CN201034149Y - Main retarding apparatus - Google Patents
Main retarding apparatus Download PDFInfo
- Publication number
- CN201034149Y CN201034149Y CNU2007201045611U CN200720104561U CN201034149Y CN 201034149 Y CN201034149 Y CN 201034149Y CN U2007201045611 U CNU2007201045611 U CN U2007201045611U CN 200720104561 U CN200720104561 U CN 200720104561U CN 201034149 Y CN201034149 Y CN 201034149Y
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- gear
- bevel gear
- differential
- drive bevel
- driven wheel
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Abstract
The utility model provides a main reduction device, comprising a planetary gear load balancing mechanism, two transmitting gears and two driving bevel gears driven by the planetary gear load balancing mechanism, a driven bevel gear engaged with the driving bevel gear, and a differential connected with the driven gear. The utility model is characterized in that one of the sun gears in the planetary gear load balancing mechanism is connected with the driving bevel gear, the other sun gear is connected with one of the mutually meshed intermediate transmitting gears by a shaft sleeve, the other intermediate transmitting gear is connected with a secondary driving bevel gear, the driving bevel gear and the secondary driving bevel gear are connected with a driven bevel gear with double-side teeth. The utility model divides the power equally into two powers which are in parallel path and are in reverse rotation direction and have equal torque, and then combines the two powers into a power by the engagement of the main and the secondary driving bevel gear and the driven bevel gear with double-side teeth and transmits the power to the differential directly by the driven bevel gear, and then outputs the power by a semi-axle gear, thus the power between the interleaving shafts is output, the axial migration of the driven bevel gear is overcome, and the transmission capability is increased by times.
Description
Technical field
The utility model relates to a kind of speed reducer, and especially a kind of main gear down device belongs to mechanical transmission design and manufacturing technology field.
Background technique
Bevel gear single-stage deceleration hyperboloid gear main reducing gear is important components in the vehicle transmission system, owing to will guarantee that vehicle has enough ground Clearances, so ceiling structure has ended the diameter of retarder driven wheel of differential, make the working life and the reliability of main reducing gear, in power train, become the link of most fragile.Traditional solution is to strengthen the offset or dish of drive bevel gear, though this method can increase the contact ratio of the main reducing gear engagement gear teeth, improve the flexural strength of gear, but increase along with offset or dish, the also corresponding increasing of the helix angle of drive bevel gear, make the normal radius of curvature of the intermeshing gear teeth also strengthen thereupon, not only reduced the contact stress between the flank of tooth, also increased along the lateral sliding of tooth depth direction and along the clump of tooth length direction to slip, final frictional loss, the reduction transmission efficiency of strengthening.Cross conference because of the contact stress between the flank of tooth and frictional loss in addition and produce too high temperature and pressure, easily cause oil film breakdown and flank of tooth sintering to be killed, antiscuffing capacity reduces.When drive bevel gear adopts bigger Offset and bigger helix angle, can produce huge end thrust, this just requires bevel gear pair to have better support stiffness, simultaneously also require tapered roller bearing that higher pre-tightness is arranged, this can cause bearing heating and wearing and tearing aggravation, the transmission efficiency and the working life of reducing main reducing gear again.
Driven wheel of differential is when transmitting torque, and its engagement position can produce skew because of the effect of axial force, and such skew comprises the axis away from drive bevel gear, and the deflection of driven wheel of differential axis, as the h among Fig. 1, Fig. 2.Along with the increase of transmitting torque, its skew is bigger, and intermeshing tooth load flank profil can be moved by the small end of Heel to the gear teeth, and form bigger stress and concentrate, thus the bearing capacity of reduction conic reducer.Wearing and tearing along with the tapered roller bearing that supports driven wheel of differential, cause the pre-tightness of tapered roller bearing to descend even disappearance, the skew of driven wheel of differential is further strengthened, and it is concentrated to form bigger stress, the support stiffness of bevel gear pair further descends, thereby has further reduced the bearing capacity and the working life of conic reducer.
