CN102287491B - Vertical type planet gearbox transmission device - Google Patents
Vertical type planet gearbox transmission device Download PDFInfo
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- CN102287491B CN102287491B CN2011102210299A CN201110221029A CN102287491B CN 102287491 B CN102287491 B CN 102287491B CN 2011102210299 A CN2011102210299 A CN 2011102210299A CN 201110221029 A CN201110221029 A CN 201110221029A CN 102287491 B CN102287491 B CN 102287491B
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Abstract
The invention discloses a vertical type planet gearbox transmission device, which comprises a box body, wherein a sun gear, at least two planet gears engaged with the sun gear, internal gear rings engaged with the planet gears, and planet gear shafts and planet carriers which are used for supporting the planet gears are arranged in the box body; and the internal gear rings are connected with the box body through a connecting sleeve. The device is characterized in that: the connecting sleeve is a flexible part; a first end where the connecting sleeve is connected with the internal gear rings is provided with a first internal spline, and a second end where the connecting sleeve is connected with the box body is provided with a second external spline; the internal gear rings are provided with a first external spline matched with the first internal spline; and the box body is provided with a second internal spline matched with the second external spline. The device has a uniform loading effect, high carrying capacity, low noise, high reliability and long service life.
Description
Technical field
The present invention relates to a kind of transmission device, particularly relate to a kind of transmission device of vertical planetary gear box.
Background technique
The vertical type high-power gear-box generally all adopts the straight-tooth planet speed reduction driving mechanism at present, and its equal load system generally adopts sun gear radial floating load balancing mechanism.Along with transmitted power is increasing, even sun gear has adopted load balancing structure, still can cause the load inequality of planet wheel, thereby cause the planet wheel the transshipped life-span greatly to be reduced, thereby reduce the reliability of whole transmission device.
In prior art, vertical type planet gearbox transmission device, comprise casing, in casing, be provided with sun gear, with at least two planet wheels of sun gear engagement, with ring gear, planet wheel shaft and the planet carrier be used to supporting planet wheel of planet wheel engagement, ring gear connects by joint sleeve with casing.In transmission device when work,, ring gear bears comes from planetary impact force, is directly passed to casing by joint sleeve.Therefore in the transmittance process of power, because the power between ring gear and joint sleeve, between joint sleeve and casing is all rigid of transmission, when sun gear and planet wheel transmitted load when inhomogeneous, cause that strength of gear is inhomogeneous, thereby cause the too early damage of some gears in train of gearings, and casing also bears larger impact.
Therefore those skilled in the art are devoted to develop a kind of vertical type planet gearbox transmission device that performance is good that all carries.
Summary of the invention
Because the above-mentioned defect of prior art, technical problem to be solved by this invention is to provide a kind of vertical type planet gearbox transmission device that performance is good that all carries.
For achieving the above object, the invention provides a kind of vertical type planet gearbox transmission device, comprise casing; In described casing, be provided with sun gear, with at least two planet wheels of described sun gear engagement, with ring gear, planet wheel shaft and the planet carrier be used to supporting described planet wheel of described planet wheel engagement; Described ring gear connects by joint sleeve with described casing; Its key is: described joint sleeve is flexible part; The first end that described joint sleeve connects with described ring gear is provided with the first internal spline, and the second end connected with described casing is provided with the second external splines; On described ring gear, be provided with the first external splines coordinated with described the first internal spline; On described casing, be provided with the second internal spline coordinated with described the second external splines.
Because joint sleeve is flexible part, itself and ring gear and casing are splined, therefore make the load be assigned with on planet wheel more even.
For further raising, all carry performance, the key tooth of described the first external splines and the key tooth of described the second external splines are crowned teeth.
For further raising, all carry performance, be provided with circlip groove in described the first internal spline; In described circlip groove, be provided with Steel Cable Baffle Ring; The key tooth of described the first external splines is arranged between described Steel Cable Baffle Ring.
For performance is all carried in further raising, the wall thickness of described ring gear is the whole depth of the gear teeth of 1～2 times of described ring gear and the engagement of described planet wheel.
Preferably, described ring gear is split-type structural, comprises the first ring gear and the second ring gear that overlap up and down; Described the first ring gear and the second ring gear all with described joint sleeve splined; The key tooth of described the first ring gear and the second ring gear all is arranged between described Steel Cable Baffle Ring.
Preferably, the width of described the first ring gear and the second ring gear equates.
Preferably, interior uniform three the described planet wheels that are provided with of described ring gear.
