CN201934590U - Differential planetary power distribution reduction gear - Google Patents
Differential planetary power distribution reduction gear Download PDFInfo
- Publication number
- CN201934590U CN201934590U CN201120000840XU CN201120000840U CN201934590U CN 201934590 U CN201934590 U CN 201934590U CN 201120000840X U CN201120000840X U CN 201120000840XU CN 201120000840 U CN201120000840 U CN 201120000840U CN 201934590 U CN201934590 U CN 201934590U
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- gear
- transmission
- shaft
- output
- differential
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Abstract
The utility model relates to a reduction gear, which comprises an input shaft, an output shaft and a speed reduction gear cluster which is arranged between the input shaft and the output shaft, and is characterized in that: the speed reduction gear cluster comprises a differential planetary device and two paths of parallel gear transmission groups, the differential planetary device comprises a central gear and a differential gear ring, which are coaxial with each other, and a planetary gear which is simultaneously engaged with the central gear and the differential gear ring, the input shaft is connected with the central gear, the two paths of gear transmission groups are respectively connected with the planetary gear and the differential gear ring in a driving way, the output shaft is also provided with an output shaft large gear, and the transmission ends of the two paths of gear transmission groups are simultaneously engaged with the output shaft large gear. The differential planetary device is adopted to be matched with two paths of distribution speed reduction transmission, so the transmission ratio is large.
Description
Technical field
The utility model relates to a kind of speed reducer, particularly a kind of differential planetary power dividing speed reducer that many power transfer routes are arranged between input end and output terminal.
Technical background
Speed reducer is as a kind of driving mechanism that reduces a rotating speed, be widely used in industry, the power of traditional speed reducer is generally the single line transmission, the whole moment of torsion of load all in full everywhere in the transmission, to the requirement of strength height of transmission part, and can't reach higher reduction speed ratio.
CN2913732Y patent as Patent Office of the People's Republic of China's bulletin on June 20th, 2007, name is called gear reduction unit, this device comprises casing and the movable supporting main drive shaft on casing, intermediate propeller shaft and passive transmission shaft, casing is bolted to connection end cap, one master gear is installed on the main drive shaft, install one on the intermediate propeller shaft by gear and two master gears, install two on the passive transmission shaft by gear, one master gear is meshed by gear with one, two master gears are meshed by gear with two, it is characterized in that: a master gear and is that 2, two master gears and two are the double circular arc tooth of modulus 3.5 by gear by the modulus of gear.This device adopts the single line transmission by the gearing down realization speed reducer output shaft of two-stage gear and the deceleration between the input shaft, to the requirement of strength height of middle driving gear and intermediate propeller shaft, and can't reach higher reduction speed ratio.
Summary of the invention
The purpose of this utility model be at the transmission of traditional speed reducer single line to middle transmission part requirement of strength height, can't reach the problem of higher reduction speed ratio, the differential planetary power dividing speed reducer of a kind of reduction speed ratio height, power dividing transmission is provided.
The technological scheme that its technical problem that solves the utility model adopts is: a kind of differential planetary power dividing speed reducer, comprise input shaft, output shaft and be arranged at input shaft and output shaft between train of reduction gears, described train of reduction gears comprises the gear transmission group that differential planetary device and two-way are parallel mutually, described differential planetary device comprises the planet wheel that coaxial sun gear and differential gear ring and while and sun gear and differential gear ring mesh, input shaft links to each other with sun gear, two-way gear transmission group is connected transmission with planet wheel with differential gear ring respectively, also be provided with the output shaft gearwheel on the output shaft, the driven end of two-way gear transmission group meshes with the output shaft gearwheel simultaneously.At first obtain bigger reduction speed ratio by the differential planetary device, drive two-way gear transmission group respectively by planet wheel and differential gear ring then and carry out gearing down, the power of single channel gear transmission group transmission has only half of total output in the transmission process, the gear transmission load is little, impact to the gear transmission group is little, therefore gear-driven centre distance has been dwindled, requirement of strength to the gear transmission group under the situation of transmitting equal-wattage reduces, saved manufactured materials greatly, reduced speed reducer and made difficulty.Two-way gear transmission group has guaranteed the whole output power of output shaft in the end by same output shaft output.
As preferably, the transmission sum of series velocity ratio of described two-way gear transmission group is identical.Guarantee the synchronism of two-way gear transmission group.
As preferably, the described gear transmission group that is connected transmission with planet wheel has first transmission shaft and second transmission shaft that is respectively equipped with input gear and output gear, input gear on first transmission shaft is connected by internal tooth casing with planet wheel, input gear engagement on the output gear on first transmission shaft and second transmission shaft, the output gear of second transmission shaft and the engagement of output shaft gearwheel.
As preferably, the gear transmission group that described and differential gear ring is connected transmission has first transmission shaft and second transmission shaft that is respectively equipped with input gear and output gear, input gear on first transmission shaft and the engagement of the external toothing of differential gear ring, input gear engagement on the output gear on first transmission shaft and second transmission shaft, the output gear of second transmission shaft and the engagement of output shaft gearwheel.The rotating speed that is delivered on first transmission shaft by planet wheel is identical with the rotating speed that is delivered to first transmission shaft by differential gear ring.