Usually the structural design of main reducing gear should satisfy following requirement: the one, can guarantee that driving and driven bevel gear has good engagement situation; The 2nd, the work of the whole flank profils of requirement utilization partly, and is concentrated to eliminate stress; The 3rd, higher transmission efficiency and working life are arranged, such bevel gear pair just has maximum bearing capacity.But existing main reducing gear structure can not satisfy bevel gear pair good engagement situation is arranged, exist bigger stress and concentrate, fail to resolve bevel gear drive and exist the various defectives that bearing capacity is low and working life is short.
Along with vehicle adopts the development to the large-tonnage direction of high power engine and automobile, train, above-mentioned every defective that the transmission of single-stage hyperbolic face cone tooth exists highlights more.
Summary of the invention
For the driven wheel of differential that overcomes existing speed reducer can produce skew because of the responsive to axial force that transmitting torque meshes the position, thereby bring transmission efficiency low, deficiencies such as working life is short, the utility model provides a kind of driven wheel of differential can not be offset, the main gear down device that transmission capacity significantly improves.
The utility model is realized by following technical proposal: a kind of main gear down device, comprise the planetary pinion load balancing mechanism, driving gear and drive bevel gear by its driving, driven wheel of differential with the drive bevel gear engagement, the differential mechanism that links to each other with driven wheel of differential, it is characterized in that one of the sun gear in the planetary pinion load balancing mechanism links to each other with drive bevel gear, two of sun gear links to each other with one of intermeshing two intermediate drive gears by axle sleeve, another intermediate drive gear links to each other with inferior drive bevel gear, and drive bevel gear all links to each other with the driven wheel of differential of a band double cog with time drive bevel gear.So that by planetary pinion load balancing mechanism and a pair of intermeshing driving gear, it is opposite that power is equally divided into sense of rotation, the power of two parallel paths that torque equates, and pass to drive bevel gear and time drive bevel gear respectively, again by main, the engagement of the driven wheel of differential of inferior two drive bevel gear and band double cog, the power of two parallel paths is combined into a power, power is directly passed to differential axle by driven wheel of differential, planetary pinion, differential gear output through differential mechanism, thereby finish the power output between the alternating axis, and overcome the axial dipole field of driven wheel of differential.
One of sun gear in the described planetary pinion load balancing mechanism links to each other with the drive bevel gear afterbody by the link in it, makes drive bevel gear under the drive of sun gear and rotate, and exports thereby constitute first via power.
Two of sun gear in the described planetary pinion load balancing mechanism overlaps an end by link in it and the hollow half axle that is slidingly mounted on the drive bevel gear afterbody and links to each other, the other end of this half-axile sleeve links to each other with intermediate drive gear on being slidingly mounted on drive bevel gear by link, this intermediate drive gear links to each other with another intermediate drive gear on being fixed on time drive bevel gear, make time drive bevel gear under sun gear drives and rotate, parallel with first via power outgoing route thereby constitute, and moment of torsion equates, the second road power outgoing route that sense of rotation is opposite.
Be respectively equipped with first tooth and second tooth on the axial direction of described driven wheel of differential, wherein first tooth is meshed with drive bevel gear, second tooth is meshed with time drive bevel gear, driven wheel of differential is rotated under two drive bevel gear of primary and secondary drive, thereby the power of two parallel paths is combined into a power.
The Hand of spiral of the double cog of described driven wheel of differential is made as two opposite Hand of spiral respectively, and it is corresponding with the gear teeth Hand of spiral of two drive bevel gear of primary and secondary respectively, together rotate so that make two opposite drive bevel gear of sense of rotation can drive it, realize the power of two parallel paths is combined into the purpose of a power.
Two drive bevel gear of described primary and secondary are respectively by a pair of back-to-back tapered roller bearing and a bearing support and a guide bearing, supporting form with the formula of bridging is installed in two seat holes of reducer shell, and the adjustment pad is arranged between tapered roller bearing seat and reducer shell.
The described differential carrier that links to each other with driven wheel of differential, the driven wheel of differential both sides link to each other with left and right sides differential carrier, by two inside tapered roller bearings of big end, be supported in the seat hole of reducing gearbox, the tapered roller bearing two ends have two to adjust nut, can adjust the pre-tightness of tapered roller bearing by adjusting nut, cooperate the Roller Shaft bearing of two drive bevel gear of primary and secondary and the adjustment pad between the reducing gearbox, can adjust the backlash of two drive bevel gear and driven gear and the position of circular tooth contact easily.