For improving the reliability of transmission device, described sun gear connects with input shaft by the torsion pass spline; Described input shaft is outside equipped with the input axle sleeve; Described input axle sleeve one end is fixedly connected with described casing, and the other end is provided with end cap; Described input shaft is by spaced clutch shaft bearing and the second bearings; Described clutch shaft bearing is arranged on the top of described input shaft, and its bearing outer ring is supported in the input axle sleeve, and bearing inner race is by the described input shaft shaft shoulder and end ring axially locating; Described the second bearing is arranged on the bottom of described input shaft, the step that its bearing outer ring is put by input shaft and with the bolted outer end of described input axle sleeve pressing plate axially locating, bearing inner race by the shaft shoulder on input shaft and with the bolted inner ring pressing plate of described input shaft axially locating.
For further improving the reliability of transmission device, the uniform preloading spring that is provided with between described clutch shaft bearing and described end cap.
Preferably, uniformly between described clutch shaft bearing and described end cap be provided with 8 preloading springs.
The invention has the beneficial effects as follows: effect of load balancing mechanism of the present invention is good, and bearing capacity is high, noise is little, reliability is high, the life-span is long.
The accompanying drawing explanation
Fig. 1 is the structural representation of the embodiment of the invention;
Fig. 2 is the A-A sectional view of Fig. 1;
Fig. 3 is the partial enlarged drawing at I place in Fig. 1;
Fig. 4 is the partial enlarged drawing at II place in Fig. 1;
Fig. 5 is the partial enlarged drawing at III place in Fig. 1;
Fig. 6 is the partial enlarged drawing at IV place in Fig. 1;
Fig. 7 is the shape schematic diagram of the external splines key tooth of ring gear in the embodiment of the invention.
Embodiment
The invention will be further described below in conjunction with drawings and Examples:
Embodiment: as shown in Figures 1 to 7, a kind of vertical composite support epicyclic gearbox transmission device, comprise casing, and casing comprises upper box 24 and lower box 10, and upper box 24 is fixedly connected with by bolt 25 with lower box 10.Upper box 24 and lower box 10 are welded by multi-sheets.In lower box 10, be provided with sun gear 3, three and the planet wheel 4 of sun gear 3 engagements, the ring gear with planet wheel 4 engagements, planet wheel shaft 11 and the planet carrier 7 be used to supporting planet wheel 4.Planet wheel 4 is uniform setting in ring gear.
Ring gear is split-type structural, comprises the first ring gear 51 and the second ring gear 52 that overlap up and down.
The width of the first ring gear 51 and the second ring gear 52 equates.
The first ring gear 51 and the second ring gear 52 are realized flexible the connection by joint sleeve 8 with lower box 10.Wherein, joint sleeve 8 is flexible part.The periphery of the first ring gear 51 and the second ring gear 52 junctions is provided with the first external splines 16, and joint sleeve 8 is provided with the end that the first ring gear 51 and the second ring gear 52 connect the first internal spline 17 coordinated with the first external splines 16.The end that joint sleeve 8 connects with lower box 10 is provided with the second external splines 18, on lower box 10, is provided with the second internal spline 19 coordinated with the second external splines 18.
As shown in Figure 7, the key tooth of the first external splines 16 is crowned teeth, and the key tooth of the second external splines 18 is identical with the key tooth of the first external splines, is all crowned teeth.Therefore, when the first external splines 16 coordinates with the first internal spline 17, can increase the degrees of freedom of the first external splines 16 key teeth, make it produce small relative shift with the key tooth of the first internal spline 17, thereby make the connection between the first ring gear 51 and the second ring gear 52 and joint sleeve 8 more flexible, and then the load that each planet wheel 4 is distributed is more even.In like manner, the connection between joint sleeve 8 and lower box 10 is also more flexible, makes the load of 4 of each planet wheels be more evenly distributed, and makes load less to the impact of lower box 10.
In the present embodiment, the wall thickness of the first ring gear 51 and the second ring gear 52 is 1.5 times of whole depths with the gear teeth of planet wheel 4 engagement, so that the first ring gear 51 and the second ring gear 52 can produce micro-strain when work, namely the first ring gear 51 and the second ring gear 52 float supports are on joint sleeve, thereby each planet wheel load is more evenly distributed.In other embodiments, the wall thickness of the first ring gear 51 and the second ring gear 52 can be also the whole depth of 1～2 times of gear teeth, to reach essentially identical technique effect.
In the first internal spline 17, be provided with circlip groove 14, the crowned teeth that is provided with Steel Cable Baffle Ring 15, the first external spliness 16 in circlip groove 14 is arranged in the circle that Steel Cable Baffle Ring 15 surrounds.Therefore, Steel Cable Baffle Ring 15 can support the first external splines 16, and limits the motion of the first external splines 16 at vertical direction.On the other hand, because the outer surface of Steel Cable Baffle Ring 15 is disc, the face that the first external splines 16 contacts with Steel Cable Baffle Ring 15 is plane, so during transmission device work, can increase the degrees of freedom of the first external splines 16, thereby further make the load of each planet wheel 4 more even.
