CN2818917Y

CN2818917Y - Planetary gearbox

Info

Publication number: CN2818917Y
Application number: CNU2005200396274U
Authority: CN
Inventors: 吴士刚; 陈宝明; 陈文杰; 孙学仁
Original assignee: Shanghai Pengpu Juli Engineering Machinery Co Ltd
Current assignee: Shanghai Pengpu Juli Engineering Machinery Co Ltd
Priority date: 2005-02-07
Filing date: 2005-02-07
Publication date: 2006-09-20
Anticipated expiration: 2015-02-07

Abstract

The utility model relates to a planetary gear gearbox which belongs to the technical field of planetary gear gearboxes for hydraulic transmission bulldozers. The utility model comprises components of a first group of planetary gear mechanism and a second group of planetary gear mechanism, such as clutches, clutch gear rings, planet carrier gears with planet carriers, planetary gears and central gears, wherein the first central gear and the second central gear are coaxial and are all power input gears. The first planet carrier gear which is provided with the first planet carrier is engaged with the first clutch gear ring; the planet carrier of the first planet carrier gear is provided with the first planetary gear which is respectively engaged with the first central gear and a common gear ring; the second planet carrier gear which is provided with the second planet carrier is engaged with the common gear ring; the planet carrier of the second planet carrier gear is provided with the second planetary gear which is respectively engaged with the second central gear and the second clutch gear ring; the second planet carrier gear which is provided with the second planet carrier is a power output gear.

Description

Planetary transmission

Technical field

The utility model relates to the gear graduation box technology, particularly a kind of hydraudynamic drive bulldozer planetary transmission technology.

Background technique

The working principle of at present domestic 165～180 horsepowers hydraudynamic drive formula bulldozer usefulness planetary transmission and structure are as shown in Figure 1.It advances and the direction conversion that retreats realizes by three groups of planetary gear constructions.First clutch 1 is used to advance, and second clutch 3 is used to retreat.The action principle of first group of planetary gears and second group of planetary gears and structure as shown in Figure 2, the third line star gear mechanism is a dual planetary gear mechanism, its action principle and structure are as shown in Figure 3.

It is constant to set the 3rd sun gear (power input gear) 14 dextrorotation veers;

When retreating, the outer tooth plate 4 of second clutch 3 compresses the internal gear 2 of second clutch 3, second gear ring 11 is fixed, then according to Fig. 1 and Fig. 2, second planet carrier 12 is rotated counterclockwise, and power transmits downwards, in this case, the engagement of three second planetary pinions 6 of second planet row and second gear ring 11, the third line star are arranged between six the third

line star gears

13,15 and with the engagement of second gear ring 11 and the 3rd sun gear 14 power loss are arranged all respectively.

When advancing, first clutch 1 compresses, and first gear ring 10 is fixed, because first planet carrier 5 is fixed, first planetary pinion 7 meshes with first gear ring 10 and first sun gear 8 respectively, so first sun gear 8 also is fixed motionless.So because second sun gear 9 and first sun gear 8 are coaxially also to be fixed.Second planet row is because second sun gear 9 is fixed, and second gear ring 11 and second planet carrier 12 are defined and can only rotate in the same way.As can see from Figure 1, second planet row and the third line star are arranged shared one second gear ring 11 and second planet carrier 12.The third line star row determines under the right handed situation that at the 3rd sun gear 14 second planet carrier 12 can only rotate by clockwise direction, thereby realizes turning to because second gear ring 11 and second planet carrier 12 are defined and can only rotate in the same way.In this case, with to retreat situation the same, the engagement of three planetary pinions 6 of second planet row and first gear ring 11, the third line star is arranged between six the third

line star gears

13,15 and with the engagement of second gear ring 11 and the 3rd sun gear 14 power loss is arranged all respectively.

From as can be seen above-mentioned, the gearbox transmission link of this driving type is many, and efficient is low.Simultaneously, use the dual planetary gear transmission as can be seen from Figure 3, physical dimension is big and complicated.

The model utility content

At the shortcoming that exists in the above-mentioned prior art, technical problem to be solved in the utility model provides a kind of function of direction conversion that can realize and reduces transmission link again, reduces the planetary transmission of energy loss.

In order to solve the problems of the technologies described above, according to a kind of planetary transmission provided by the utility model, it comprises I clutch, I clutch gear ring, I planetary pinion and the I sun gear of I group planetary gear mechanism, II clutch, II clutch gear ring, II planetary pinion, II sun gear and the shared gear ring of II group planetary gear mechanism; Also comprise I planet carrier gear that is provided with the I planet carrier and the II planet carrier gear that is provided with the II planet carrier, wherein I sun gear and II sun gear are coaxial, are power input gear; Be provided with the I planet carrier gear and the engagement of I clutch gear ring of I planet carrier, the planet carrier of I planet carrier gear is provided with the I planetary pinion, the I planetary pinion meshes with I sun gear and shared gear ring respectively, be provided with the II planet carrier gear and the engagement of shared gear ring of II planet carrier, the planet carrier of II planet carrier gear is provided with the II planetary pinion, and the II planetary pinion meshes with II sun gear and II clutch gear ring respectively; The II planet carrier gear that is provided with the II planet carrier is a power output gear;

When retreating, the I clutch compresses, I clutch gear ring is fixed motionless, the I planet carrier is fixed, the I sun gear turns clockwise, drive shared gear ring by the I planetary pinion and counterclockwise rotate, shared gear ring drives II planet carrier gear and counterclockwise rotates, by the downward transferring power of II planet carrier gear;

When advancing, the II clutch compresses, and II clutch gear ring is fixed motionless, and the II sun gear turns clockwise, and drives II planet carrier gear by the II planetary pinion and turns clockwise, by the downward outputting power of II planet carrier gear.