Described driven wheel of differential both sides link to each other with left and right sides differential carrier, with bolt it is fastened in the middle of the differential carrier, thereby power is directly passed to differential axle, planetary pinion by driven gear, through differential gear output, finish the power output between the alternating axis.
The utility model compared with prior art has following advantage and effect: adopt such scheme, promptly shunt by working power, the transmission device at interflow, improved the structure of traditional main reducing gear, make full use of branch, the characteristic of interflow transmission, especially the two sides gear teeth by driven wheel of differential respectively with the master, the engagement of inferior two drive bevel gear, in the process of transferring power, the axial force equal and opposite in direction that the engagement position is produced, but direction is opposite, thereby cancel out each other, so fundamentally solved the problem of driven wheel of differential skew, helped improving the support stiffness of driven wheel of differential, keep bevel gear pair that good engagement situation is arranged.Concrete effect embodies as follows:
1. increase exponentially owing to the bevel gear pair bearing capacity, help adopting less initiative taper tooth offset distance and than low pitch angle, thereby reduced contact stress and the end thrust that has reduced bearing between the flank of tooth, improved the transmission efficiency of single reduction gear and the fatigue life of gear significantly.
2. because driving gear and drive bevel gear all are paired installation forms, the axial force that transmission produced obtains balance preferably, and stable drive, noise are reduced.Help to improve the engagement situation of bevel gear pair.
3. owing to there are two pairs of bevel gear pairs while joggleword driven gears axial dipole field can not take place, reducing stress again concentrates, can guarantee simultaneously that two pairs of driving and driven bevel gears have good engagement situation, help adopting the gear width of broad, so the peak torque that main reducing gear can transmit is more than the twice of equivalent diameter driven wheel of differential, has prolonged bevel gear pair working life and reliability.
4. the both sides gear teeth of driven wheel of differential produce the axial force opposite sign but equal magnitude at the engagement position of transferring power, can cancel out each other, reduced the load of the tapered roller bearing of driven wheel of differential supporting, reduce the quality of differential assembly, the bearing bearing load of both sides is equated, improved the support stiffness of driven wheel of differential, the retarder transmission is more steady, when the support stiffness that guarantees enough driven wheels of differential requires, can appropriateness reduce the pre-tightness that driven wheel of differential supports tapered roller bearing, improve transmission efficiency, prolonged the working life of tapered roller bearing and the adjustment cycle of maintenance.
5. because the ability of two drive bevel gear retarder transmitting torques significantly improves, can guarantee that vehicle has the enough desirable ground Clearance, has improved the passing ability of vehicle.So the main reducing gear that the utility model provides especially is suitable for powerful lorry, tractor and high-performance motor bus.Also can be widely used in the fields such as central driver of railway locomotive, tractor and helicopter.
Description of drawings
Fig. 1 is the kind of drive schematic representation of existing jackshaft single-stage deceleration main reducing gear;
Fig. 2 is existing main reducing gear and wheel reductor double reduction device kind of drive schematic representation;
Fig. 3 is the kind of drive schematic representation of of the present utility model pair of drive bevel gear speed reducer;
Fig. 4 is that the A of Fig. 3 is to view;
Fig. 5 is that the B of Fig. 3 is to view;
Fig. 6 be among Fig. 3 C to view;
Fig. 7 is a main gear down device structure sectional view of the present utility model;
Fig. 8 is the E-E view of Fig. 7;
Fig. 9 is the D-D view of Fig. 7;
Figure 10 is another main gear down device structure sectional view of the present utility model.
Embodiment
Below in conjunction with accompanying drawing the utility model is described in further detail, but content of the present utility model is not limited thereto.