As preferably, described output shaft gearwheel is a herringbone tooth.Avoided output shaft to be subjected to axial impact when herringbone tooth can effectively increase transmission intensity, same, with the output gear of second transmission shaft of output shaft gearwheel engagement also be herringbone tooth.
As preferably, described output shaft gearwheel is formed by the opposite helical gear combination of both direction.
As preferably, the output gear of described second transmission shaft is formed by the opposite helical gear combination of both direction.
As preferably, between the output gear of described second transmission shaft and second transmission shaft, all be adopted as socket between output shaft gearwheel and the output shaft and install, make that the Gear Processing difficulty reduces, more compact structure, the speed reducer volume is littler.
As preferably, described input shaft adopts the tooth cover that floats to be connected with sun gear.It is reliable that this structure has transmitting movement, the advantage that the decentraction compensation ability is good.
The utility model adopts the differential planetary device to cooperate the gearing down of two-way shunting, when increasing reduction speed ratio, transmitted power is shunted, reduced impact to the gear transmission group, under the situation of same power, manufactured materials can be saved, under the situation of same intensity, maximum transmission power can be increased; Adopt herringbone tooth transmission output, axial impact is little, operates steadily the reliability height.
Description of drawings
Fig. 1 is a kind of structural representation of the utility model.
Fig. 2 is the structural representation of the utility model differential planetary device.
Fig. 3 is a transmission sketch of the present utility model.
Among the figure: 1. input shaft, tooth cover, 3. differential planetary device 2. float, 4. first transmission shaft, 5. first transmission shaft input gear, the 6. first transmission shaft output gear, 7. second transmission shaft, 8. second transmission shaft input gear, the 9. second transmission shaft output gear, 10. output shaft, 11. the output shaft gearwheel, 12. sun gears, 13. planet wheels, 14. differential gear ring, 15. internal tooth casings.
Embodiment
Also in conjunction with the accompanying drawings the utility model is further specified below by specific embodiment.
Embodiment: a kind of differential planetary power dividing speed reducer, as shown in Figure 1 to Figure 3.This device comprises an input shaft 1 and an output shaft 10, the gear transmission group gearing down that walks abreast by differential planetary device 3 and two-way between input shaft 1 and the output shaft 10.Input shaft 1 connects with the sun gear 12 of differential planetary device 3 by the tooth cover 2 of floating, differential planetary device 3 also comprises differential gear ring 14 and planet wheel 13, differential gear ring 14 and sun gear 12 arranged concentric, planet wheel 13 meshes with differential gear ring 14 and sun gear 12 between differential gear ring 14 and sun gear 12 and simultaneously, and planet wheel 13 rotates and rotations around sun gear 12.Planet wheel 13 drives the transmission of left road gear transmission group by internal tooth casing 15, and differential gear ring 14 drives the transmission of right side gear transmission group, and two-way gear transmission group transmission progression is identical, and the velocity ratio of every grade of transmission is identical.Two-way gear transmission group all has first transmission shaft 4 and second transmission shaft 7 of difference tape input gear and output gear.Left side road gear transmission group drive connection is as follows, connect internal tooth casing 15 by bearing on planet wheel 13 axis, internal tooth casing 15 is imported gear 5 engagements with first transmission shaft on first transmission shaft 4 and is connected, the first transmission shaft output gear 6 and 8 engagements of second transmission shaft input gear, the output gear 9 of second transmission shaft and 11 engagements of the output shaft gearwheel on the output shaft 10.Right wing gear transmission group drive connection is as follows: the external tooth of differential gear ring 14 and 5 engagements of first transmission shaft input gear, the first transmission shaft output gear 6 and 8 engagements of second transmission shaft input gear, the output gear 9 of second transmission shaft and 11 engagements of the output shaft gearwheel on the output shaft 10.Two groups of gear transmission groups at last with transmission of power to same output shaft 10.The output gear 9 of second transmission shaft and output shaft gearwheel 11 be the herringbone tooth gear for being made up of the opposite helical gear of both direction all, and output gear 9 and output shaft gearwheel 11 adopt sleeve structure to be installed on second transmission shaft 7, the output shaft 10.
