flat-plate.But, by theory analysis and experimental results show that present ring-type gear reducer exists vibration, noise, temperature rise and bearing early damage in actual use, increased output mechanism, the efficient of retarder is reduced, shortcomings, particularly retarder such as and manufacture cost increases, and bearing capacity is not strong in continuously running, heavy duty, at a high speed, problem is more outstanding under the big speed ratio operating mode, influenced it greatly and applied, the technical problem that the ring type gear reducer needs to be resolved hurrily in becoming.
Summary of the invention:
The objective of the invention is deficiency, a kind of planetary balance-wheel speed reducer is provided, have compact structure, simple at ring type little tooth difference planetary reduction gear in existing, velocity ratio is big, and carrying and overload capacity are strong, and machining accuracy easily guarantees, low cost of manufacture, vibration, noise is little, characteristics such as rapid heat dissipation.
The object of the present invention is achieved like this: a kind of planetary balance-wheel speed reducer mainly comprises: slow down part and second level planetary balance-wheel reduction part of round box, two end caps, the ring gear that has internal tooth, first order spur gear or helical gear graded.First order spur gear or the helical gear part of slowing down is made up of the input gear shaft of straight-tooth or helical teeth and 2-8 straight-tooth or helical teeth driven gear; Second level planetary balance-wheel deceleration part is mainly by the 2-8 that is connected with a driven gear eccentric crankshaft and 1-4 escapement that has an identical external tooth and innerly form for discoidal output shaft etc., wherein eccentric crankshaft is combined by pivoted arm and eccentric bushing, and eccentric bushing is fixed in the middle part of pivoted arm.Be connected with the ring gear of band internal tooth on the inwall of round box, the internal tooth of ring gear is involute tooth or pin tooth.Two end caps are separately positioned on the two end part of casing, the input gear shaft passes the center of an end end cap and flexibly connects by bearing and end cap, output shaft passes the center of the other end end cap and flexibly connects by bearing and end cap, and the input gear shaft is concentric out-of-alignment symmetry axis with output shaft.Tooth on the input gear shaft is straight-tooth or helical teeth.At arranged outside one supporting disk of the inboard of end cap and input gear shaft, supporting disk flexibly connects by bearing and end cap, and supporting disk supports eccentric crankshaft and revolves round the sun with eccentric crankshaft.2-8 driven gear is fixed in respectively on the corresponding eccentric crankshaft, and 2-8 driven gear is divided into one deck or two-layer circumferencial direction along the input gear shaft evenly distributes, and simultaneously and the input gear shaft mesh.The two ends of each eccentric crankshaft are respectively by bearing and flexibly connect with the integrated disc portions of supporting disk and output shaft respectively.1-4 escapement also flexibly connects with eccentric crankshaft respectively by bearing respectively, the symmetry axis of escapement is coaxial decentraction with the symmetry axis of driven gear, angle between 1-4 escapement evenly distributes along the inner circumference of round box, the external tooth of 1-4 escapement is involute-type tooth or gerotor type tooth, the involute-type external tooth while of 1-4 escapement and the involute-type internal tooth engagement of the ring gear of casing, perhaps the gerotor type external tooth of 1-4 the escapement while meshes with the pin type internal tooth of the ring gear of casing, finishes few tooth difference transmission output.
Retarded motion process of the present invention is as follows: power is by the input of input gear shaft, mesh with straight-tooth or helical teeth on 2-8 the driven gear by the straight-tooth or the helical teeth of input on the gear shaft, thereby 2-8 driven gear rotated, realize that first order straight-tooth or helical teeth slow down and power dividing.The rotation of 2-8 driven gear drives corresponding eccentric crankshaft and rotates, the rotation of eccentric crankshaft drives 1-4 escapement and produces swing, since the ring gear that is engaged be fixed on the casing motionless, therefore the swing of escapement forces the center line revolution of eccentric crankshaft around output shaft, be bearing on the supporting disk by bearing respectively and the defeated integrated disc portions of output because of the eccentric crankshaft two ends again, so eccentric crankshaft drives output shaft and rotates, the output of realization power, it is zero crank-type output mechanism that output shaft and escapement constitute velocity ratio, realizes second level deceleration.
After the present invention adopts technique scheme, have compact structure, simple, velocity ratio is big, and carrying and overload capacity are strong, and machining accuracy easily guarantees, low cost of manufacture is vibrated, noise is little, advantages such as rapid heat dissipation.The present invention can be widely used in the machinery such as metallurgy, mine, chemical industry, communications and transportation, building, agricultural, generating, engineering machinery.
