CN204553712U - A kind of retarder for lifting of ocean platform device - Google Patents
A kind of retarder for lifting of ocean platform device Download PDFInfo
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- CN204553712U CN204553712U CN201520191147.3U CN201520191147U CN204553712U CN 204553712 U CN204553712 U CN 204553712U CN 201520191147 U CN201520191147 U CN 201520191147U CN 204553712 U CN204553712 U CN 204553712U
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- gear
- retarder
- external gear
- lifting
- planetary
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Abstract
The utility model provides a kind of retarder for lifting of ocean platform device, and comprise planetary gear mechanisms for two stages and one-level involute less tooth difference gear mechanism, first order planetary gears comprises central gear, planetary pinion and ring gear; Second level planetary gears comprises central gear and planetary pinion, and involute less tooth difference gear mechanism comprises eccentric shaft, external gear and inner tooth shell, and eccentric shaft and planetary pinion connect firmly, and power is reached external gear; External gear is under the acting in conjunction of eccentric shaft and inner tooth shell, while revolve round the sun around inner tooth shell axis, while around the reverse rotation of own axes, and through planet carrier, the spinning motion of external gear is reached output shaft gear, can be used for lifting of ocean platform device and other require in the transmission of big speed ratio, high pulling torque.
Description
Technical field
The utility model relates to a kind of retarder, is specifically related to a kind of retarder that can be used for lifting of ocean platform device.
Background technique
The lifting of ocean platform gear-box of current extensive use, three grades or level Four NGW type planetary gears or two-stage planet are mostly adopted to add three grades of parallel-axes gears mechanism compositions, this gear mechanism application is very general, is widely used in the transmissions such as wind-powered electricity generation, boats and ships, automobile.But in the transmission device that velocity ratio is very large, its physical dimension and quality comparation large.Because each lifting of ocean platform device at least needs tens such gear-boxes, thus very high to the power density requirements of gear-box.
Model utility content
The utility model object is to provide a kind of retarder for lifting of ocean platform device.
For achieving the above object, the utility model have employed following technological scheme.
Comprise output shaft gear, power input shaft, retarder subelement and first planet gear mechanism, described retarder subelement comprises reduction case, second planetary gears, involute planetary gear gear mechanism and planet carrier, planet carrier is by being arranged at the large bearing supporting of planet carrier in reduction case, described involute planetary gear gear mechanism comprises external gear, inner tooth shell and eccentric shaft, inner tooth shell is fixed on reduction case, the internal tooth engaged with external gear is provided with in inner tooth shell, the planetary pinion of eccentric shaft and the second planetary gears connects firmly, the eccentric part of eccentric shaft is connected by eccentric part bearing with external gear, eccentric shaft is by being arranged at the eccentric shaft bearing supporting on planet carrier, one end of power input shaft is connected with the central gear of the second planetary gears, the other end is connected with the clutch end of first planet gear mechanism, output shaft gear is connected with planet carrier.
The planetary number of first, second planetary gears described is 2 ~ 4.
Described eccentric shaft is configured with two eccentric parts, the phase difference of two eccentric parts is 180 degree.
Described involute planetary gear gear mechanism comprises two panels external gear, and two panels external gear is connected with corresponding eccentric part respectively by the eccentric part bearing be arranged on eccentric part.
The profile of tooth of described external gear and internal tooth is through the involute of the thinning correction of the flank shape of tooth top, and it is 0.01 ~ 0.05mm that tooth top repaiies thin amount.
The addendum coefficient of described external gear and internal tooth is 0.5 ~ 0.8.
The number of teeth difference of described external gear and inner tooth shell is 1 ~ 4.
The beneficial effects of the utility model are embodied in:
The kind of drive that retarder for lifting of ocean platform device described in the utility model adopts planetary gear mechanisms for two stages in parallel with one-level involute planetary gear gear mechanism, by arranging primary planet pinion mechanism at the input end of retarder subelement, its gear range is increased to hundreds of to several thousand by tens to hundreds of, minimum amount of parts and the lightest quality is in turn ensure that while realizing big speed ratio, there is the advantages such as compact structure, significantly can alleviate the volume of gear-box, and improve specific power, reduce costs.
Accompanying drawing explanation
Fig. 1 is structural representation of the present utility model;
Fig. 2 is the B-B sectional view of Fig. 1;
Fig. 3 is the C-C sectional view of Fig. 1;
In figure: 1 is inner tooth shell, 2 is internal tooth, and 3 is planet carrier, and 4 is power input shaft, and 5 is eccentric shaft, 5a, 5b are eccentric part, and 6 is eccentric part bearing, and 7a, 7b are external gear, gear centered by 8,9 is planetary pinion, and 10 is the large bearing of planet carrier, and 11 is eccentric shaft bearing, and 12 is output shaft gear.
Embodiment
Below in conjunction with accompanying drawing, the utility model is elaborated.
See Fig. 1, Fig. 2 and Fig. 3, retarder for lifting of ocean platform device described in the utility model comprises output shaft gear 12, power input shaft 4, retarder subelement and first planet gear mechanism, described retarder subelement comprises reduction case, second planetary gears, involute planetary gear gear mechanism and planet carrier 3, first planet gear mechanism comprises central gear, the planetary pinion engaged with central gear and the ring gear engaged with planetary pinion, the planetary pinion that second planetary gears comprises central gear and engages with central gear, planet carrier 3 is supported by the large bearing 10 of planet carrier be arranged in reduction case, described involute planetary gear gear mechanism comprises external gear, inner tooth shell 1 and eccentric shaft 5, inner tooth shell 1 is fixed on reduction case, the internal tooth 2 engaged with external gear is provided with in inner tooth shell 1, the planetary pinion 9 of eccentric shaft 5 and the second planetary gears connects firmly, the eccentric part of eccentric shaft is connected by eccentric part bearing 6 with external gear, eccentric shaft is supported by the eccentric shaft bearing 11 be arranged on planet carrier 3, one end of power input shaft 4 is connected with the central gear 8 of the second planetary gears, the other end is connected with the clutch end of first planet gear mechanism, output shaft gear 12 is connected with planet carrier 3.
The number of the planetary pinion 9 of first, second planetary gears described is 2 ~ 4.
Described eccentric shaft 5 is configured with two eccentric parts 5a, 5b, the phase difference of two eccentric parts is 180 degree.Described involute planetary gear gear mechanism comprises two panels external gear 7a, 7b, and two panels external gear 7a, 7b are connected with corresponding eccentric part respectively by the eccentric part bearing 6 be arranged on eccentric part 5a, 5b.The profile of tooth of described external gear 7a, 7b and internal tooth 2 is through the involute of the thinning correction of the flank shape of tooth top, and it is 0.01 ~ 0.05mm that tooth top repaiies thin amount.The addendum coefficient of described external gear 7a, 7b and internal tooth 2 is 0.5 ~ 0.8.The number of teeth difference of described external gear 7a, 7b and inner tooth shell 1 is 1 ~ 4.
Power inputs from the central gear 8 of described second planetary gears, reaches described external gear, then reaches planet carrier 3 by external gear 7a, 7b through eccentric shaft 5, pass to output shaft gear finally by planet carrier through described planetary pinion 9 and eccentric shaft 5.Described external gear 7a, 7b eccentric part also around eccentric shaft 5 while engaging with internal tooth 2 turns round, under the acting in conjunction of internal tooth 2 and eccentric part 5a, 5b, its spinning motion around the reverse rotation of own axes, and to be exported by output shaft gear through planet carrier 3 by external gear while the revolution of inner tooth shell 1 axis.
Embodiment
See Fig. 1, Fig. 2 and Fig. 3, retarder described in the utility model comprises primary planet pinion mechanism and one-level involute planetary gear gear mechanism, described planetary gears comprises central gear and planetary pinion, involute planetary gear gear mechanism comprises external gear 7a, 7b, inner tooth shell 1 and the eccentric shaft 5 rotated integrally with the planetary pinion 9 of described primary planet pinion mechanism, inner tooth shell is fixed on reduction case, the internal tooth 2 engaged with external gear is provided with in inner tooth shell 1, planetary pinion 9 and the described eccentric shaft 5 of described primary planet pinion mechanism connect firmly, power inputs from the central gear 8 of described primary planet pinion mechanism, described external gear is reached through described planetary pinion 9 and eccentric shaft 5, output shaft gear 12 is reached through planet carrier 3 again by external gear.
Described primary planet pinion mechanism comprises the central gear 8 rotated integrally with power input shaft 4 and the planetary pinion 9 engaged with described central gear.
The number of the planetary pinion 9 of described primary planet pinion mechanism is 3.
Described eccentric shaft is configured with two eccentric parts 5a, 5b, the phase difference of two eccentric parts is 180 degree.
Described involute planetary gear gear mechanism comprises two panels external gear 7a, 7b, and external gear 7a, 7b are coordinated with corresponding eccentric part respectively by the eccentric part bearing 6 be arranged on eccentric part 5a, 5b, are rotatably supported by eccentric part.
Described external gear 7a, 7b eccentric part also around eccentric shaft 5 while engaging with internal tooth 2 turns round, under the acting in conjunction of internal tooth 2 and eccentric part 5a, 5b, external gear around inner tooth shell 1 axis revolution while around the reverse rotation of own axes, after planetary differential motion, the spinning motion of external gear is exported from output shaft by planet carrier 3.
The profile of tooth of described external gear 7a, 7b and internal tooth 2 is through the involute of the thinning correction of the flank shape of tooth top.Different according to module, tooth top is repaiied thin amount and is about 0.01 ~ 0.05mm.
The addendum coefficient of described external gear 7a, 7b and internal tooth 2 is 0.5 ~ 0.8.The phenomenons such as involute interference, radial loading interference and profile overlap interference can be avoided like this.
The number of teeth difference of described external gear 7a, 7b and inner tooth shell is 1 ~ 4, can meet different transmissions when requirement of strength.
Be furnished with eccentric shaft bearing 11 between described eccentric shaft 5 and planet carrier 3, eccentric shaft is rotatably supported by eccentric shaft bearing 11 by planet carrier.