The gearing down of this device can further specify with following example, motor speed is 600rpm, power input to a machine is delivered to input shaft 1, input shaft is connected with sun gear 12 in the differential planetary device 3 by floating buss 2, the reduction speed ratio 8.2039 of differential planetary device 3, promptly rotating speed of motor is dropped to 73.14rpm from 600rpm, simultaneously the power transmission is divided into two the tunnel, left side road is that planet wheel 13 drives first transmission shaft 4, engagement by the first transmission shaft output gear 6 and second transmission shaft input gear 8 drives 7 rotations of second transmission shaft, reduction speed ratio 4.5217, promptly rotating speed drops to 16.18rpm from 73.14rpm; Right wing is that differential gear ring 14 drives first transmission shaft 4, engagement by the first transmission shaft output gear 6 and second transmission shaft input gear 8 drives 7 rotations of second transmission shaft, equally also rotating speed is dropped to 16.18rpm from 73.14rpm, drive output shaft 10 rotations by the second transmission shaft output gear 9 of two-way and the engagement of output shaft gearwheel 11 at last, reduction speed ratio 3.375, promptly rotating speed drops to 4.794rpm from 16.18rpm.Realized the gearing down process of resultant gear ratio 125.2.
It is streamed that this device adopts differential planetary to divide, and load distribution evenly reduces strength demand, and velocity ratio is big, adopts the synthetic output of herringbone gear, and transmitting torque is big, effectively avoids the impulsive load of squeezer.
Claims (10)
1. differential planetary power dividing speed reducer, comprise input shaft, output shaft and be arranged at input shaft and output shaft between train of reduction gears, it is characterized in that: described train of reduction gears comprises the gear transmission group that differential planetary device and two-way are parallel mutually, described differential planetary device comprises the planet wheel that coaxial sun gear and differential gear ring and while and sun gear and differential gear ring mesh, input shaft links to each other with sun gear, two-way gear transmission group is connected transmission with planet wheel with differential gear ring respectively, also be provided with the output shaft gearwheel on the output shaft, the driven end of two-way gear transmission group meshes with the output shaft gearwheel simultaneously.
2. differential planetary power dividing speed reducer according to claim 1 is characterized in that: the transmission sum of series velocity ratio of described two-way gear transmission group is identical.
3. differential planetary power dividing speed reducer according to claim 2, it is characterized in that: the described gear transmission group that is connected transmission with planet wheel has first transmission shaft and second transmission shaft that is respectively equipped with input gear and output gear, input gear on first transmission shaft is connected by internal tooth casing with planet wheel, input gear engagement on the output gear on first transmission shaft and second transmission shaft, the output gear of second transmission shaft and the engagement of output shaft gearwheel.
4. according to claim 1 or 2 or 3 described differential planetary power dividing speed reducers, it is characterized in that: the gear transmission group that described and differential gear ring is connected transmission has first transmission shaft and second transmission shaft that is respectively equipped with input gear and output gear, input gear on first transmission shaft and the engagement of the external toothing of differential gear ring, input gear engagement on the output gear on first transmission shaft and second transmission shaft, the output gear of second transmission shaft and the engagement of output shaft gearwheel.
5. according to claim 1 or 2 or 3 described differential planetary power dividing speed reducers, it is characterized in that: described output shaft gearwheel is a herringbone tooth.
6. differential planetary power dividing speed reducer according to claim 4 is characterized in that: described output shaft gearwheel is a herringbone tooth, with the output gear of second transmission shaft of output shaft gearwheel engagement also be herringbone tooth.
7. differential planetary power dividing speed reducer according to claim 6 is characterized in that: described output shaft gearwheel is formed by the opposite helical gear combination of both direction.
8. differential planetary power dividing speed reducer according to claim 6 is characterized in that: the output gear of described second transmission shaft is formed by the opposite helical gear combination of both direction.
9. differential planetary power dividing speed reducer according to claim 6 is characterized in that: between the output gear of described second transmission shaft and second transmission shaft, all be adopted as socket between output shaft gearwheel and the output shaft and install.
10. according to claim 1 or 2 or 3 described differential planetary power dividing speed reducers, it is characterized in that: described input shaft adopts the tooth cover that floats to be connected with sun gear.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201120000840XU CN201934590U (en) | 2011-01-04 | 2011-01-04 | Differential planetary power distribution reduction gear |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201120000840XU CN201934590U (en) | 2011-01-04 | 2011-01-04 | Differential planetary power distribution reduction gear |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201934590U true CN201934590U (en) | 2011-08-17 |
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ID=44446109
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201120000840XU Expired - Fee Related CN201934590U (en) | 2011-01-04 | 2011-01-04 | Differential planetary power distribution reduction gear |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN201934590U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105987149A (en) * | 2016-07-14 | 2016-10-05 | 江阴齿轮箱制造有限公司 | Closed differential transmission structure system and power dividing method thereof |
| CN109681586A (en) * | 2019-01-18 | 2019-04-26 | 天津工业大学 | A kind of curved tooth double helical tooth planetary differential gearing system that can actively adjust the speed |
-
2011
- 2011-01-04 CN CN201120000840XU patent/CN201934590U/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105987149A (en) * | 2016-07-14 | 2016-10-05 | 江阴齿轮箱制造有限公司 | Closed differential transmission structure system and power dividing method thereof |
| CN109681586A (en) * | 2019-01-18 | 2019-04-26 | 天津工业大学 | A kind of curved tooth double helical tooth planetary differential gearing system that can actively adjust the speed |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20110817 Termination date: 20170104 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |