CN100462586C - Main speed reducing device having dynamic branch off structure - Google Patents
Main speed reducing device having dynamic branch off structure Download PDFInfo
- Publication number
- CN100462586C CN100462586C CNB2007100631935A CN200710063193A CN100462586C CN 100462586 C CN100462586 C CN 100462586C CN B2007100631935 A CNB2007100631935 A CN B2007100631935A CN 200710063193 A CN200710063193 A CN 200710063193A CN 100462586 C CN100462586 C CN 100462586C
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- Prior art keywords
- gear
- driven gear
- dynamic branch
- differential
- main reducing
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- Expired - Fee Related
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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
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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
- F16H48/00—Differential gearings
- F16H48/06—Differential gearings with gears having orbital motion
- F16H48/08—Differential gearings with gears having orbital motion comprising bevel gears
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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
- F16H48/00—Differential gearings
- F16H48/06—Differential gearings with gears having orbital motion
- F16H48/08—Differential gearings with gears having orbital motion comprising bevel gears
- F16H2048/085—Differential gearings with gears having orbital motion comprising bevel gears characterised by shafts or gear carriers for orbital gears
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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
- F16H48/00—Differential gearings
- F16H48/38—Constructional details
- F16H2048/385—Constructional details of the ring or crown gear
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Retarders (AREA)
Abstract
The invention relates to a main speed reducer with power diverting structure used to drive bridge, comprising a main speed reducer frame 1, two active gears 2, 4, a couple of power diverting cylinder gears 3, 5 which are meshed and in 1:1 gear ratio, a high-carrier differential integration 6 and an inactive gear 7. The power is input via the active gear 2 or 4, the power diverting cylinder gears 3, 5 divert half power to another active gear, the inactive gear 7 is arranged on the differential integration 6, while two ends are both disposed with teeth meshed with two active gears, to collect the powers on two transmission branch chains to be transmitted to the differential integration. The invention can avoid wheel speed reducer to reduce noise, cost and energy consumption with confirmed ground height of vehicle.
Description
Technical field
The present invention relates to a kind of main reducing gear that is applicable to the wheeled vehicle ransaxle, be specifically related to a kind of main reducing gear with dynamic branch structure.
Background technique
For cross-country ability and the passing capacity that improves vehicle, many off-road vehicles, cross-country cargo carrier and engineering vehicle all require vehicle to have bigger road clearance, and in many cases, the road clearance of vehicle depends primarily on the diameter of driving wheel and the diameter of main reducing gear.Single step helical conic reducer commonly used on the common wheeled vehicle is in order to satisfy required output torque, the diameter of driven gear is all bigger, be difficult to satisfy simultaneously the requirement of road clearance, many for this reason engineering vehicles have to adopt the double reduction mechanism that comprises wheel reductor.The double reduction bridge has adopted less velocity ratio in main retarding stage, reduced the output torque on the driven gear, thereby reduced the diameter of main reducing gear driven gear, increased road clearance, but have the cost height, problem such as transmission efficiency is low, noise is big and the wheel reductor heating is serious when running at high speed.Because wheel reductor is usually located in the wheel hub, radiating condition is very bad, and too high oily temperature not only makes machine oil and oil sealing be easy to wear out, and also might cause the tire internal air pressure to raise and blows out, and jeopardizes vehicle driving safety.Therefore the oil consumption of double reduction bridge that contains wheel reductor is not a kind of desirable layout structure apparently higher than the single-stage reduction axle yet.
In the main reducing gear of common in addition single reduction gear and the double reduction bridge that comprises wheel reductor, tooth on the driven gear is formed in a side of driven gear, when driving gear and driven gear carry out engagement driving, driven gear be subjected to that driving gear applies along differential axle to component, thereby cause the axial force imbalance of driven gear, distortion influences the normal engaged between the flank of tooth greatly during heavy duty, thereby limited the bearing capacity of driven gear, and then limited the moment of torsion that it can transmit.And the bigger axial force that driven gear applies reducer shell in order to bear heavy duty the time also is provided with the flange plate that contains stiffening rib usually between differential casing and driven gear, increased churning loss when running at high speed.In existing main reducing gear, driven gear need transmit this differential casing with moment of torsion by this flange plate, and then moment of torsion is passed to the cross axle of differential mechanism by differential casing, like this, flange plate and differential casing need bear very big moment of torsion when bearing very big axial force, thereby also need thicker with the differential casing design under the situation of flange plate increasing.Because differential casing need carry out subdivision on the plane at cross axle place, so that existing cross axle is installed, the thinnest part of differential casing also must pass several bolts, so the housing of differential mechanism all designs thicklyer usually simultaneously.This comprises the design of flange plate and thicker differential casing, both has been unfavorable for alleviating the weight of main reducing gear, has also limited the bearing capacity of the differential gear that is arranged at differential casing inside.The axial force of bearing on the differential casing finally is to pass to bevel housing by being installed in a pair of tapered roller bearing that differential casing is, the friction torque of tapered roller bearing under big axially load is bigger, and efficient is not high.
Summary of the invention
The object of the present invention is to provide a kind of compact structure, the main reducing gear that bearing capacity is high with dynamic branch structure, in limited space, increase substantially the bearing capacity of main reducing gear, under the prerequisite of road clearance that guarantees vehicle and passing capacity, remove wheel reductor from, thereby the cost of ransaxle is descended significantly, and reduce the oil consumption and the noise of vehicle.
To achieve these goals, technical solution of the present invention is, a kind of main reducing gear with dynamic branch structure, and it comprises at least:
Bevel housing;
Differential assembly, it is arranged on the bevel housing;
Driven gear is arranged on the differential assembly;
Driving gear, it is arranged on the bevel housing, and is meshed with driven gear;
Wherein, the both sides end face of described driven gear is shaped on the tooth that the number of teeth equates, described driving gear is set to two, these two driving gear numbers of teeth equate, and be meshed with the tooth of driven gear both sides respectively, on the gear shaft of these two driving gears, be respectively arranged with cylindrical gears, this two cylindrical gears is meshed and constitutes the dynamic branch cylindrical gear pair that a pair of velocity ratio is 1:1, the power of described main reducing gear is by one of them driving gear input, by this to dynamic branch cylindrical gears adjutant wherein half dynamic branch give another driving gear, and power is come together on the driven gear by the engagement driving of two driving gears and driven gear.
In the present invention, described differential assembly comprises differential casing, is arranged on the cross axle in the differential casing, the differential gear that is arranged on the planetary pinion on the cross axle and is meshed with this planetary pinion.
In the present invention, described driven gear has endoporus, and driven gear is enclosed within on the differential casing by this endoporus with being slidingly matched, and the cross axle axle head of described differential mechanism passes differential casing, and key is connected on the endoporus of described driven gear.
Position corresponding to the cross axle axle head on described endoporus is provided with 4 keyways, and 4 axle heads of described cross axle are formed with key, thereby by the key of this axle head and cooperating of keyway, the cross axle of differential mechanism directly given power transmission by driven gear.Like this, differential casing will not bear moment of torsion.
In the present invention, described cross axle is the combination cross axle, this combination cross axle comprises that central square, one are had strong market potential and two short pins, described central square has two crossing through holes, described having strong market potential run through central square, and described two ends of having strong market potential form key with the endoporus of driven gear and cooperate, and an end of described short pin forms key with driven gear and cooperates, the other end inserts in the through hole of central square, and ends at the periphery of having strong market potential.
Like this, each parts in the differential mechanism comprise that planetary pinion and combination cross axle can assemble by inserting by part, make differential casing locate also (the connecting by bolt again) of one at the cross axle place and do not need as existing differential casing, to cut open into two-part, and because the housing of differential mechanism does not bear moment of torsion, the housing of differential mechanism can be made very thinly, for given differential casing diameter, can hold bigger differential gear in the differential casing, improve the bearing capacity of differential mechanism.
In the present invention, described driven gear can be done a spot of play along the axis of differential mechanism, has guaranteed that the axial force that the driving gear of both sides acts on the compound driven gear equates that it is uniform making the distribution of power on the Transmitted chains of both sides.
In the present invention, described dynamic branch cylindrical gear pair is connected with the gear shaft of driving gear by key.
In the present invention, two cylindrical gearss of described dynamic branch cylindrical gear pair are helical gear, and its helix angle is identical, and rotation direction is opposite.
Utilize said structure of the present invention, the effect of main reducing gear of the present invention is significant: because the present invention all meshes rotation by driving gear in the both sides of driven gear, the both sides driving gear that it is subjected to is cancelled out each other at the reducer shaft component that makes progress, thereby the unbalanced problem of the axial force of having avoided the driven gear in the existing main reducing gear, even make this driven gear can not produce distortion yet and bring thus under heavily loaded situation engagement problem, there are two pairs of active and passive gears to work simultaneously in addition, therefore improved the bearing capacity of driven gear, make it can transmit bigger moment of torsion, satisfied the needs of output high pulling torque.And, because the axial force of both sides offsets on the driven gear, thereby do not need to be used to carry the flange plate of this axial force, and it is thinner that differential casing also can be provided with, not only structure is more compact, and for same differential casing diameter, can hold bigger differential gear in the differential casing, improved the bearing capacity of differential mechanism, the bearing capacity of differential mechanism can be complementary with the main reducing gear with dynamic branch structure.Therefore, the main reducing gear with dynamic branch structure of ransaxle that is applicable to of the present invention can increase output torque in several times ground in limited space, thereby can under the prerequisite that guarantees the ransaxle road clearance, remove wheel reductor from, reduce the vehicle bridge cost, reduce oil consumption.
Description of drawings
Fig. 1 structural representation with main reducing gear of dynamic branch structure of the present invention;
The compound driven gear of Fig. 2 main reducing gear of the present invention and the structural representation that is connected and makes up cross axle of differential spider;
The structural representation of Fig. 3 compound driven gear of the present invention;
The plan view of Fig. 4 Fig. 3 of the present invention;
Fig. 5 combination cross axle of the present invention structural representation of having strong market potential;
The side view of Fig. 6 Fig. 5 of the present invention;
The plan view of Fig. 7 Fig. 5 of the present invention;
The short pin structure schematic representation of the combination cross axle of Fig. 8 invention;
The short pin structure side view that Fig. 9 the present invention is shown in Figure 8;
The short pin structure plan view that Figure 10 the present invention is shown in Figure 8;
Figure 11 combination cross axle of the present invention central authorities box structure schematic representation;
The side view of Figure 12 Figure 11 of the present invention.
Embodiment
As shown in Figure 1, main reducing gear with dynamic branch structure of the present invention, it includes bevel housing 1 at least, is arranged at the differential assembly 6 on the bevel housing 1, two driving gears 2,4 that are arranged at the driven gear 7 on the differential assembly and are arranged on the bevel housing 1 and are meshed with driven gear 7.For convenience of description, be that this main reducing gear that view is used for back driving axle is an example to advance direction along garage, this two driving gear 2,4 is become left side driving gear 2 and right side driving gear 4 respectively.As Fig. 1, shown in Figure 3, the both sides end face of driven gear 7 of the present invention is shaped on the tooth that the number of teeth equates, the number of teeth of left side driving gear 2 and right side driving gear 4 equates, and be meshed with the driving gear of driven gear 7 both sides respectively, on the gear shaft 21 of left side driving gear 2, be provided with left side dynamic branch cylindrical gears 3, be provided with the right side dynamic branch gear 5 that is meshed with left side dynamic branch cylindrical gears 3 on the gear shaft 41 of right side driving gear 4, this left side dynamic branch cylindrical gears 3 is 1:1 with the velocity ratio of right side dynamic branch cylindrical gears 5.Utilize said structure, described power with main reducing gear of dynamic branch structure can be by left side driving gear 2 or 4 inputs of right side driving gear, by velocity ratio be a pair of dynamic branch cylindrical gears 3,5 of 1:1 will be wherein half dynamic branch give another driving gear, and the power on two transmission branch chain is come together on the driven gear 7 by left side driving gear 2 and right side driving gear 4 engagement driving with the tooth of driven gear 7 both sides.
Like this, in the main reducing gear working procedure with dynamic branch structure of the present invention, the driving gear 2 of driven gear 7 and both sides, 4 transmissions that are meshed, the both sides driving gear 2 that it is subjected to, 4 apply speed reducer assembly 6 axially on component cancel out each other, thereby the unbalanced problem of the axial force of having avoided the driven gear in the existing main reducing gear, there are two pairs of active and passive gears to work simultaneously in addition, improved the bearing capacity of driven gear, make it can transmit bigger moment of torsion, thereby can under the situation that does not increase driven gear 7 diameters, the needs of output high pulling torque have been satisfied.And, because the axial force of both sides offsets on the driven gear 7, thereby do not need as existing differential mechanism, to utilize flange plate and differential casing to carry this axial force, thereby can cancel flange plate and with differential casing be provided with thinner, not only structure is more compact, and for same differential casing diameter, can hold bigger differential gear in the differential casing, improved the bearing capacity of differential mechanism, the bearing capacity of differential mechanism can be complementary with the main reducing gear with dynamic branch structure.Therefore, main reducing gear of the present invention can increase output torque in several times ground in limited space, thereby can remove wheel reductor under the prerequisite that guarantees the ransaxle road clearance, reduces the vehicle bridge cost, reduces oil consumption.