The outside of all carrying planetary pinion shell 47 is by nut 1, flange connector 2, oil sealing 3, oil sealing base 4, bearing 5 is installed in the load balancing mechanism shell 6, this shell is by screw 8, bearing 9 links to each other with intermediate drive gear shell 41, sun gear 46 is equipped with in the inside of all carrying planetary pinion shell 47,43, planetary pinion 45 and cross axle 44, wherein, sun gear 46 links to each other with drive bevel gear 18 tail ends by spline 7, drive bevel gear 18 is by locking nut 10, needle bearing 14 is through in the intermediate gear 12, so that drive bevel gear 18 is under sun gear 46 drives and rotate, thereby constitute first via power outgoing route, sun gear 43 links to each other by the hollow half axle cover 42 that spline 7 and flip sleeve are contained on the drive bevel gear 18, hollow half axle cover 42 links to each other with intermediate drive gear 12 by spline 11, intermediate drive gear 12 and another intermediate drive gear 39 engagements, intermediate drive gear 39 is fixed on time drive bevel gear 35 by nut 40, so that inferior drive bevel gear 35 is under sun gear 43 drives and rotate, parallel with first via power outgoing route thereby constitute, and moment of torsion equates, the second road power outgoing route that sense of rotation is opposite, intermediate drive gear 12,39 are installed in the cavity 13 of intermediate drive gear shell 41, intermediate drive gear shell 41 links to each other with reducing gearbox 21 by screw, drive bevel gear 18, inferior drive bevel gear 35 is respectively by bearing support 38 and interior tapered roller bearing group 15 thereof, 17 and pad 16,37 are installed in the seat hole 36 of reducing gearbox 21, two drive bevel gear 18,35 head end is respectively by guide bearing 19, snap ring 20, double-screw bolt 33 and guide bearing lid 34 are fixed on the reducing gearbox 21, as Fig. 9, thereby make the master, inferior two drive bevel gear 18 and 35 bridge in the seat hole 36 that is supported on reducing gearbox 21, two drive bevel gear 18,35 the gear teeth respectively with the axial two-sided gear teeth 48 of driven wheel of differential 24,50 engagements, as Fig. 7, driven wheel of differential 24 also can be formed by two back-to-back bevel gear combinations, wherein the interarea gear teeth 48 of driven wheel of differential 24 mesh with the gear teeth 49 of drive bevel gear 18, the sense of rotation of driven wheel of differential 24 is g, the Hand of spiral of its interarea gear teeth 48 is dextrorotation, the sense of rotation of drive bevel gear 18 is f accordingly, the Hand of spiral of its gear teeth 49 is left-handed, as Fig. 3, Fig. 5, Fig. 6, the inferior face gear teeth 50 of driven wheel of differential 24 and 51 engagements of the gear teeth of time drive bevel gear 35, the sense of rotation of driven wheel of differential 24 is g, secondly the Hand of spiral of the face gear teeth 50 is left-handed, the sense of rotation of time drive bevel gear 35 is d accordingly, the Hand of spiral of its gear teeth 51 is dextrorotation, as Fig. 3, Fig. 4, Fig. 6, so that make two drive bevel gear 18 that sense of rotation is opposite, 35 can drive driven wheel of differential 24 together rotates, realization is combined into the power of two parallel paths the purpose of a power, driven wheel of differential 24 both sides link to each other with left and right sides differential carrier 23, it is fastened on middle with bolt 25, by two inside tapered roller bearings 22 of big end, be supported in the seat hole of reducing gearbox 21, tapered roller bearing 22 is anchored in the seat hole of reducing gearbox 21 with bearing cap 26 by bolt 27, tapered roller bearing 22 two ends have two to adjust nut 30, can adjust the pre-tightness of tapered roller bearing 22 by adjusting nut 30, cooperate main, the Roller Shaft bearing 38 of inferior two drive bevel gear and the adjustment pad 37 between the reducing gearbox 21, can adjust two drive bevel gear 18 easily, 35 and the backlash of driven wheel of differential 24 and the position of circular tooth contact, the inner edge of driven wheel of differential 24 is provided with six hole slots 54, differential axle 32 correspondences which is provided with planetary pinion 28 place hole slot 53, as Fig. 8, two differential gears 31 and pad 29 are installed in a left side respectively, in the right differential carrier 23, thereby power is directly passed to differential axle 32 by driven gear 24, planetary pinion 28, through differential gear 31 outputs, finish the power output between the alternating axis, as Fig. 7.
