CN201559525U - Drive axle with double driven gears - Google Patents
Drive axle with double driven gears Download PDFInfo
- Publication number
- CN201559525U CN201559525U CN 200920181113 CN200920181113U CN201559525U CN 201559525 U CN201559525 U CN 201559525U CN 200920181113 CN200920181113 CN 200920181113 CN 200920181113 U CN200920181113 U CN 200920181113U CN 201559525 U CN201559525 U CN 201559525U
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- Prior art keywords
- axle
- gear
- conical gear
- drive axle
- passive
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
- F16H1/20—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members
- F16H1/22—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
- F16H1/222—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with non-parallel axes
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Retarders (AREA)
Abstract
A drive axle with double driven gears can lead output torsion moment of a single-level speed reducing drive axle to exceed the domestic existing highest level and to achieve 60000N M. The technical scheme includes that left and right speed reducing double-curved-surface bevel gear pairs which parallel independently drive left and right wheels, and a differential function of the drive axle is completed via a front-end differential mechanism, thereby effectively avoiding contradiction that strengths of driving gears, driven gears, planet gears and half axle gears for present domestic single-level speed reducing heavy vehicle axles can not meet design requirements in terms of structural design. Left and right driven bevel gears are arranged oppositely and respectively rotate leftwards and rightwards, thereby being capable of effectively eliminating relatively large axial force, reducing load of bearings, and effectively saving space so as to lead arrangement of parts to be more compact. The drive axle can be widely used for a heavy automobile driven by a single rear axle and a cross-country vehicle, and has functions of increasing trafficability, improving mechanical efficiency and reducing energy consumption.
Description
[technical field]
The utility model relate to a kind of be used on the heavy motor vehicle and cross country car on, output torque reaches the above singl-reduction axle of 60000Nm, more specifically to a kind of pair of ring gear drive axle.
[background technology]
Drive axle is one of important symbol of heavy motor vehicle, its basic structure has following three kinds: central singl-reduction axle, central twin-stage drive axle, central single-stage, hub reduction drive axle, central authorities' singl-reduction axle is a kind of in the drive axle structure, be the base model of drive axle, in autotruck, occupy an leading position.At present, domestic output torque is in the singl-reduction axle of 45000-55000Nm, comprise that the east wind moral receives 508, high pulling torque singl-reduction axles such as 498 of liberation, be subjected to the restriction of material technology, thermal treatment process technology, quality is stable not enough, and the productive costs height fails to obtain the market approval.
On the present at home market, central authorities' twin-stage drive axle mainly contains two types: a class such as Eton series of products, just in single reduction gear, reserved in advance the space, when requiring increasing traction and speed ratio, the cylindrical planetary gear speed reduction gearing of can packing into slows down former central single-stage and makes central dual-ratio reduction drive axle into, this transformation of the way " three change " degree height, axle housing, main reduction gear etc. all can be general, and the bevel gear diameter is constant; Another kind of as Rockwell's series of products, when wanting increasing traction and speed ratio, after needing transformation of the way first order bevel gear, reinstall second stage spur gear wheel or helical wheel, become the central dual-ratio reduction drive axle of requirement, at this moment axle housing can be general, main reduction gear is not general, basin corner gear exceeds certain numerical value or traction total mass when big because above-mentioned central dual-ratio reduction bridge all is speed ratios at central single-stage bridge, a kind of model that derives from as series of products, they are difficult to be modified to front driving axle, use to be subjected to certain limitation.Therefore, comprehensive, the dual-ratio reduction bridge does not generally all develop as a kind of basical traditional model drive axle, but the drive axle that derives from as a certain special consideration exists, and the dual-ratio reduction drive axle exists, and mechanical efficiency is low, energy loss is big, complex structure, the defective of cost height and maintenance convenience difference.
