CN102748460A - Secondary box structure of planet wheel system of speed changing box - Google Patents
Secondary box structure of planet wheel system of speed changing box Download PDFInfo
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- CN102748460A CN102748460A CN2012102425134A CN201210242513A CN102748460A CN 102748460 A CN102748460 A CN 102748460A CN 2012102425134 A CN2012102425134 A CN 2012102425134A CN 201210242513 A CN201210242513 A CN 201210242513A CN 102748460 A CN102748460 A CN 102748460A
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- planet wheel
- gear train
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Abstract
The invention provides a secondary box structure of a planet wheel system of a speed changing box. According to the technical scheme, the secondary box structure comprises a oblique-tooth planet wheel system of a secondary box and a secondary box synchronizer, wherein the secondary box synchronizer is located in front of the planet wheel system. The secondary box structure of the planet wheel system of the speed changing box has the beneficial effects that the structure is simple and the design is reasonable; the secondary box synchronizer is located in front of the planet wheel system, so that the length of an output shaft of a planet frame is shortened, and the stressing condition of the output shaft is improved; and the planet wheel system adopts oblique teeth to improve the bearing capability of a gear.
Description
Technical field
The present invention is a kind of gearbox planetary gear train odd-side structure.
Background technique
In the common heavy type lorry transmission-gear box structure; Gear diameter on two jack shaft range of structures shelves odd-side jack shafts differs greatly; Its life-span can be mutually far short of what is expected; Another shortcoming is that the power to housing that two jack shaft structures produce increases along with the increase of input torque, and therefore for the gearbox of high pulling torque, the possibility of gearbox cracking is big.
The odd-side of planetary structure has utilized the characteristics of planetary structure gear radial force for internal force, and is very little to the power of housing, and simultaneously, when odd-side was in top grade, planetary structure integral body was rotated around the axle center, and this moment, the transmission efficiency of planetary mechanism was high.To sum up, use gearbox for the heavy truck of high pulling torque, the odd-side planetary gear train is a kind of scheme preferably.
Traditional scope shelves odd-side planetary gear train is positioned at before the scope shelves synchronizer, because the planetary gear train characteristic, the scope shelves are when high or low shelves, and planet carrier output shaft part all bears than high pulling torque.By synchronizer ring bracket and connected to the planetary gear train, the ring gear mounting constraints, high cone synchronizer valley section with the output shaft connected to the carrier at the smaller diameter.When the transmission input torque higher than the rated input torque, especially in sub-box high-grade status, carrier output shaft section and upscale joints prone valleys cone distortion, or even rupture.Therefore, the high pulling torque gearbox is under the prerequisite that keeps planetary gear train, and the torque condition of optimization planet carrier when the high and low shelves of scope shelves improves the planet carrier twisting strength, is a problem that urgently needs solution.
Summary of the invention
The present invention is directed to the deficiency of existing technology; Provide a kind of simple in structure; Reasonable in design; Can make the high pulling torque gearbox under the prerequisite that keeps planetary gear train, optimize the torque condition of planet carrier when the high and low shelves of scope shelves, improve the technological scheme of the gearbox planetary gear train odd-side structure of planet carrier twisting strength.
The present invention realizes through following technical measures: a kind of gearbox planetary gear train odd-side structure, comprise odd-side planetary gear train, odd-side synchronizer, and said odd-side synchronizer is positioned at before the said planetary gear train.
Further improvement of the present invention there is, including the sub-box synchronization synchronizer gear sets, synchronous tooth Block, upscale cone valleys, the synchronization gear sleeve and the inner ring gear spline bushing twisting through the mass connected to the transmission torque spline bushing spline-coupled to the ring gear mounted on the inner-tooth by tooth top circle axially positioning the wire ring, the inner ring wall of the right processing, the ring gear left and right torsion rely pass spline sleeve and stopper side of the planet wheel axial limit; installed in the high valleys cone carrier on the front, with high-grade grain carrier cone spline joints front diameter increased, the synchronization gear seat through the needle bearing mounted on the planet carrier front, the synchronization gear seat mounted on the planet carrier to rely on the front of the front and rear bracket axial positioning.
Further improvement of the present invention also has, and above-mentioned odd-side planetary gear train adopts the helical teeth structure.
Further improvement of the present invention also has; Above-mentioned odd-side planetary gear train comprises output shaft, sun gear, the planet wheel that is connected with main shaft, said main shaft and output shaft axial limiting sun gear, the spacing planet wheel of sun gear; The spacing ring gear of planet wheel, the axial force of helical teeth planetary gear train is in internal balance.
Further improvement of the present invention also has, and spline catch and jump ring are installed in above-mentioned sun gear two ends, and there are the gap in planet wheel and planet carrier both ends of the surface, by sun gear axial limiting planet wheel, the adjustment pad is installed between sun gear and main shaft; Torsion pass spline housing external splines is installed on the ring gear, the processing of ring gear right side rib, ring gear left and right dependence torsion pass spline housing and rib axial limiting on planet wheel.