As shown in Figure 1, differential assembly 6 of the present invention can comprise: differential casing 61, end cap 62 is arranged at the cross axle 65 in the differential casing 61, the differential gear 64 that is arranged at the planetary pinion 63 on this cross axle 65 and is meshed with planetary pinion 63.
In the present invention, as shown in Figure 1 and Figure 2, driven gear 7 has endoporus 71, this driven gear 7 is enclosed within on the housing 61 of differential gear with high bearing capacity assembly 6 with being slidingly matched by this endoporus 71, the axle head of the cross axle 65 of described differential assembly 6 passes differential casing 61, and key is connected on the endoporus 71 of described driven gear 7.Like this, driven gear 7 can directly pass to moment of torsion cross axle by this key connection, and the housing of differential mechanism is not bear moment of torsion, thereby can further reduce the design thickness of the housing 61 of differential mechanism, for given differential casing 61 diameters, can hold bigger differential gear in the differential casing 61, improve the bearing capacity of differential assembly 6.
As shown in Figure 2, as a concrete example, can be shaped on key 651 respectively at 4 axle heads of cross axle 65, on the endoporus 71 of driven gear 7, be formed with and this key 651 corresponding 4 keyways 72, thereby can directly power transmission be given the cross axle 65 of differential assembly 6 with the driven gear that cooperates of keyway 72 by this key 651.
Shown in Fig. 2, Fig. 5-12, cross axle 65 among the present invention can be the combination cross axle, this combination cross axle 65 comprises the central square 66 that is positioned at four planetary pinion 63 front-end faces centres, the 67 and two short pins 68 of having strong market potential, and wherein central square 66 has two crossing through holes 661.Have strong market potential and 67 run through central square 66, its two ends are shaped on key 651, match with two keyways 72 of driven gear 7.One end of every short pin 68 is shaped on key 651, matches with the keyway 72 of driven gear 7, and the other end is inserted in the hole 661 of central square 66, ends at 67 the periphery of having strong market potential.Like this, each parts in the differential assembly 6 comprise that planetary pinion 63 and combination cross axle 65 can assemble by inserting by part, make differential casing 61 locate also (the connecting by bolt again) of one at cross axle 65 places and do not need as existing differential casing, to cut open into two-part, thereby the thickness of the housing 61 of differential mechanism can further reduce, for given differential casing 61 diameters, can hold bigger differential gear in the differential casing 61, further improve the bearing capacity of differential assembly 6.
In the present invention, as Fig. 1-shown in Figure 4, can form described keyway 72 at the axial direction of driven gear 7 upper edge differential assemblies, and this keyway 72 runs through the endoporus 71 of driven gear 7 along the axial direction of this differential assembly.Like this, this driven gear 7 is not subjected to the restriction of the key 651 on the cross axle 65 at the axial direction of differential assembly, and, thereby on the axial direction of differential assembly, be not subjected to the restriction of differential casing 6 owing to this driven gear 7 is slidingly matched with differential casing 6 yet.The axial position of this driven gear 7 is to determine automatically when being meshed with two driving gears at the same time, can adjust burden apportionment on the transmission branch chain of the left and right sides by doing a spot of play along the axis of differential gear with high bearing capacity assembly 6, and finally the load on the transmission branch chain of the left and right sides equates, thereby the axial force that is subjected on two end faces of driven gear 7 reaches balance when equating, thereby guaranteed that the load distribution on the transmission branch chain of the left and right sides is uniform.
In the present invention, as a concrete example, as shown in Figure 1, described dynamic branch cylindrical gears 3,5 can be connected with the gear shaft 21,41 of driving gear 2,4 by spline respectively.
In the present invention, because the number of teeth of both sides driving gear 2,4 equates that the velocity ratio of two dynamic branch cylindrical gearss 3,5 is 1:1 (number of teeth equates), the number of teeth of driven gear 7 both sides also equates, therefore the velocity ratio on two transmission branch chain is strict equating, can not produce movement interference.
As a specific embodiment, as shown in Figure 1, power is by right side driving gear 4 input, by dynamic branch gear 5 and dynamic branch gear 3 will be wherein half power pass to left side driving gear 2, and finally converge on the compound driven gear 7.