[utility model content]
The utility model is in order to overcome the difficult problem that existing high pulling torque single-stage reduction axle moment of torsion is not enough and existing dual-ratio reduction bridge efficient is low, energy consumption is big, a kind of pair of ring gear drive axle is provided, this drive axle is with a kind of brand new structure design, make it can under the condition of current material technology, thermal treatment process technology, satisfy the above requirement of output torque 60000Nm, and can replace highway with the dual-ratio reduction drive axle of using on the heavy motor vehicle (single rear-axle drive vehicle), to reach the purpose that improves mechanical efficiency, minimizing energy consumption.
The technical solution of the utility model is: two ring gear drive axles, comprise preposition diff, described diff is the open type diff, before comprising, half-rear axle gear and four planetary wheels, two pairs of deceleration hyperboloidal bevel gear sets arranged side by side about being provided with in the described drive axle, every pair of described deceleration hyperboloidal bevel gear set comprises initiatively conical gear and passive conical gear, the half front axle gear of described diff is connected with right initiatively conical gear by spline, described right initiatively conical gear and right passive conical gear are pair of meshing conical gear pair, the passive conical gear in the described right side is captiveed joint with the drive axle right axle sleeve, and described drive axle right axle sleeve is connected with the automobile back wheel right axle shaft by spline;
The half-rear axle gear of described diff is connected with an active cylindrical wheel by spline, and described active cylindrical wheel and a passive cylindrical wheel constitute cylindrical gear pair, and described passive cylindrical wheel is connected with left side active conical gear by spline; A described left side initiatively conical gear and left passive conical gear be another to the pitch cone gear pair, the passive conical gear in a described left side is captiveed joint with the drive axle left axle sleeve, described drive axle left axle sleeve is connected with the automobile back wheel left half axle by spline.
As from the foregoing, the passive conical gear that in drive axle described in the utility model, has two separate rotations, left and right passive conical gear is direct individual drive left and right half respectively, so just remedied the heavy vehicle bridge of design the deficiency that planetary side gear intensity can not meet design requirement from structure.
The utility model feature is that also described left and right passive conical gear employing is arranged on the same axis dorsad, and adopts left-handed and dextrorotation respectively.Can offset bigger axial force like this and make compact conformation; Preposition diff is finished differential function and can be remedied the parts gap, makes the synchronous all the time stressed operation of left and right sides conical gear.
The utility model feature is that also the right-hand component of left and right passive conical gear bolster and described drive axle right axle sleeve adopt interference fit, and the left-hand component of described bolster adopts grommet to be connected with described drive axle left axle sleeve.Be exactly as a whole connecting into of bolster, right axle sleeve and right passive conical gear rigidity like this, the left-hand component of described bolster adopts grommet to be connected with described drive axle left axle sleeve.Can relatively rotate between left so passive conical gear and the bolster.This structure design has not only satisfied the non-uniform movement of left and right wheel, goes back actv. and has reduced amount of parts and improved the stability of parts work.
The utility model feature also is in the middle of the described left and right passive conical gear annular anti-attrition packing ring to be housed, and is fixed on the passive conical gear in the described right side with straight pin, limit radial movement, and by the motion of bearing pre-fastening restrictive axial.Guaranteed the mutual slip of the passive conical gear in the described left and right sides so on the one hand, can satisfy matching requirements by actv. on the other hand, and can guarantee that the passive conical gear in the left and right sides of automobile requires motion according to road conditions.
Principle of work of the present utility model is: this drive axle adopts two passive conical gears individual drive left and right wheels respectively, and the differential function of drive axle is finished by preposition diff.Referring to Fig. 1, input torque is realized torque distribution by diff 3 earlier, part moment of torsion is through half front axle gear 1 → right initiatively conical gear 5 → right passive conical gear 8 → right axle shaft 7 → right wheel 6, and another part moment of torsion process half-rear axle gear 2 → a pair of cylindrical gear pair 4 → left side is conical gear 12 → left passive conical gear 9 → left half axle 10 → left wheel 11 initiatively.Because two pairs of separate deceleration hyperboloidal bevel gear sets about having, so axle reduction, increase the function of turning round and also be achieved.Wherein a pair of cylindrical gear pair construction parameter is identical, so they are transfer torque and do not carry out speed change.