Description of drawings:
Fig. 1 is a hyperbolic axle double pendulum wheel planetary balance-wheel speed reducer structural representation of the present invention;
Fig. 2 is the A-A sectional view of Fig. 1;
Fig. 3 is three-crankshaft three escapement planetary balance-wheel speed reducer structural representations of the present invention;
Fig. 4 is the A-A sectional view of Fig. 3;
Fig. 5 is three-crankshaft two escapement planetary balance-wheel speed reducer structural representations of the present invention;
Fig. 6 is the A-A sectional view of Fig. 5;
Fig. 7 is four bent axles, four escapement planetary balance-wheel speed reducer structural representations of the present invention;
Fig. 8 is the A-A sectional view of Fig. 7;
Fig. 9 is six bent axles, four escapement planetary balance-wheel speed reducer structural representations of the present invention;
Figure 10 is the A-A sectional view of Fig. 9;
Figure 11 is three-crankshaft three escapement planetary balance-wheel speed reducer transmission principle figure of the present invention;
Figure 12 is six bent axles, four escapement planetary balance-wheel speed reducer transmission principle figure of the present invention.
Among the figure: 1 is the input gear shaft, and 2 is supporting disk, and 3 is driven gear, and 4 is eccentric crankshaft, and 5 is escapement, and 6 is spacer sleeve, and 7 is seal ring, and 8,13 is end cap, and 9 is output shaft, and 10 is bearing, and 11 is casing, and 12 is ring gear.
Embodiment:
Below in conjunction with embodiment, the present invention is further described.
As shown in Figure 1, 2, a kind of hyperbolic axle double pendulum wheel planetary balance-wheel speed reducer mainly comprises: round box 11, two end caps 8 and 13, the ring gear 12 that has internal tooth, first order spur gear deceleration part and second level planetary balance-wheel reduction part are graded.First order spur gear deceleration part is made up of input gear shaft 1 and 2 straight-tooth driven gears 3 of straight-tooth; Second level planetary balance-wheel deceleration part is mainly by 2 eccentric crankshafts 4 that are connected with driven gear 3 and 2 escapements 5 that have an identical external tooth and innerly form for discoidal output shaft 9 etc., wherein eccentric crankshaft 4 is combined by pivoted arm and eccentric bushing, and eccentric bushing is fixed in the middle part of pivoted arm by key.Be connected with the ring gear 12 of band internal tooth on the inwall of round box 11, the internal tooth of ring gear 12 is an involute tooth.Two end caps 8 and 13 are separately positioned on the two end part of casing, input gear shaft 1 passes the center of an end end cap 13 and flexibly connects by bearing and end cap 13, output shaft 9 passes the center of the other end end cap 8 and flexibly connects by bearing and end cap 8, and input gear shaft 1 is concentric out-of-alignment symmetry axis with output shaft 9.Tooth on the input gear shaft 1 is a straight-tooth.At arranged outside one supporting disk 2 of the inboard of end cap 13 and input gear shaft 1, supporting disk 2 flexibly connects by bearing and end cap 13, and supporting disk 2 supports eccentric crankshafts 4 and revolves round the sun with eccentric crankshaft 4.2 driven gears 3 are fixed in respectively on 2 corresponding eccentric crankshafts 4, and 2 driven gears 3 are divided into one deck and evenly distribute along the circumferencial direction of importing gear shaft 1, and while and 1 engagement of input gear shaft.The two ends of eccentric crankshaft 4 are respectively by bearing and flexibly connect with the integrated disc portions of supporting disk 2 and output shaft 9 respectively.2 escapements 5 flexibly connect with eccentric crankshaft 4 respectively by bearing respectively, the symmetry axis of escapement 5 is coaxial decentraction with the symmetry axis of driven gear 3, angle between 2 escapements 5 evenly distributes along the inner circumference of round box 11, the external tooth of 2 escapements 5 is the involute-type tooth, the involute-type external tooth while of 2 escapements 5 and the involute-type internal tooth engagement of the ring gear 12 of casing 11, finish few tooth difference transmission output.
Shown in Fig. 3,4, a kind of three-crankshaft three escapement planetary balance-wheel speed reducers mainly comprise: slow down part and second level planetary balance-wheel reduction part of round box 11, two end caps 8 and 13, the ring gear 12 that has internal tooth, first order helical gears graded.First order helical gear slows down and partly is made up of input gear shaft 1 and 3 helical teeth driven gears 3 of helical teeth; Second level planetary balance-wheel deceleration part is mainly by 3 eccentric crankshafts 4 that are connected with driven gear 3 and 3 escapements 5 that have an identical external tooth and innerly form for discoidal output shaft 9 etc., wherein eccentric crankshaft 4 is combined by pivoted arm and eccentric bushing, and eccentric bushing is fixed in the middle part of pivoted arm by key.Be connected with the ring gear 12 of band internal tooth on the inwall of round box 11, the internal tooth of ring gear 12 is an involute tooth.Two end caps 8 and 13 are separately positioned on the two end part of casing, input gear shaft 1 passes the center of an end end cap 13 and flexibly connects by bearing and end cap 13, output shaft 9 passes the center of the other end end cap 8 and flexibly connects by bearing and end cap 8, and input gear shaft 1 is concentric out-of-alignment symmetry axis with output shaft 9.Tooth on the input gear shaft 1 is a helical teeth.At arranged outside one supporting disk 2 of the inboard of end cap 13 and input gear shaft 1, supporting disk 2 flexibly connects by bearing and end cap 13, and supporting disk 2 supports eccentric crankshafts 4 and revolves round the sun with eccentric crankshaft 4.3 driven gears 3 are fixed in respectively on 3 corresponding eccentric crankshafts 4, and 3 driven gears 3 are divided into one deck and evenly distribute along the circumferencial direction of importing gear shaft 1, and while and 1 engagement of input gear shaft.The two ends of eccentric crankshaft 4 are respectively by bearing and flexibly connect with the integrated disc portions of supporting disk 2 and output shaft 9 respectively.3 escapements 5 flexibly connect with eccentric crankshaft 4 respectively by bearing respectively, the symmetry axis of escapement 5 is coaxial decentraction with the symmetry axis of driven gear 3, angle between 3 escapements 5 evenly distributes along the inner circumference of round box 11, the external tooth of 3 escapements 5 is the involute-type tooth, the involute-type external tooth while of 3 escapements 5 and the involute-type internal tooth engagement of the ring gear 12 of casing 11, finish few tooth difference transmission output.
Shown in Fig. 5,6, a kind of three-crankshaft double pendulum wheel planetary balance-wheel speed reducer mainly comprises: slow down part and second level planetary balance-wheel reduction part of round box 11, two end caps 8 and 13, the ring gear 12 that has internal tooth, first order helical gears graded.First order helical gear slows down and partly is made up of input gear shaft 1 and 3 straight-tooth driven gears 3 of helical teeth; Second level planetary balance-wheel deceleration part is mainly by 3 eccentric crankshafts 4 that are connected with driven gear 3 and 2 escapements 5 that have an identical external tooth and innerly form for discoidal output shaft 9 etc., wherein eccentric crankshaft 4 is combined by pivoted arm and eccentric bushing, and eccentric bushing is fixed in the middle part of pivoted arm by key.Be connected with the ring gear 12 of band internal tooth on the inwall of round box 11, the internal tooth of ring gear 12 is the pin tooth.Two end caps 8 and 13 are separately positioned on the two end part of casing, input gear shaft 1 passes the center of an end end cap 13 and flexibly connects by bearing and end cap 13, output shaft 9 passes the center of the other end end cap 8 and flexibly connects by bearing and end cap 8, and input gear shaft 1 is concentric out-of-alignment symmetry axis with output shaft 9.Tooth on the input gear shaft 1 is a helical teeth.At arranged outside one supporting disk 2 of the inboard of end cap 13 and input gear shaft 1, supporting disk 2 flexibly connects by bearing and end cap 13, and supporting disk 2 supports eccentric crankshafts 4 and revolves round the sun with eccentric crankshaft 4.3 driven gears 3 are fixed in respectively on 3 corresponding eccentric crankshafts 4, and 3 driven gears 3 are divided into one deck and evenly distribute along the circumferencial direction of importing gear shaft 1, and while and 1 engagement of input gear shaft.The two ends of eccentric crankshaft 4 are respectively by bearing and flexibly connect with the integrated disc portions of supporting disk 2 and output shaft 9 respectively.2 escapements 5 flexibly connect with eccentric crankshaft 4 respectively by bearing respectively, the symmetry axis of escapement 5 is coaxial decentraction with the symmetry axis of driven gear 3, angle between 2 escapements 5 evenly distributes along the inner circumference of round box 11, the external tooth of 2 escapements 5 is the gerotor type tooth, the gerotor type external tooth while of 2 escapements 5 and the pin type internal tooth engagement of the ring gear 12 of casing 11, finish few tooth difference transmission output.