Sun gear 3 connects with input shaft 1 by torsion pass spline 2, and input shaft 1 is outside equipped with input axle sleeve 20.Input axle sleeve 20 1 ends are fixedly connected with upper box 24, and the other end is provided with end cap 13.
Input shaft 1 is supported by spaced clutch shaft bearing 61 and the second bearing 62.Wherein, clutch shaft bearing 61 is arranged on the top of input shaft 1, and its bearing outer ring is supported in input axle sleeve 20, and bearing inner race is by input shaft 1 shaft shoulder and end ring 22 axially locating; The second bearing 62 is arranged on the bottom of input shaft 1, its bearing outer ring by input the step on axle sleeve 20 and with bolted outer end clamp plate 9 axially locating of input axle sleeve 20, bearing inner race by the shaft shoulder on input shaft 1 and with bolted inner ring pressing plate 21 axially locating of input shaft.Therefore, this bearing structure can bear radial load, can bear thrust load again, can also meet the requirement that vertical type planet gearbox transmission device power is large, the input shaft rotating speed is high simultaneously.
In the present embodiment, uniformly between the bearing outer ring of clutch shaft bearing 61 and end cap 13 be provided with 8 (only illustrating two in figure) preloading springs 23.In other embodiments, those skilled in the art, according to the thrust load of clutch shaft bearing 61 suffered minimums and the pretightening force of preloading spring, can obtain by conventionally calculation the quantity that preloading spring arranges.Due to the setting of preloading spring, therefore effectively avoided skidding between clutch shaft bearing 61 rollers and raceway, thereby improved the operational safety of bearing and gear-box.
During this transmission device work, moment of torsion is from input shaft 1 input, through torsion pass spline 2, transfer torque on sun gear 3, by sun gear 2, moment of torsion is assigned on each planet wheel 4 uniformly, planet wheel 4 and the first ring gear 51 and the second ring gear 5 engagements, also rotate planet wheel around sun gear 3 except rotation; Planet wheel 4 transfers torque to planet carrier 7 through planet wheel shaft 11, by planet carrier 7 and output shaft 12, moment of torsion is exported.
More than describe preferred embodiment of the present invention in detail.Should be appreciated that those of ordinary skill in the art just can design according to the present invention make many modifications and variations without creative work.Therefore, all technician in the art, all should be in the determined protection domain by claims under this invention's idea on the basis of existing technology by the available technological scheme of logical analysis, reasoning, or a limited experiment.
Claims (9)
1. a vertical type planet gearbox transmission device, comprise casing (10,24); In described casing (10,24), be provided with sun gear (3), with at least two planet wheels (4) of described sun gear (3) engagement, with ring gear (51,52), planet wheel shaft (11) and the planet carrier (7) be used to supporting described planet wheel (4) of described planet wheel (4) engagement; Described ring gear (51,52) connects by joint sleeve (8) with described casing (10); It is characterized in that: described joint sleeve (8) is flexible part; The first end that described joint sleeve (8) connects with described ring gear is provided with the first internal spline (17), and the second end connected with described casing (10) is provided with the second external splines (18); On described ring gear (51,52), be provided with the first external splines (16) coordinated with described the first internal spline (17); On described casing (10), be provided with the second internal spline (19) coordinated with described the second external splines (18); Described sun gear (3) connects with input shaft (1) by torsion pass spline (2); Described input shaft (1) is outside equipped with input axle sleeve (20); Described input axle sleeve (20) one ends are fixedly connected with described casing (24), and the other end is provided with end cap (13); Described input shaft (1) is supported by spaced clutch shaft bearing (61) and the second bearing (62); Described clutch shaft bearing (61) is arranged on the top of described input shaft (1), and its bearing outer ring is supported in input axle sleeve (20), and bearing inner race is by described input shaft (1) shaft shoulder and end ring (22) axially locating; Described the second bearing (62) is arranged on the bottom of described input shaft (1), its bearing outer ring by the step in input axle sleeve (20) and with the bolted outer end clamp plate of described input axle sleeve (20) (9) axially locating, bearing inner race by the shaft shoulder on input shaft (1) and with the bolted inner ring pressing plate of described input shaft (21) axially locating.
2. vertical type planet gearbox transmission device as claimed in claim 1, it is characterized in that: the key tooth of described the first external splines (16) and described the second external splines (18) is crowned teeth.
3. vertical type planet gearbox transmission device as claimed in claim 1, is characterized in that: in described the first internal spline (17), be provided with circlip groove (14); In described circlip groove (14), be provided with Steel Cable Baffle Ring (15); The key tooth of described the first external splines (16) is arranged between described Steel Cable Baffle Ring (15).