The beneficial effects of the utility model are, can the output torque that have central single-stage reduction axle now is double, if the output torque of certain central single-stage reduction axle is 30000Nm, adopt the output torque of two ring gear drive axles of same model can reach 60000Nm so, and can not diminish the ground Clearance.This drive axle can be widely used on the heavy motor vehicle of single rear-axle drive and on the cross country car, can play to improve trafficability, improve mechanical efficiency, the effect that cuts down the consumption of energy.
[description of drawings]
The utility model will be further described in conjunction with the embodiments with reference to the accompanying drawings.
Fig. 1 is a fundamental diagram of the present utility model,
Fig. 2 is two ring gear structural representations,
Fig. 3 is the structural representation of the utility model diff,
Fig. 4 is an integral structure scheme drawing of the present utility model.
Among the figure: 1 is the half front axle gear, and 2 is the half-rear axle gear, and 3 is diff, 4 is cylindrical gear pair, and 5 is right initiatively conical gear, and 6 is right wheel, 7 is right axle shaft, and 8 is right passive conical gear, and 9 is left passive conical gear, 10 is left half axle, and 11 is left wheel, and 12 is initiatively conical gear of a left side, 13 is right axle sleeve, and 14 is bolster, and 15 are the anti-attrition packing ring, 16 is grommet, and 17 is left axle sleeve.
[specific embodiment]
Referring to accompanying drawing 1,2,3,4, two ring gear drive axles, comprise preposition diff 3, described diff 3 is the open type diff, comprise half front axle gear 1, half-rear axle gear 2 and four planetary wheels, two pairs of deceleration hyperboloidal bevel gear sets arranged side by side about being provided with in the described drive axle, every pair of described deceleration hyperboloidal bevel gear set comprises initiatively conical gear and passive conical gear, the half front axle gear 1 of diff 3 is connected with right initiatively conical gear 5 by spline, right initiatively conical gear 5 is a pair of meshing conical gear pair with right passive conical gear 8, right passive conical gear 8 passes through bolted connection with drive axle right axle sleeve 13, described drive axle right axle sleeve 14 is connected with automobile back wheel right axle shaft 7 by spline, and right axle shaft 7 is rigidly connected with right wheel 6.
The half-rear axle gear 2 of diff 3 is connected with active cylindrical wheel 4 by spline, and described active cylindrical wheel 4 constitutes cylindrical gear pair with passive cylindrical wheel 4 ' engagement, and described passive cylindrical wheel 4 ' is connected with left side active conical gear 12 by spline; A left side initiatively conical gear 12 is that another is to the pitch cone gear pair with left passive conical gear 9, the passive conical gear 9 in a left side passes through bolted connection with drive axle left axle sleeve 17, drive axle left axle sleeve 17 is connected with automobile back wheel left half axle 10 by spline, and left half axle 10 is rigidly connected with left wheel 11.
Moment of torsion by the driving engine input passes to diff 3 through flange, and diff is given half front axle gear 1 and half-rear axle gear 2 by center cross and planetary wheel with the moment of torsion mean allocation; Half front axle gear 1 passes to right initiatively conical gear 5 by spline with moment of torsion, and the deceleration of the right conical gear pair of process increases to be turned round, and moment of torsion passes to right axle sleeve 13 through right ring gear 8 and bolt, and right axle sleeve 13 passes to right axle shaft 7 with moment of torsion, drives right wheel 6 and rotates.