Be furnished with the large bearing 10 of planet carrier between described planet carrier 3 and reduction case, planet carrier is rotatably supported by the large bearing 10 of planet carrier by reduction case.
Power is inputted by central gear 8, the eccentric shaft 5 that warp and planetary pinion 9 connect firmly reaches external gear, under the driving of the eccentric shaft connected firmly with planetary pinion, external gear makes plane rocking by the active force of inner tooth shell, both revolved round the sun around inner tooth shell axis, again around the reverse rotation of own axes, and the spinning motion of external gear is exported through planet carrier.Gear range is tens to hundreds of, if input end adds one-level dotted portion planetary gears, its gear range can from hundreds of to several thousand.
Retarder described in the utility model has that amount of parts is few, velocity ratio is large, compact structure, the advantages such as transmitting torque is large, can be widely used in, in the high transmission device of big speed ratio, high pulling torque, power density requirements, can be used for lifting of ocean platform device.
Claims (7)
1. the retarder for lifting of ocean platform device, it is characterized in that: comprise output shaft gear (12), power input shaft (4), retarder subelement and first planet gear mechanism, described retarder subelement comprises reduction case, second planetary gears, involute planetary gear gear mechanism and planet carrier (3), planet carrier (3) is by being arranged at the large bearing of planet carrier (10) supporting in reduction case, described involute planetary gear gear mechanism comprises external gear, inner tooth shell (1) and eccentric shaft (5), inner tooth shell (1) is fixed on reduction case, the internal tooth (2) engaged with external gear is provided with in inner tooth shell (1), eccentric shaft (5) connects firmly with the planetary pinion (9) of the second planetary gears, the eccentric part of eccentric shaft is connected by eccentric part bearing (6) with external gear, eccentric shaft is by being arranged at eccentric shaft bearing (11) supporting on planet carrier (3), one end of power input shaft (4) is connected with the central gear (8) of the second planetary gears, the other end is connected with the clutch end of first planet gear mechanism, output shaft gear (12) is connected with planet carrier (3).
2. a kind of retarder for lifting of ocean platform device according to claim 1, is characterized in that: the number of the planetary pinion (9) of first, second planetary gears described is 2 ~ 4.
3. a kind of retarder for lifting of ocean platform device according to claim 1, it is characterized in that: described eccentric shaft (5) is configured with two eccentric parts, the phase difference of two eccentric parts is 180 degree.
4. a kind of retarder for lifting of ocean platform device according to claim 3, it is characterized in that: described involute planetary gear gear mechanism comprises two panels external gear, two panels external gear is connected with corresponding eccentric part respectively by the eccentric part bearing (6) be arranged on eccentric part.
5. a kind of retarder for lifting of ocean platform device according to claim 1, is characterized in that: the profile of tooth of described external gear and internal tooth (2) is through the involute of the thinning correction of the flank shape of tooth top, and it is 0.01 ~ 0.05mm that tooth top repaiies thin amount.
6. a kind of retarder for lifting of ocean platform device according to claim 1, is characterized in that: the addendum coefficient of described external gear and internal tooth (2) is 0.5 ~ 0.8.
7. a kind of retarder for lifting of ocean platform device according to claim 1, is characterized in that: the number of teeth difference of described external gear and inner tooth shell (1) is 1 ~ 4.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520191147.3U CN204553712U (en) | 2015-03-31 | 2015-03-31 | A kind of retarder for lifting of ocean platform device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520191147.3U CN204553712U (en) | 2015-03-31 | 2015-03-31 | A kind of retarder for lifting of ocean platform device |
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| Publication Number | Publication Date |
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| CN204553712U true CN204553712U (en) | 2015-08-12 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201520191147.3U Active CN204553712U (en) | 2015-03-31 | 2015-03-31 | A kind of retarder for lifting of ocean platform device |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105369792A (en) * | 2015-11-02 | 2016-03-02 | 武汉船用机械有限责任公司 | Speed reducing device of gear-and-rack type lifting system and gear-and-rack type lifting system |
| CN105697664A (en) * | 2016-04-22 | 2016-06-22 | 重庆齿轮箱有限责任公司 | Gear transmission mechanism and lifting gearbox |
| CN109780149A (en) * | 2019-03-13 | 2019-05-21 | 吉林大学 | A kind of speed change gear based on small teeth number difference planet gear |
-
2015
- 2015-03-31 CN CN201520191147.3U patent/CN204553712U/en active Active
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105369792A (en) * | 2015-11-02 | 2016-03-02 | 武汉船用机械有限责任公司 | Speed reducing device of gear-and-rack type lifting system and gear-and-rack type lifting system |
| CN105369792B (en) * | 2015-11-02 | 2017-08-08 | 武汉船用机械有限责任公司 | The deceleration device and pinion and-rack jacking system of pinion and-rack jacking system |
| CN105697664A (en) * | 2016-04-22 | 2016-06-22 | 重庆齿轮箱有限责任公司 | Gear transmission mechanism and lifting gearbox |
| CN109780149A (en) * | 2019-03-13 | 2019-05-21 | 吉林大学 | A kind of speed change gear based on small teeth number difference planet gear |
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