Shown in Fig. 7,8, a kind of four bent axles, four escapement planetary balance-wheel speed reducers mainly comprise: round box 11, two end caps 8 and 13, the ring gear 12 that has internal tooth, first order spur gear deceleration part and second level planetary balance-wheel reduction part are graded.First order spur gear deceleration part is made up of input gear shaft 1 and 4 straight-tooth driven gears 3 of straight-tooth; Second level planetary balance-wheel deceleration part is mainly by 4 eccentric crankshafts 4 that are connected with driven gear 3 and 4 escapements 5 that have an identical external tooth and innerly form for discoidal output shaft 9 etc., wherein eccentric crankshaft 4 is combined by pivoted arm and eccentric bushing, and eccentric bushing is fixed in the middle part of pivoted arm by key.Be connected with the ring gear 12 of band internal tooth on the inwall of round box 11, the internal tooth of ring gear 12 is an involute tooth.Two end caps 8 and 13 are separately positioned on the two end part of casing, input gear shaft 1 passes the center of an end end cap 13 and flexibly connects by bearing and end cap 13, output shaft 9 passes the center of the other end end cap 8 and flexibly connects by bearing and end cap 8, and input gear shaft 1 is concentric out-of-alignment symmetry axis with output shaft 9.Tooth on the input gear shaft 1 is a straight-tooth.At arranged outside one supporting disk 2 of the inboard of end cap 13 and input gear shaft 1, supporting disk 2 flexibly connects by bearing and end cap 13, and supporting disk 2 supports eccentric crankshafts 4 and revolves round the sun with eccentric crankshaft 4.4 driven gears 3 are fixed in respectively on 4 corresponding eccentric crankshafts 4, and 4 driven gears 3 are divided into one deck and evenly distribute along the circumferencial direction of importing gear shaft 1, and while and 1 engagement of input gear shaft.The two ends of eccentric crankshaft 4 are respectively by bearing and flexibly connect with the integrated disc portions of supporting disk 2 and output shaft 9 respectively.4 escapements 5 flexibly connect with eccentric crankshaft 4 respectively by bearing respectively, the symmetry axis of escapement 5 is coaxial decentraction with the symmetry axis of driven gear 3, angle between 4 escapements 5 evenly distributes along the inner circumference of round box 11, the external tooth of 4 escapements 5 is the involute-type tooth, the involute-type external tooth while of 4 escapements 5 and the involute-type internal tooth engagement of the ring gear 12 of casing 11, finish few tooth difference transmission output.
Shown in Fig. 9,10, a kind of six bent axles, four escapement planetary balance-wheel speed reducers mainly comprise: round box 11, two end caps 8 and 13, the ring gear 12 that has internal tooth, first order spur gear deceleration part and second level planetary balance-wheel reduction part are graded.First order spur gear deceleration part is made up of input gear shaft 1 and 6 straight-tooth driven gears 3 of straight-tooth; Second level planetary balance-wheel deceleration part is mainly by 6 eccentric crankshafts 4 that are connected with driven gear 3 and 4 escapements 5 that have an identical external tooth and innerly form for discoidal output shaft 9 etc., wherein eccentric crankshaft 4 is combined by pivoted arm and eccentric bushing, and eccentric bushing is fixed in the middle part of pivoted arm by key.Be connected with the ring gear 12 of band internal tooth on the inwall of round box 11, the internal tooth of ring gear 12 is an involute tooth.Two end caps 8 and 13 are separately positioned on the two end part of casing, input gear shaft 1 passes the center of an end end cap 13 and flexibly connects by bearing and end cap 13, output shaft 9 passes the center of the other end end cap 8 and flexibly connects by bearing and end cap 8, and input gear shaft 1 is concentric out-of-alignment symmetry axis with output shaft 9.Tooth on the input gear shaft 1 is a straight-tooth.At arranged outside one supporting disk 2 of the inboard of end cap 13 and input gear shaft 1, supporting disk 2 flexibly connects by bearing and end cap 13, and supporting disk 2 supports eccentric crankshafts 4 and revolves round the sun with eccentric crankshaft 4.6 driven gears 3 are fixed in respectively on 6 corresponding eccentric crankshafts 4, and 6 driven gears 3 are divided into two-layer circumferencial direction along input gear shaft 1 and evenly distribute, and while and 1 engagement of input gear shaft.The two ends of eccentric crankshaft 4 are respectively by bearing and flexibly connect with the integrated disc portions of supporting disk 2 and output shaft 9 respectively.4 escapements 5 flexibly connect with eccentric crankshaft 4 respectively by bearing respectively, the symmetry axis of escapement 5 is coaxial decentraction with the symmetry axis of driven gear 3, angle between 4 escapements 5 evenly distributes along the inner circumference of round box 11, the external tooth of 4 escapements 5 is the involute-type tooth, the involute-type external tooth while of 4 escapements 5 and the involute-type internal tooth engagement of the ring gear 12 of casing 11, finish few tooth difference transmission output.