In like manner, half-rear axle gear 2 passes to cylindrical gear pair 4,4 ' by spline with moment of torsion, cylindrical gear pair 4,4 ' passes to initiatively conical gear 12 of a left side by spline with moment of torsion again, the deceleration of the left conical gear pair of process increases to be turned round, passive conical gear 9 and bolt pass to left axle sleeve 17 to moment of torsion through a left side, left axle sleeve 17 is connected with left half axle 10 by spline, and left axle sleeve 17 passes to left half axle 10 with moment of torsion, drives left wheel 11 and rotates.
In Fig. 1, we as can be seen main reduction gear form by preposition diff 3, a pair of cylindrical wheel 4,4 ' and two pair of hyperboloidal bevel gear set, cylindrical wheel has only the function of carry-over moment, not having to slow down increases the function of turning round, so the basic specification of active cylindrical wheel 4 and passive cylindrical wheel 4 ' is all identical.The basic specification of two pairs of double curved surface conical gears is also identical, is the rotation direction difference of each profile of tooth, and right initiatively conical gear 5 selects left-handed, and then right passive conical gear 8 is dextrorotation, and left side active conical gear 12 is dextrorotation, and then left passive conical gear 9 is left-handed.
In Fig. 1, we are left half axle 10 and left passive conical gear 9, right axle shaft 7 and right passive conical gear 8 direct connections as can be seen.When designing the drive axle of output torque 50000Nm as the principle of design by existing single-stage drive axle, planetary side gear need reach the load bearing requirements of 25000Nm, and passive conical gear need satisfy the load bearing requirements of 50000Nm.And by the principle of design of two ring gear drive axles, two pairs of passive conical gears drive left and right sides semiaxis respectively, each passive conical gear just only needs the load of carrying 25000Nm like this, and diff be arranged in slow down increase turn round before, the moment of torsion that planetary side gear is born is 25000Nm/i (i is a reduction ratio), and the moment of torsion that axle side gear bears when i=5 only is 5000Nm.
We find from top analysis, design the drive axle of identical output torque, and by the principle of design of two ring gear drive axles, the load bearing requirements of passive conical gear has only 1/2 of the passive conical gear carrying of ordinary single-stage reduction axle; The load bearing requirements of planetary side gear is the 1/i (i is a reduction ratio) of ordinary single-stage deceleration bridge planetary side gear carrying.We can know that two ring gear drive axles reduce greatly to the requirement of the strength of gear teeth thus, make to produce output torque 60000Nm and above singl-reduction axle becomes feasible under the prior art condition.
In Fig. 2, we are the right-hand component and the right axle sleeve 13 employing interference fit of the bolster 14 of left and right passive conical gear as can be seen, are exactly as a whole connecting into of bolster 14, right axle sleeve 13 and right passive conical gear 8 rigidity like this; The left-hand component of bolster 14 adopts grommet 16 to be connected with left axle sleeve 17, can relatively rotate between left so passive conical gear 9 and the pivot shaft 14.This structure design has satisfied the non-uniform movement requirement of left and right wheel.
The annular anti-attrition packing ring 15 (being formed by two semicircle bolt togethers) of left and right sides ring gear 9 and 8 centre is fixed on limit radial movement on the right passive conical gear 8 with straight pin, and is moving by bearing pre-fastening restrictive axial string again.Guarantee the mutual slip of the passive conical gear 9 in the left and right sides and 8 so on the one hand, can satisfy matching requirements by actv. on the other hand.The passive conical gear in the left and right sides that can guarantee automobile requires motion according to road conditions.
Although illustrated and described embodiment of the present utility model, for the ordinary skill in the art, be appreciated that under the situation that does not break away from principle of the present utility model and spirit and can carry out multiple variation, modification, replacement and modification to these embodiment, scope of the present utility model is limited by claims and equivalent thereof.