For the phase angle that makes left and right sides driving gear 2,4 can be complementary with the phase angle of the teeth groove of driven gear 7 both sides, avoid driven gear 7 to destroy normal engaged between the flank of tooth, can add suitable adjustment link by suitable technological method or in structural design and guarantee phase angle correct between each transmission part because of too much axial float.In the present embodiment, for the phase angle that makes left and right sides driving gear 2,4 can be complementary with the phase angle of the teeth groove of compound driven gear 7 both sides, left side and right side dynamic branch cylindrical gears 3,5 all are set to helical gear, and helix angle is identical, and rotation direction is opposite; When being assembling, the technological method that is adopted comes two end faces of grinding dynamic branch cylindrical gears 5 by measurement size, change the phase angle of right side driving gear 4 by the distribution that changes two face grinding surpluses, thereby guarantee to have correct phase angle between each transmission part with respect to left side driving gear 2.Utilize the said structure of present embodiment, realized phase matching, guaranteed two driving gears and the correct engaging position of driven gear by latter two transmission branch chain strictness of dynamic branch.
In the present invention, also be provided with parts such as bearing 11,12,13, bearing cap 14, end cap 15, dust cover 16, oil sealing 17 and oil sealing support 18 on the bevel housing, the structure of those parts and position relation and conventional design are similar, do not repeat them here.
Carry out dynamic branch, main reducing gear driven gear 7 to measures such as the direct moment of torsion transmission of differential spider 65 and thin-walled differential casings by two driving gears 2,4 that utilize of the present invention, can in limited space, increase output torque in several times ground, thereby can under the prerequisite of the minimum road clearance that guarantees ransaxle, remove wheel reductor from, reduce the vehicle bridge cost, reduce oil consumption.
Concrete structure of making according to present embodiment and implementation methods only are used to the embodiment and the feasibility that illustrate that the present invention is feasible, but not are used to limit the present invention.
Claims (9)
1. main reducing gear with dynamic branch structure, it comprises at least:
Bevel housing;
Differential assembly, it is arranged on the bevel housing;
Driven gear is arranged on the differential assembly;
Driving gear, it is arranged on the bevel housing, and is meshed with driven gear;
It is characterized in that, the both sides end face of described driven gear is shaped on the tooth that the number of teeth equates, described driving gear is set to two, these two driving gear numbers of teeth equate, and be meshed with the tooth of driven gear both sides respectively, on the gear shaft of these two driving gears, be respectively arranged with cylindrical gears, this two cylindrical gears is meshed and constitutes the dynamic branch cylindrical gear pair that a pair of velocity ratio is 1:1, the power of described main reducing gear is by one of them driving gear input, by this dynamic branch cylindrical gears adjutant wherein half dynamic branch give another driving gear, and power is come together on the driven gear by the engagement driving of two driving gears and driven gear.
2. the main reducing gear with dynamic branch structure as claimed in claim 1, it is characterized in that, described differential assembly comprises differential casing, is arranged on the cross axle in the differential casing, the differential gear that is arranged on the planetary pinion on the cross axle and is meshed with this planetary pinion.
3. the main reducing gear with dynamic branch structure as claimed in claim 2, it is characterized in that, described driven gear has endoporus, driven gear is enclosed within on the differential casing by this endoporus with being slidingly matched, the axle head of the cross axle of described differential mechanism passes differential casing, and key is connected on the endoporus of described driven gear.
4. the main reducing gear with dynamic branch structure as claimed in claim 3, it is characterized in that, position corresponding to the cross axle axle head on described endoporus is provided with 4 keyways, 4 axle heads of described cross axle are formed with key, thereby by the key of this axle head and cooperating of keyway, the cross axle of differential mechanism directly given power transmission by driven gear.
5. the main reducing gear with dynamic branch structure as claimed in claim 4 is characterized in that, form described keyway at the axial direction of driven gear upper edge differential assembly, and this keyway runs through the endoporus of driven gear along the axial direction of differential assembly.
6. the main reducing gear with dynamic branch structure as claimed in claim 3 is characterized in that, described differential casing is structure as a whole at place, cross axle place.
7. the main reducing gear with dynamic branch structure as claimed in claim 2, it is characterized in that, described cross axle is the combination cross axle, described combination cross axle comprises that central square, one are had strong market potential and two short pins, described central square has two crossing through holes, described having strong market potential run through central square, described two ends of having strong market potential form key with the endoporus of driven gear and cooperate, one end of described short pin forms key with driven gear and cooperates, the other end inserts in the through hole of central square, and ends at the periphery of having strong market potential.