Claims (6)
1, a kind of planetary balance-wheel speed reducer, mainly comprise: round box (11), two end caps (8,13), the ring gear (12) that has internal tooth, it is characterized in that also comprising that first order spur gear or helical gear slow down partly and second level planetary balance-wheel deceleration part, first order spur gear or the helical gear part of slowing down is made up of the input gear shaft (1) of straight-tooth or helical teeth and 2-8 straight-tooth or helical teeth driven gear (3), second level planetary balance-wheel deceleration part mainly is made up of for discoidal output shaft (9) with 1-4 escapement (5) and the inner that has identical external tooth 2-8 the eccentric crankshaft (4) that is connected with driven gear (3), wherein eccentric crankshaft (4) is combined by pivoted arm and eccentric bushing, eccentric bushing is fixed in the middle part of pivoted arm, on the inwall of round box (11), be connected with the ring gear (12) of band internal tooth, the internal tooth of ring gear (12) is involute tooth or pin tooth, two end caps (8,13) be separately positioned on the two end part of casing (11), input gear shaft (1) passes the center of an end end cap (13) and flexibly connects by bearing and end cap (13), output shaft (9) passes the center of the other end end cap (8) and flexibly connects by bearing and end cap (8), input gear shaft (1) is concentric out-of-alignment symmetry axis with output shaft (9), tooth on the input gear shaft (1) is straight-tooth or helical teeth, arranged outside one supporting disk (2) at the inboard of end cap (13) and input gear shaft (1), supporting disk (2) flexibly connects by bearing and end cap (13), supporting disk (2) supports eccentric crankshaft (4) and revolves round the sun with eccentric crankshaft (4), 2-8 driven gear (3) is fixed in respectively on the corresponding eccentric crankshaft (4), the circumferencial direction that 2-8 driven gear (3) is divided into one deck or two-layer edge input gear shaft (1) evenly distributes, and mesh with input gear shaft (1) simultaneously, the two ends of each eccentric crankshaft (4) respectively by bearing and respectively with the flexible connection of the integrated disc portions of supporting disk (2) and output shaft (9), 1-4 escapement (5) also flexibly connects with eccentric crankshaft (4) respectively by bearing respectively, the symmetry axis of escapement (5) is coaxial decentraction with the symmetry axis of driven gear (3), angle between 1-4 the escapement (5) evenly distributes along the inner circumference of round box (11), the external tooth of 1-4 escapement (5) is involute-type tooth or gerotor type tooth, the involute-type internal tooth engagement of the involute-type external tooth while of 1-4 escapement (5) and the ring gear (12) of casing (11), perhaps the gerotor type external tooth of 1-4 escapement (5) while meshes with the pin type internal tooth of the ring gear (12) of casing (11).
2, planetary balance-wheel speed reducer according to claim 1, it is characterized in that a kind of hyperbolic axle double pendulum wheel planetary balance-wheel speed reducer, mainly comprise: round box (11), two end caps (8,13), the ring gear (12) that has internal tooth, first order spur gear deceleration part and second level planetary balance-wheel deceleration part, first order spur gear deceleration part is made up of input gear shaft (1) and 2 straight-tooth driven gears (3) of straight-tooth, second level planetary balance-wheel deceleration part mainly is made up of for discoidal output shaft (9) with 2 escapement (5) and the inners that have identical external tooth 2 eccentric crankshafts (4) that are connected with driven gear (3), wherein eccentric crankshaft (4) is combined by pivoted arm and eccentric bushing, eccentric bushing is fixed in the middle part of pivoted arm by key, on the inwall of round box (11), be connected with the ring gear (12) of band internal tooth, the internal tooth of ring gear (12) is an involute tooth, two end caps (8,13) be separately positioned on the two end part of casing, input gear shaft (1) passes the center of an end end cap (13) and flexibly connects by bearing and end cap (13), output shaft (9) passes the center of the other end end cap (8) and flexibly connects by bearing and end cap (8), input gear shaft (1) is concentric out-of-alignment symmetry axis with output shaft (9), tooth on the input gear shaft (1) is a straight-tooth, arranged outside one supporting disk (2) at the inboard of end cap (13) and input gear shaft (1), supporting disk (2) flexibly connects by bearing and end cap (13), supporting disk (2) supports eccentric crankshaft (4) and revolves round the sun with eccentric crankshaft (4), 2 driven gears (3) are fixed in respectively on corresponding 2 eccentric crankshafts (4), 2 driven gears (3) are divided into one deck and evenly distribute along the circumferencial direction of importing gear shaft (1), and mesh with input gear shaft (1) simultaneously, the two ends of eccentric crankshaft (4) respectively by bearing and respectively with the flexible connection of the integrated disc portions of supporting disk (2) and output shaft (9), 2 escapements (5) flexibly connect with eccentric crankshaft (4) respectively by bearing respectively, the symmetry axis of escapement (5) is coaxial decentraction with the symmetry axis of driven gear (3), angle between 2 escapements (5) evenly distributes along the inner circumference of round box (11), the external tooth of 2 escapements (5) is the involute-type tooth, the involute-type external tooth while of 2 escapements (5) and the involute-type internal tooth engagement of the ring gear (12) of casing (11).