Claims (4)
1. two ring gear drive axles, comprise preposition diff, described diff is the open type diff, before comprising, half-rear axle gear and four planetary wheels, it is characterized in that: two pairs of deceleration hyperboloidal bevel gear sets arranged side by side about being provided with in the described drive axle, every pair of described deceleration hyperboloidal bevel gear set comprises initiatively conical gear and passive conical gear, the half front axle gear of described diff is connected with right initiatively conical gear by spline, described right initiatively conical gear and right passive conical gear are pair of meshing conical gear pair, the passive conical gear in the described right side is captiveed joint with the drive axle right axle sleeve, and described drive axle right axle sleeve is connected with the automobile back wheel right axle shaft by spline;
The half-rear axle gear of described diff is connected with an active cylindrical wheel by spline, and described active cylindrical wheel and a passive cylindrical wheel constitute cylindrical gear pair, and described passive cylindrical wheel is connected with left side active conical gear by spline; A described left side initiatively conical gear and left passive conical gear be another to the pitch cone gear pair, the passive conical gear in a described left side is captiveed joint with the drive axle left axle sleeve, described drive axle left axle sleeve is connected with the automobile back wheel left half axle by spline.
2. according to claim 1 pair of ring gear drive axle is characterized in that: described left and right passive conical gear adopts and is arranged in dorsad on the same axis, and adopts left-handed and dextrorotation respectively.
3. according to claim 1 pair of ring gear drive axle, it is characterized in that: the right-hand component of described left and right passive conical gear bolster and described drive axle right axle sleeve adopt interference fit, and the left-hand component of described bolster adopts grommet to be connected with described drive axle left axle sleeve.
4. according to claim 1 pair of ring gear drive axle, it is characterized in that in the middle of the described left and right passive conical gear annular anti-attrition packing ring being housed, and be fixed on the passive conical gear in the described right side with straight pin, limit radial movement, and by the motion of bearing pre-fastening restrictive axial.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200920181113 CN201559525U (en) | 2009-12-11 | 2009-12-11 | Drive axle with double driven gears |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200920181113 CN201559525U (en) | 2009-12-11 | 2009-12-11 | Drive axle with double driven gears |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201559525U true CN201559525U (en) | 2010-08-25 |
Family
ID=42624672
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 200920181113 Expired - Fee Related CN201559525U (en) | 2009-12-11 | 2009-12-11 | Drive axle with double driven gears |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN201559525U (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102756645A (en) * | 2012-06-05 | 2012-10-31 | 深圳市德塔电动汽车科技有限公司 | Chassis system for pure electric explosion-proof vehicle |
| CN108583275A (en) * | 2018-03-29 | 2018-09-28 | 厦门理工学院 | A kind of Double-axis transmission automobile |
| CN108859704A (en) * | 2018-06-28 | 2018-11-23 | 山东蓬翔汽车有限公司 | A kind of motor postposition pure electric vehicle drive axle of heavy truck |
| CN109695686A (en) * | 2018-12-07 | 2019-04-30 | 一汽解放汽车有限公司 | A kind of drive axle double speed decelerator structure of bi-bevel gear |
-
2009
- 2009-12-11 CN CN 200920181113 patent/CN201559525U/en not_active Expired - Fee Related
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102756645A (en) * | 2012-06-05 | 2012-10-31 | 深圳市德塔电动汽车科技有限公司 | Chassis system for pure electric explosion-proof vehicle |
| CN108583275A (en) * | 2018-03-29 | 2018-09-28 | 厦门理工学院 | A kind of Double-axis transmission automobile |
| CN108859704A (en) * | 2018-06-28 | 2018-11-23 | 山东蓬翔汽车有限公司 | A kind of motor postposition pure electric vehicle drive axle of heavy truck |
| CN109695686A (en) * | 2018-12-07 | 2019-04-30 | 一汽解放汽车有限公司 | A kind of drive axle double speed decelerator structure of bi-bevel gear |
| CN109695686B (en) * | 2018-12-07 | 2024-02-23 | 一汽解放汽车有限公司 | Driving axle double-speed reducer structure with double bevel gears |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C17 | Cessation of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20100825 Termination date: 20111211 |