8. the main reducing gear with dynamic branch structure as claimed in claim 1 is characterized in that, described dynamic branch cylindrical gear pair is connected with the gear shaft of driving gear by key.
9. the main reducing gear with dynamic branch structure as claimed in claim 1 is characterized in that, two cylindrical gearss of described dynamic branch cylindrical gear pair are helical gear, and its helix angle is identical, and rotation direction is opposite.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2007100631935A CN100462586C (en) | 2007-01-31 | 2007-01-31 | Main speed reducing device having dynamic branch off structure |
| PCT/CN2007/000591 WO2008095344A1 (en) | 2007-01-31 | 2007-02-17 | A kind of split-power final reduction gear |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2007100631935A CN100462586C (en) | 2007-01-31 | 2007-01-31 | Main speed reducing device having dynamic branch off structure |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101016932A CN101016932A (en) | 2007-08-15 |
| CN100462586C true CN100462586C (en) | 2009-02-18 |
Family
ID=38726119
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2007100631935A Expired - Fee Related CN100462586C (en) | 2007-01-31 | 2007-01-31 | Main speed reducing device having dynamic branch off structure |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN100462586C (en) |
| WO (1) | WO2008095344A1 (en) |
Families Citing this family (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| ES2437668T3 (en) * | 2010-09-20 | 2014-01-13 | Siemens Aktiengesellschaft | Distributed power transmission mechanism for a wind power generator |
| CN102463461A (en) * | 2010-11-04 | 2012-05-23 | 长春轨道客车装备有限责任公司 | Locomotive wheelset phase angle adjustor and locomotive wheelset phase angle adjustment method |
| CN102465976A (en) * | 2010-11-18 | 2012-05-23 | 杭州联盛电子有限公司 | Differential damping clutch |
| CN103968003B (en) * | 2014-05-20 | 2016-08-24 | 西北工业大学 | An a kind of Helicopter Main Reducer point torsion drive mechanism |
| JP2016102568A (en) * | 2014-11-28 | 2016-06-02 | 武蔵精密工業株式会社 | Differential gear and process of manufacture of the same |
| CN105042023A (en) * | 2015-06-15 | 2015-11-11 | 重庆工商职业学院 | Adjustable double-end-surface gear transmission mechanism |
| CN104896057A (en) * | 2015-06-15 | 2015-09-09 | 重庆工商职业学院 | Highly stable and adjustable double-end face gear transmission mechanism |
| CN105179639A (en) * | 2015-06-15 | 2015-12-23 | 重庆工商职业学院 | Double-end-face gear transmission mechanism |
| CN104976312A (en) * | 2015-06-15 | 2015-10-14 | 重庆工商职业学院 | Double-end-face gear transmission mechanism with high stability |
| 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 |
| CN109723767B (en) * | 2019-01-23 | 2022-03-25 | 胡捷 | Vehicle speed reducer with power split output and differential function |
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| US5800305A (en) * | 1995-12-29 | 1998-09-01 | Koon-Woo Kang | Reduction gear with coaxial input and output shafts and combining planetary and nonplanetary gearing |
| CN2316169Y (en) * | 1997-11-21 | 1999-04-28 | 北京理工大学 | Main transmission and differential speed lock device for automobile |
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- 2007-01-31 CN CNB2007100631935A patent/CN100462586C/en not_active Expired - Fee Related
- 2007-02-17 WO PCT/CN2007/000591 patent/WO2008095344A1/en active Application Filing
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| EP0551122A2 (en) * | 1992-01-10 | 1993-07-14 | Kasahara Fumio | Power transmission |
| US6837820B1 (en) * | 2001-02-28 | 2005-01-04 | Torque-Traction Technologies, Inc. | Differential drive gear assembly |
| CN1378925A (en) * | 2002-02-21 | 2002-11-13 | 新疆升晟股份有限公司 | Differential 4 wheels independent driver for motor-driven vehicle |
| CN2718321Y (en) * | 2004-08-18 | 2005-08-17 | 杨林江 | Front-drive main reducer of electric automobile |
| CN1587753A (en) * | 2004-09-08 | 2005-03-02 | 周殿玺 | Universal transfer device |
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|---|---|
| CN101016932A (en) | 2007-08-15 |
| WO2008095344A1 (en) | 2008-08-14 |
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