3, planetary balance-wheel speed reducer according to claim 1, it is characterized in that a kind of three-crankshaft three escapement planetary balance-wheel speed reducers, mainly comprise: round box (11), two end caps (8,13), the ring gear (12) that has internal tooth, first order helical gear slows down partly and second level planetary balance-wheel deceleration part, first order helical gear slows down and partly is made up of input gear shaft (1) and 3 helical teeth driven gears (3) of helical teeth, second level planetary balance-wheel deceleration part mainly is made up of for discoidal output shaft (9) with 3 escapement (5) and the inners that have identical external tooth 3 eccentric crankshafts (4) that are connected with driven gear (3), wherein eccentric crankshaft (4) is combined by pivoted arm and eccentric bushing, eccentric bushing is fixed in the middle part of pivoted arm by key, on the inwall of round box (11), be connected with the ring gear (12) of band internal tooth, the internal tooth of ring gear (12) is an involute tooth, two end caps (8,13) be separately positioned on the two end part of casing, input gear shaft (1) passes the center of an end end cap (13) and flexibly connects by bearing and end cap (13), output shaft (9) passes the center of the other end end cap (8) and flexibly connects by bearing and end cap (8), input gear shaft (1) is concentric out-of-alignment symmetry axis with output shaft (9), tooth on the input gear shaft (1) is a helical teeth, arranged outside one supporting disk (2) at the inboard of end cap (13) and input gear shaft (1), supporting disk (2) flexibly connects by bearing and end cap (13), supporting disk (2) supports eccentric crankshaft (4) and revolves round the sun with eccentric crankshaft (4), 3 driven gears (3) are fixed in respectively on corresponding 3 eccentric crankshafts (4), 3 driven gears (3) are divided into one deck and evenly distribute along the circumferencial direction of importing gear shaft (1), and mesh with input gear shaft (1) simultaneously, the two ends of eccentric crankshaft (4) respectively by bearing and respectively with the flexible connection of the integrated disc portions of supporting disk (2) and output shaft (9), 3 escapements (5) flexibly connect with eccentric crankshaft (4) respectively by bearing respectively, the symmetry axis of escapement (5) is coaxial decentraction with the symmetry axis of driven gear (3), angle between 3 escapements (5) evenly distributes along the inner circumference of round box (11), the external tooth of 3 escapements (5) is the involute-type tooth, the involute-type external tooth while of 3 escapements (5) and the involute-type internal tooth engagement of the ring gear (12) of casing (11).
4, planetary balance-wheel speed reducer according to claim 1, it is characterized in that a kind of three-crankshaft double pendulum wheel planetary balance-wheel speed reducer, mainly comprise: round box (11), two end caps (8,13), the ring gear (12) that has internal tooth, first order helical gear slows down partly and second level planetary balance-wheel deceleration part, first order helical gear slows down and partly is made up of input gear shaft (1) and 3 straight-tooth driven gears (3) of helical teeth, second level planetary balance-wheel deceleration part mainly is made up of for discoidal output shaft (9) with 2 escapement (5) and the inners that have identical external tooth 3 eccentric crankshafts (4) that are connected with driven gear (3), wherein eccentric crankshaft (4) is combined by pivoted arm and eccentric bushing, eccentric bushing is fixed in the middle part of pivoted arm by key, on the inwall of round box (11), be connected with the ring gear (12) of band internal tooth, the internal tooth of ring gear (12) is the pin tooth, two end caps (8,13) be separately positioned on the two end part of casing, input gear shaft (1) passes the center of an end end cap (13) and flexibly connects by bearing and end cap (13), output shaft (9) passes the center of the other end end cap (8) and flexibly connects by bearing and end cap (8), input gear shaft (1) is concentric out-of-alignment symmetry axis with output shaft (9), tooth on the input gear shaft (1) is a helical teeth, arranged outside one supporting disk (2) at the inboard of end cap (13) and input gear shaft (1), supporting disk (2) flexibly connects by bearing and end cap (13), supporting disk (2) supports eccentric crankshaft (4) and revolves round the sun with eccentric crankshaft (4), 3 driven gears (3) are fixed in respectively on corresponding 3 eccentric crankshafts (4), 3 driven gears (3) are divided into one deck and evenly distribute along the circumferencial direction of importing gear shaft (1), and mesh with input gear shaft (1) simultaneously, the two ends of eccentric crankshaft (4) respectively by bearing and respectively with the flexible connection of the integrated disc portions of supporting disk (2) and output shaft (9), 2 escapements (5) flexibly connect with eccentric crankshaft (4) respectively by bearing respectively, the symmetry axis of escapement (5) is coaxial decentraction with the symmetry axis of driven gear (3), angle between 2 escapements (5) evenly distributes along the inner circumference of round box (11), the external tooth of 2 escapements (5) is the gerotor type tooth, the gerotor type external tooth while of 2 escapements (5) and the pin type internal tooth engagement of the ring gear (12) of casing (11).