Further improvement of the present invention also has, and above-mentioned planet carrier is anterior, the rear portion is provided with supporting structure.
The beneficial effects of the present invention are: sub-box using helical planetary gear train, the sub tank planetary gear synchronizer placed before the shortened carrier output shaft lengths to improve the force output shaft; canceled ring stand, synchronous toothed sleeve and ring gear spline bushing twisting through the mass is connected; upscale cone mounted on the planet carrier grains on the front, with high-grade grain carrier cone spline joints front diameter increased, improving the state of the planet carrier grade the force; synchronization gear seat through needle bearing mounted on the front of the carrier synchronizer gear seat mounting flanges on both sides; sun gear installed at both ends of spline blank with the retainer, the planetary wheel ends with the planet carrier surface gaps , to limit the planet from the sun wheel axle, mounted between the sun gear and spindle shims; biography twisted spline sleeve, splined to the inner ring, the inner ring on the right processing ribs, internal gear left and right Splined rely pass twisted wall of the planet wheel with an axial stop; Planetary axial positioning of the relationship: the axial shaft and the output shaft limit sun wheel, the sun wheel stop planetary gear, planetary gear limit ring gear, helical planetary gear train so the axial force internal balance; front and rear portions of the carrier is provided with a support structure, the vehicle can be reduced around the double support of the transmission factor of the internal working to improve sub- Box life.
Description of drawings
Fig. 1 is traditional scope shelves odd-side planetary gear train structural representation.
Fig. 2 is the structural representation of the specific embodiment of the invention.
In the figure, a spindle, two, front bracket, 3, needle roller bearings, four, Deputy box synchronizer, 5, synchronous gear sets, 6, after the blank, 7, upscale Cone Valley, 8, pass twisted splines sets, 9, the ring gear 10, planetary gear 11, planetary gear train 12, the sun gear 13, the output shaft 14, a carrier 15, the spline bracket 16, retainer 17, a carrier front, 18, synchronous tooth Block, 19, shims, 20, wire ring, 21, ring gear bracket.
Embodiment
For clearly demonstrating the technical characterstic of this programme, through an embodiment, this programme is set forth below.
As illustrated in A planetary gear transmission sub-box structure, including the sub-box planetary gear train, Deputy box synchronizer, Deputy box planetary gear train 11 Bevel, improve gearbox bearing capacity and a significant reduction gearbox Noise assembly; the sub tank 4 is placed in synchronous planetary gear train 11, before reducing the planet carrier 14 is the length of the output shaft 13, reducing the high torque planetary carrier 14 when the output shaft 13 of torsion; eliminating the conventional structure of the ring gear holder 21, the synchronization gear sleeve 5 and the ring gear 9 through the mass twisted spline bushing 8 is connected; upscale Cone Valley 7 installed in front of the planet carrier 17, in grade 7 and the planet carrier cone valleys front 17 flowers key to increase the diameter of joints, improve planetary gear train 11 in the upscale state, the planet carrier 14 of the stress state; synchronization gear seat 18 through needle bearing 3 mounted on the front of the carrier 17, the synchronization gear seat 18 mounted on the planet rely on front frame portion 17 before and after the axial positioning bracket 2,6; sun wheel 12, both ends of the spline bracket 15 and the retainer 16, the planet wheel 10, the left and right end surfaces of the planetary carrier 14 there is a gap, by the sun axial stop planetary wheel 12 wheel 10; sun wheel 12 and a shaft installation and adjustment spacers 19, about 12, respectively, depend on the sun wheel shaft 1 and the output shaft 13 axially; pass twisted spline bushing 8 is spline-coupled mounting the inner ring 9, relying on internal tooth ring gear 9 with the top wire ring 20 axially positioned within the right side of the ring gear 9 processing ribs, the inner ring 9 left and right to rely on mass twisted spline bushing 8 and wall 10 axially on the planet wheel stopper; planetary gear train 11 in the axial direction positional relationship is: the output shaft 1 and the sun gear shaft 13, the axial stop 12, the sun wheel 12, planet wheel 10 stop, the planet wheel 10 is limited to bit internal ring gear 9.Wherein, planet carrier 14 Front-end Design support, and planet carrier 14 forward and backward dual-grippers can reduce the influence of car load factor to the odd-side proper functioning, improve the odd-side life-span.
Above-mentioned odd-side structure also can be used for the straight-tooth planetary gear train.
The present invention can pass through or adopt existing techniques in realizing without the technical characteristics of describing; Repeat no more at this; Certainly, above-mentioned explanation is not to be limitation of the present invention, and the present invention also is not limited in above-mentioned giving an example; Variation, remodeling, interpolation or replacement that those skilled in the art are made in essential scope of the present invention also should belong to protection scope of the present invention.
Claims (6)
1. a gearbox planetary gear train odd-side structure comprises odd-side planetary gear train, odd-side synchronizer, it is characterized in that said odd-side synchronizer is positioned at before the said planetary gear train.