Among Figure 10, the afterbody that removes drive bevel gear 18, inferior drive bevel gear 35 passes through roller bearing 52 cantilever support respectively on intermediate drive gear shell 41, cancel simultaneously outside guide bearing 15, snap ring 20, double-screw bolt 33 and the guide bearing lid 33 of two drive bevel gear head ends, all the other structures are all identical with Fig. 7.
Claims (8)
1. main gear down device, comprise the planetary pinion load balancing mechanism, driving gear and drive bevel gear by its driving, driven wheel of differential with the drive bevel gear engagement, the differential mechanism that links to each other with driven wheel of differential, it is characterized in that one of the sun gear in the planetary pinion load balancing mechanism links to each other with drive bevel gear, two of sun gear links to each other with one of intermeshing two intermediate drive gears by axle sleeve, another intermediate drive gear links to each other with inferior drive bevel gear, and drive bevel gear all links to each other with the driven wheel of differential of a band double cog with time drive bevel gear.
2. main gear down device according to claim 1 is characterized in that one of the sun gear in the described planetary pinion load balancing mechanism links to each other with the drive bevel gear afterbody by the link in it.
3. main gear down device according to claim 1, it is characterized in that two the overlapping an end by link in it and the hollow half axle that is slidingly mounted on the drive bevel gear afterbody and link to each other of sun gear in the described planetary pinion load balancing mechanism, the other end of this half-axile sleeve links to each other with intermediate drive gear on being slidingly mounted on drive bevel gear by link, and this intermediate drive gear links to each other with another intermediate drive gear on being fixed on time drive bevel gear.
4. main gear down device according to claim 1 is characterized in that being respectively equipped with first tooth and second tooth on the axial direction of described driven wheel of differential, and wherein first tooth is meshed with drive bevel gear, and second tooth is meshed with time drive bevel gear.
5. main gear down device according to claim 1, the Hand of spiral that it is characterized in that the double cog of described driven wheel of differential is made as two opposite Hand of spiral respectively, and the gear teeth Hand of spiral of two drive bevel gear of primary and secondary is corresponding with the Hand of spiral of double cog respectively.
6. main gear down device according to claim 1, it is characterized in that two drive bevel gear of described primary and secondary are respectively by a pair of back-to-back tapered roller bearing and a bearing support and a guide bearing, be installed in two seat holes of reducer shell, and between tapered roller bearing seat and reducer shell, be provided with the adjustment pad.
7. main gear down device according to claim 1 is characterized in that the described differential carrier that links to each other with driven wheel of differential, by two inside tapered roller bearings of big end, is supported in the seat hole of reducing gearbox, and the tapered roller bearing two ends have two to adjust nut.
8. main gear down device according to claim 1 is characterized in that described driven wheel of differential both sides link to each other with left and right sides differential carrier, with bolt it is fastened in the middle of the differential carrier.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2007201045611U CN201034149Y (en) | 2007-04-23 | 2007-04-23 | Main retarding apparatus |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2007201045611U CN201034149Y (en) | 2007-04-23 | 2007-04-23 | Main retarding apparatus |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201034149Y true CN201034149Y (en) | 2008-03-12 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNU2007201045611U Expired - Fee Related CN201034149Y (en) | 2007-04-23 | 2007-04-23 | Main retarding apparatus |
Country Status (1)
| Country | Link |
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| CN (1) | CN201034149Y (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104889487A (en) * | 2014-03-05 | 2015-09-09 | 宁波德美锯业有限公司 | High-speed precise circular sawing machine |
| CN109372977A (en) * | 2018-12-05 | 2019-02-22 | 苏州绿控传动科技股份有限公司 | Electricity drives bridge list speed variable device |
| 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 |
-
2007
- 2007-04-23 CN CNU2007201045611U patent/CN201034149Y/en not_active Expired - Fee Related
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104889487A (en) * | 2014-03-05 | 2015-09-09 | 宁波德美锯业有限公司 | High-speed precise circular sawing machine |
| CN109372977A (en) * | 2018-12-05 | 2019-02-22 | 苏州绿控传动科技股份有限公司 | Electricity drives bridge list speed variable device |
| 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: 20080312 |