4. vertical type planet gearbox transmission device as claimed in claim 1 is characterized in that: the wall thickness of described ring gear (51,52) is 1～2 times of described ring gear (51,52) and the whole depth of the gear teeth of described planet wheel (4) engagement.
5. vertical type planet gearbox transmission device as claimed in claim 3, it is characterized in that: described ring gear is split-type structural, comprises the first ring gear (51) and the second ring gear (52) that overlap up and down; Described the first ring gear (51) and the second ring gear (52) all with described joint sleeve (8) splined; The key tooth of described the first ring gear (51) and the second ring gear (52) all is arranged between described Steel Cable Baffle Ring (15).
6. vertical type planet gearbox transmission device as claimed in claim 5 is characterized in that: the width of described the first ring gear (51) and the second ring gear (52) equates.
7. as claim 1,4 or 5 described vertical type planet gearbox transmission devices, it is characterized in that: uniform three the described planet wheels (4) that are provided with in described ring gear (51,52).
8. vertical type planet gearbox transmission device as claimed in claim 1, is characterized in that: the uniform preloading spring (23) that is provided with between described clutch shaft bearing (61) and described end cap (13).
9. vertical type planet gearbox transmission device as claimed in claim 8, is characterized in that: uniform 8 preloading springs (23) that are provided with between the bearing outer ring of described clutch shaft bearing (61) and described end cap (13).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011102210299A CN102287491B (en) | 2011-08-03 | 2011-08-03 | Vertical type planet gearbox transmission device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011102210299A CN102287491B (en) | 2011-08-03 | 2011-08-03 | Vertical type planet gearbox transmission device |
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| Publication Number | Publication Date |
|---|---|
| CN102287491A CN102287491A (en) | 2011-12-21 |
| CN102287491B true CN102287491B (en) | 2013-11-27 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2011102210299A Active CN102287491B (en) | 2011-08-03 | 2011-08-03 | Vertical type planet gearbox transmission device |
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| CN (1) | CN102287491B (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105134918A (en) * | 2015-06-09 | 2015-12-09 | 孙美娜 | Deep groove ball bearings of integrated planet wheel reduction gear |
| CN108412963A (en) * | 2018-05-15 | 2018-08-17 | 湘潭大学 | A kind of big torque actuated and high thrust load integrated device |
| CN108412970B (en) * | 2018-05-25 | 2018-09-25 | 上海奥托克动力系统有限公司 | vertical gearbox |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1687616A (en) * | 2005-04-29 | 2005-10-26 | 清华大学 | Vertical type high speed gear reducer |
| CN201301933Y (en) * | 2008-11-14 | 2009-09-02 | 南京高精齿轮集团有限公司 | Upright herringbone tooth planetary reducer |
| CN101761633A (en) * | 2008-12-11 | 2010-06-30 | 天津市正平机械新技术有限公司 | Four-stage driving combined type speed reducer and speed reduction method thereof |
| CN101846156A (en) * | 2010-03-01 | 2010-09-29 | 吴声震 | Vertical and high-speed quasi-planetary reduction gearbox for nuclear generation |
| CN202170968U (en) * | 2011-08-03 | 2012-03-21 | 重庆齿轮箱有限责任公司 | Vertical planetary gear box transmission device |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60157550A (en) * | 1984-01-28 | 1985-08-17 | Hitachi Constr Mach Co Ltd | Reduction gear |
| JP2008133849A (en) * | 2006-11-27 | 2008-06-12 | Toyota Motor Corp | Positioning structure of thrust bearing |
-
2011
- 2011-08-03 CN CN2011102210299A patent/CN102287491B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1687616A (en) * | 2005-04-29 | 2005-10-26 | 清华大学 | Vertical type high speed gear reducer |
| CN201301933Y (en) * | 2008-11-14 | 2009-09-02 | 南京高精齿轮集团有限公司 | Upright herringbone tooth planetary reducer |
| CN101761633A (en) * | 2008-12-11 | 2010-06-30 | 天津市正平机械新技术有限公司 | Four-stage driving combined type speed reducer and speed reduction method thereof |
| CN101846156A (en) * | 2010-03-01 | 2010-09-29 | 吴声震 | Vertical and high-speed quasi-planetary reduction gearbox for nuclear generation |
| CN202170968U (en) * | 2011-08-03 | 2012-03-21 | 重庆齿轮箱有限责任公司 | Vertical planetary gear box transmission device |
Non-Patent Citations (2)
| Title |
|---|
| JP昭60-157550A 1985.08.17 |
| JP特开2008-133849A 2008.06.12 |
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| CN102287491A (en) | 2011-12-21 |
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