(2) according to claim 1, wherein the transmission planetary gear sub-box structure, characterized in that said auxiliary tank including synchronization synchronizer gear sets, synchronous tooth Block, upscale cone valleys, the synchronization gear sleeve and the inner ring through the mass twisted spline bushing connected set of the transfer torque spline mounted on the spline-coupled to the ring gear, through the internal gear teeth of the top circle of the wire ring axial positioning of the inner ring wall of the right processing , ring gear left and right to rely on mass twisted spline bushing with axial ribs on the planet wheel stopper; installed in the high valleys cone carrier on the front, with high-grade grain carrier cone spline joints front diameter increased, the synchronization gear seat through a needle bearing mounted on the front of the carrier, the synchronization gear seat mounted on the planet carrier to rely on the front of the front and rear bracket axial positioning.
3. gearbox planetary gear train odd-side structure according to claim 1 and 2 is characterized in that, said odd-side planetary gear train adopts the helical teeth structure.
4. gearbox planetary gear train odd-side structure according to claim 1 and 2; It is characterized in that; Said odd-side planetary gear train comprises output shaft, sun gear, the planet wheel that is connected with main shaft, said main shaft and output shaft axial limiting sun gear, the spacing planet wheel of sun gear; The spacing ring gear of planet wheel, the axial force of helical teeth planetary gear train is in internal balance.
5. gearbox planetary gear train odd-side structure according to claim 4; It is characterized in that spline catch and jump ring are installed in said sun gear two ends, there are the gap in planet wheel and planet carrier both ends of the surface; By sun gear axial limiting planet wheel, the adjustment pad is installed between sun gear and main shaft; Torsion pass spline housing external splines is installed on the ring gear, the processing of ring gear right side rib, ring gear left and right dependence torsion pass spline housing and rib axial limiting on planet wheel.
6. gearbox planetary gear train odd-side structure according to claim 2 is characterized in that, said planet carrier is anterior, the rear portion is provided with supporting structure.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2012102425134A CN102748460A (en) | 2012-07-13 | 2012-07-13 | Secondary box structure of planet wheel system of speed changing box |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2012102425134A CN102748460A (en) | 2012-07-13 | 2012-07-13 | Secondary box structure of planet wheel system of speed changing box |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN102748460A true CN102748460A (en) | 2012-10-24 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2012102425134A Pending CN102748460A (en) | 2012-07-13 | 2012-07-13 | Secondary box structure of planet wheel system of speed changing box |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104373562A (en) * | 2014-11-24 | 2015-02-25 | 中国地质大学（武汉） | Lubricating planet wheel gearbox secondary box |
| CN104500705A (en) * | 2014-11-24 | 2015-04-08 | 中国地质大学（武汉） | Sub-gearbox for planetary gear train of transmission |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60151461A (en) * | 1983-12-06 | 1985-08-09 | アー ベー ボルボ | Range gear box for automobile |
| US4976671A (en) * | 1982-06-07 | 1990-12-11 | Ab Volvo | Range gearbox for motor vehicles |
| WO1996020358A1 (en) * | 1994-12-28 | 1996-07-04 | Scania Cv Aktiebolag | Planetary gearing |
| CN101120188A (en) * | 2003-01-14 | 2008-02-06 | 沃尔沃拉斯特瓦格纳公司 | Gearbox for motor vehicles |
| CN201802841U (en) * | 2010-03-27 | 2011-04-20 | 浙江长泰机械有限公司 | Medium-sized automobile transmission with main box and secondary box |
| CN202659872U (en) * | 2012-07-13 | 2013-01-09 | 中国重汽集团济南动力有限公司 | Secondary box structure of transmission planetary gear train |
-
2012
- 2012-07-13 CN CN2012102425134A patent/CN102748460A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4976671A (en) * | 1982-06-07 | 1990-12-11 | Ab Volvo | Range gearbox for motor vehicles |
| JPS60151461A (en) * | 1983-12-06 | 1985-08-09 | アー ベー ボルボ | Range gear box for automobile |
| WO1996020358A1 (en) * | 1994-12-28 | 1996-07-04 | Scania Cv Aktiebolag | Planetary gearing |
| CN101120188A (en) * | 2003-01-14 | 2008-02-06 | 沃尔沃拉斯特瓦格纳公司 | Gearbox for motor vehicles |
| CN201802841U (en) * | 2010-03-27 | 2011-04-20 | 浙江长泰机械有限公司 | Medium-sized automobile transmission with main box and secondary box |
| CN202659872U (en) * | 2012-07-13 | 2013-01-09 | 中国重汽集团济南动力有限公司 | Secondary box structure of transmission planetary gear train |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104373562A (en) * | 2014-11-24 | 2015-02-25 | 中国地质大学（武汉） | Lubricating planet wheel gearbox secondary box |
| CN104500705A (en) * | 2014-11-24 | 2015-04-08 | 中国地质大学（武汉） | Sub-gearbox for planetary gear train of transmission |
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Application publication date: 20121024 |