The planetary transmission of the utility model design, owing to adopted the planet carrier gear that is provided with planet carrier, make it advance only to have adopted and realize by the two groups of epicyclic gears structure with the direction that retreats conversion, be dual planetary gear driving mechanism of no use, also lacked one group of planetary gear mechanism, so its transmission be succinct, physical dimension is little, transmission link is few, and energy loss is few, the transmission efficiency height.

Description of drawings

Fig. 1 is the structural principle schematic representation of the planetary transmission that the hydraudynamic drive formula is pushed to machine in the prior art.

Fig. 2 is the working principle schematic representation of fixed gear ring in the planetary gear mechanism.

Fig. 3 is the working principle schematic representation of fixed gear ring in the dual planetary gear driving mechanism.

Fig. 4 is the structural principle schematic representation of planetary transmission among the utility model embodiment.

Fig. 5 is the working principle schematic representation of fixed carrier in the planetary gear mechanism.

Embodiment

Below in conjunction with description of drawings enforcement of the present utility model is described in further detail, but present embodiment is not limited to the utility model, every employing analog structure of the present utility model and similar variation thereof all should be listed the novel protection domain of this enforcement in.

Referring to shown in Figure 4, in embodiment of the present utility model, the planetary transmission that is provided, it comprise I clutch 27, I clutch gear ring 31, the I planet carrier gear 32 that is provided with the I planet carrier, I planetary pinion 37 and I sun gear 38, the II group planetary gear mechanism of I group planetary gear mechanism II clutch 29, II clutch gear ring 34, be provided with II planet carrier gear 36, II planetary pinion 35, II sun gear 39 and the shared gear ring 33 of II planet carrier; Wherein I sun gear 38 and II sun gear 39 are coaxial, are power input gear; Be provided with the I

planet carrier gear

32 and 31 engagements of I clutch gear ring of I planet carrier, the planet carrier of I planet carrier gear 32 is provided with I planetary pinion 37, I planetary pinion 37 meshes with I sun gear 38 and shared gear ring 33 respectively, be provided with the II planet carrier gear 36 and shared gear ring 33 engagements of II planet carrier, the planet carrier of II planet carrier gear 36 is provided with II planetary pinion 35, the II planetary pinions 35 and meshes with II sun gear 39 and II clutch gear ring 34 respectively; The II planet carrier gear 36 that is provided with the II planet carrier is power output gear;

When retreating, I clutch 27 compresses, I clutch gear ring 31 is fixed motionless, the planet carrier of I planet carrier gear 32 is fixed, I sun gear 38 turns clockwise, drive the rotation counterclockwise of shared gear ring 33 by I planetary pinion 37, shared gear ring 33 drives II planet carrier gear 36 rotation counterclockwise, by II planet carrier gear 36 downward transferring power;

When advancing, the outer tooth plate 30 of II clutch 29 compresses the internal gear 28 of II clutch, II clutch gear ring 34 is fixed motionless, II sun gear 39 turns clockwise, drive II planet carrier gear 36 by II planetary pinion 35 and turn clockwise, by II planet carrier gear 36 downward outputting powers.

Referring to shown in Figure 2, when clutch gear ring 17 was fixed, sun gear 20 turned clockwise, and drove the rotation of planet carrier (or planet carrier gear) 18 clockwise directions by planetary pinion 19.

Referring to shown in Figure 3, in the dual planetary gear driving mechanism, when clutch gear ring 21 was fixed, sun gear 23 turned clockwise, and drove planet carrier 22 rotation counterclockwise by inner planet gear 24 and exterior epicyclic gear 25.

Referring to shown in Figure 5, when planet carrier (or planet carrier gear) 43 was fixed, sun gear 44 turned clockwise, and drove gear ring (comprising clutch gear ring, shared gear ring) 42 rotation counterclockwise by planetary pinion 41.

In the present embodiment, clutch is the hydraulic coupling that is provided with piston.

In addition, on the basis of the foregoing description, to one of ordinary skill in the art, the utility model still can be done many variations.

Claims

1, a kind of planetary transmission, it comprises I clutch, I clutch gear ring, I planetary pinion and the I sun gear of I group planetary gear mechanism, II clutch, II clutch gear ring, II planetary pinion, II sun gear and the shared gear ring of II group planetary gear mechanism; It is characterized in that also comprise I planet carrier gear that is provided with the I planet carrier and the II planet carrier gear that is provided with the II planet carrier, wherein I sun gear and II sun gear are coaxial, are power input gear; Be provided with the I planet carrier gear and the engagement of I clutch gear ring of I planet carrier, the planet carrier of I planet carrier gear is provided with the I planetary pinion, the I planetary pinion meshes with I sun gear and shared gear ring respectively, be provided with the II planet carrier gear and the engagement of shared gear ring of II planet carrier, the planet carrier of II planet carrier gear is provided with the II planetary pinion, and the II planetary pinion meshes with II sun gear and II clutch gear ring respectively; The II planet carrier gear that is provided with the II planet carrier is a power output gear.

2, planetary transmission according to claim 1 is characterized in that, described clutch is the hydraulic coupling that is provided with piston.