5, planetary balance-wheel speed reducer according to claim 1, it is characterized in that a kind of four bent axles, four escapement planetary balance-wheel speed reducers, mainly comprise: round box (11), two end caps (8,13), the ring gear (12) that has internal tooth, first order spur gear deceleration part and second level planetary balance-wheel deceleration part, first order spur gear deceleration part is made up of input gear shaft (1) and 4 straight-tooth driven gears (3) of straight-tooth, second level planetary balance-wheel deceleration part mainly is made up of for discoidal output shaft (9) with 4 escapement (5) and the inners that have identical external tooth 4 eccentric crankshafts (4) that are connected with driven gear (3), wherein eccentric crankshaft (4) is combined by pivoted arm and eccentric bushing, eccentric bushing is fixed in the middle part of pivoted arm by key, on the inwall of round box (11), be connected with the ring gear (12) of band internal tooth, the internal tooth of ring gear (12) is an involute tooth, two end caps (8,13) be separately positioned on the two end part of casing, input gear shaft (1) passes the center of an end end cap (13) and flexibly connects by bearing and end cap (13), output shaft (9) passes the center of the other end end cap (8) and flexibly connects by bearing and end cap (8), input gear shaft (1) is concentric out-of-alignment symmetry axis with output shaft (9), tooth on the input gear shaft (1) is a straight-tooth, arranged outside one supporting disk (2) at the inboard of end cap (13) and input gear shaft (1), supporting disk (2) flexibly connects by bearing and end cap (13), supporting disk (2) supports eccentric crankshaft (4) and revolves round the sun with eccentric crankshaft (4), 4 driven gears (3) are fixed in respectively on corresponding 4 eccentric crankshafts (4), 4 driven gears (3) are divided into one deck and evenly distribute along the circumferencial direction of importing gear shaft (1), and mesh with input gear shaft (1) simultaneously, the two ends of eccentric crankshaft (4) respectively by bearing and respectively with the flexible connection of the integrated disc portions of supporting disk (2) and output shaft (9), 4 escapements (5) flexibly connect with eccentric crankshaft (4) respectively by bearing respectively, the symmetry axis of escapement (5) is coaxial decentraction with the symmetry axis of driven gear (3), angle between 4 escapements (5) evenly distributes along the inner circumference of round box (11), the external tooth of 4 escapements (5) is the involute-type tooth, the involute-type external tooth while of 4 escapements (5) and the involute-type internal tooth engagement of the ring gear (12) of casing (11).
6, planetary balance-wheel speed reducer according to claim 1, it is characterized in that a kind of six bent axles, four escapement planetary balance-wheel speed reducers, mainly comprise: round box (11), two end caps (8,13), the ring gear (12) that has internal tooth, first order spur gear deceleration part and second level planetary balance-wheel deceleration part, first order spur gear deceleration part is made up of input gear shaft (1) and 6 straight-tooth driven gears (3) of straight-tooth, second level planetary balance-wheel deceleration part mainly is made up of for discoidal output shaft (9) with 4 escapement (5) and the inners that have identical external tooth 6 eccentric crankshafts (4) that are connected with driven gear (3), wherein eccentric crankshaft (4) is combined by pivoted arm and eccentric bushing, eccentric bushing is fixed in the middle part of pivoted arm by key, on the inwall of round box (11), be connected with the ring gear (12) of band internal tooth, the internal tooth of ring gear (12) is an involute tooth, two end caps (8,13) be separately positioned on the two end part of casing, input gear shaft 1 passes the center of an end end cap (13) and flexibly connects by bearing and end cap (13), output shaft (9) passes the center of the other end end cap (8) and flexibly connects by bearing and end cap (8), input gear shaft (1) is concentric out-of-alignment symmetry axis with output shaft (9), tooth on the input gear shaft (1) is a straight-tooth, arranged outside one supporting disk (2) at the inboard of end cap (13) and input gear shaft (1), supporting disk (2) flexibly connects by bearing and end cap (13), supporting disk (2) supports eccentric crankshaft (4) and revolves round the sun with eccentric crankshaft (4), 6 driven gears (3) are fixed in respectively on corresponding 2 eccentric crankshafts (4), 6 driven gears (3) are divided into two-layer circumferencial direction along input gear shaft (1) and evenly distribute, and mesh with input gear shaft (1) simultaneously, the two ends of eccentric crankshaft (4) respectively by bearing and respectively with the flexible connection of the integrated disc portions of supporting disk (2) and output shaft (9), 4 escapements (5) flexibly connect with eccentric crankshaft (4) respectively by bearing respectively, the symmetry axis of escapement (5) is coaxial decentraction with the symmetry axis of driven gear (3), angle between 4 escapements (5) evenly distributes along the inner circumference of round box (11), the external tooth of 4 escapements (5) is the involute-type tooth, the involute-type external tooth while of 4 escapements (5) and the involute-type internal tooth engagement of the ring gear (12) of casing (11).
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2006100543520A CN100414139C (en) | 2006-06-12 | 2006-06-12 | Planetary balance-wheel speed reducer |
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| Application Number | Priority Date | Filing Date | Title |
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| CNB2006100543520A CN100414139C (en) | 2006-06-12 | 2006-06-12 | Planetary balance-wheel speed reducer |
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| CN1865731A true CN1865731A (en) | 2006-11-22 |
| CN100414139C CN100414139C (en) | 2008-08-27 |
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| CNB2006100543520A Expired - Fee Related CN100414139C (en) | 2006-06-12 | 2006-06-12 | Planetary balance-wheel speed reducer |
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104154185A (en) * | 2014-08-19 | 2014-11-19 | 郑州高端装备与信息产业技术研究院有限公司 | Built-in planetary transmission high-rigidity small-tooth-difference gear transmission device |
| CN104500661A (en) * | 2015-01-15 | 2015-04-08 | 重庆大学 | Composite high-order cycloidal planetary transmission device |
| CN108953501A (en) * | 2018-09-19 | 2018-12-07 | 杭州星河传动机械研究院有限公司 | Multi-eccentric speed reducer |
| US11365786B2 (en) * | 2017-11-14 | 2022-06-21 | Kimex Group s.r.o. | Transmission |
| US11506262B2 (en) * | 2018-09-10 | 2022-11-22 | Valeo Systèmes d'Essuyage | Mechanical reduction gearing and associated geared motor |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN85205664U (en) * | 1985-12-28 | 1986-12-10 | 沈阳矿山机器厂 | Planetary reducer with internal gear |
| CN2037791U (en) * | 1988-10-22 | 1989-05-17 | 钟建民 | Stepless variator |
| CN2099224U (en) * | 1991-07-20 | 1992-03-18 | 兰州减速机厂 | Stepless epicyclic speed reducer |
| CN2438872Y (en) * | 1999-09-14 | 2001-07-11 | 胡瑞生 | Three crankshaft tilting ring machine |
| JP3934336B2 (en) * | 2000-12-21 | 2007-06-20 | 住友重機械工業株式会社 | Method for reducing backlash of simple planetary gear mechanism and method for manufacturing the same |
| CN1189680C (en) * | 2003-05-14 | 2005-02-16 | 重庆大学 | Conical cycloid wheel planet transmission means |
-
2006
- 2006-06-12 CN CNB2006100543520A patent/CN100414139C/en not_active Expired - Fee Related
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104154185A (en) * | 2014-08-19 | 2014-11-19 | 郑州高端装备与信息产业技术研究院有限公司 | Built-in planetary transmission high-rigidity small-tooth-difference gear transmission device |
| CN104500661A (en) * | 2015-01-15 | 2015-04-08 | 重庆大学 | Composite high-order cycloidal planetary transmission device |
| US11365786B2 (en) * | 2017-11-14 | 2022-06-21 | Kimex Group s.r.o. | Transmission |
| US11506262B2 (en) * | 2018-09-10 | 2022-11-22 | Valeo Systèmes d'Essuyage | Mechanical reduction gearing and associated geared motor |
| CN108953501A (en) * | 2018-09-19 | 2018-12-07 | 杭州星河传动机械研究院有限公司 | Multi-eccentric speed reducer |
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| Publication number | Publication date |
|---|---|
| CN100414139C (en) | 2008-08-27 |
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Assignee: Science and Technology Branch of Xuzhou Construction Machinery Group Co., Ltd. Assignor: Chongqing University Contract fulfillment period: 2009.1.20 to 2013.1.20 contract change Contract record no.: 2009320000250 Denomination of invention: Planetary balance-wheel speed reducer Granted publication date: 20080827 License type: Exclusive license Record date: 2009.3.6 |
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Free format text: EXCLUSIVE LICENSE; TIME LIMIT OF IMPLEMENTING CONTACT: 2009.1.20 TO 2013.1.20; CHANGE OF CONTRACT Name of requester: JIANGSU AOXIN ROAD NDUSTRY ELECTRICAL APPLIANCES Effective date: 20090306 |
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Granted publication date: 20080827 |