CN113623377A - Inner limiting double anti-drop interaxial differential structure assembly - Google Patents
Inner limiting double anti-drop interaxial differential structure assembly Download PDFInfo
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- CN113623377A CN113623377A CN202110965117.3A CN202110965117A CN113623377A CN 113623377 A CN113623377 A CN 113623377A CN 202110965117 A CN202110965117 A CN 202110965117A CN 113623377 A CN113623377 A CN 113623377A
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- 230000000295 complement effect Effects 0.000 claims description 6
- 238000005299 abrasion Methods 0.000 description 5
- 238000005461 lubrication Methods 0.000 description 4
- 230000005540 biological transmission Effects 0.000 description 2
- 239000003638 chemical reducing agent Substances 0.000 description 2
- 230000000903 blocking effect Effects 0.000 description 1
- 230000007812 deficiency Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000009977 dual effect Effects 0.000 description 1
- 239000012208 gear oil Substances 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000002265 prevention Effects 0.000 description 1
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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
- F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
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Abstract
The invention discloses an inner-limiting double-anti-drop interaxial differential mechanism structure assembly which is characterized by comprising an input shaft, a cross shaft, a planet wheel, a rear half shaft wheel, a driving cylindrical gear, a thrust bearing, an axle difference shell and a sliding meshing sleeve, wherein the input shaft is connected with the cross shaft through a connecting rod; compared with the traditional structure, the arrangement of the limiting structures on two sides of the inner hole of the driving cylindrical gear solves the problem that the bushing is separated from any side; the arrangement of the driving cylindrical gear and the inverted cone structure meshing teeth of the sliding meshing sleeve solves the problem that the meshing teeth are disengaged after the differential lock is locked; the arrangement of the eccentric ball structure of the planet wheel spherical surface not only ensures the effective limit of the shaft difference shell to the planet wheel, but also well lubricates the two spherical surfaces; the arrangement of the planetary gear three-section type inner hole structure ensures effective spacing between the planetary gear three-section type inner hole structure and also ensures that the shaft holes of the planetary gear three-section type inner hole structure and the shaft holes of the planetary gear three-section type inner hole structure are well lubricated, so that the occurrence of different grinding faults is reduced.
Description
Technical Field
The invention relates to the technical field of heavy truck automobile axles, in particular to an inner limiting double anti-drop interaxial differential mechanism structure assembly.
Background
The interaxle differential assembly is an important part of a main speed reducer assembly of a middle axle of a drive axle, and not only plays a role of transmitting torque transmitted from an input shaft to a main cylindrical gear and a driven cylindrical gear of the middle axle, but also has a function of generating differential speed between the main cylindrical gear and the driven cylindrical gear so as to ensure the normal running of a vehicle.
In the traditional interaxial differential assembly, a lining limiting structure is not arranged in an inner hole of a driving cylindrical gear, and the driving gear is complex in loading condition, so that the driving gear continuously participates in interaxial differential speed and generates axial motion with an input shaft, so that the fault of lining disengagement occurs frequently, and even if the lining disengagement prevention limiting structure is arranged, the single-side limiting structure is adopted, and the fact that both sides of the lining can disengage in actual use is verified; in the traditional interaxial differential assembly, the engaging teeth of the driving cylindrical gear and the sliding engaging sleeve are straight edges, so that a dropping fault is often caused after the padlock is actually used, and the padlock is not firm; the outer spherical surface of the traditional planet gear and the inner spherical surface of the shaft difference shell are concentric, the clearance between the outer spherical surface of the traditional planet gear and the inner spherical surface of the shaft difference shell is too large and too small, the meshing clearance of the bevel gear is affected by the too large clearance, effective lubrication cannot be achieved between the spherical surfaces with too small clearances, and the abrasion is serious; the planet wheel inner hole and the cross shaft are matched, the meshing of the bevel gear is influenced due to the overlarge gap between the planet wheel inner hole and the cross shaft, and the gear oil with the undersized gap cannot enter fully, so that the abrasion is serious.
Disclosure of Invention
The present invention is directed to overcome the above-mentioned deficiencies of the prior art and to provide an inner-limiting dual anti-drop interaxial differential assembly.
The technical scheme provided by the invention is as follows: an inner-limiting double anti-drop interaxial differential structure assembly is characterized by comprising an input shaft, a cross shaft, a planet wheel, a rear half shaft wheel, a driving cylindrical gear, a thrust bearing, an axle difference shell and a sliding meshing sleeve;
the inner diameter of the cross shaft is the same as the outer diameter of the cross shaft matching position of the input shaft, the inner diameter of the cross shaft is matched with the outer diameter of the cross shaft matching position of the input shaft to realize radial limiting, and the input shaft drives the cross shaft to rotate freely; the inner diameter of the planet wheel is the same as the outer diameter of the cross shaft, the planet wheel and the cross shaft are assembled together, and the planet wheel freely rotates on the cross shaft; the inner diameter of the spherical surface of the shaft difference shell is the same as the outer diameter of the spherical surface of the planet wheel, the shaft difference shell and the planet wheel are assembled together in a matching way through the inner diameter and the outer diameter of the spherical surface, and the shaft difference shell floats on the planet wheel and is limited by the planet wheel in the axial direction and the radial direction; the inner diameter of the rear half shaft wheel is the same as the outer diameter of the matching position of the rear half shaft wheel of the input shaft, and the rear half shaft wheel and the input shaft are matched and assembled together, so that the rear half shaft wheel can freely rotate on the input shaft; the back half shaft wheel and the planet wheel have the same module of the bevel gear, the pitch cone angles are complementary, the shaft axes are mutually vertical, the pitch cone points are superposed, and the meshing and the relative rotation relation of the straight bevel gear are realized by meshing; the inner diameter of the driving cylindrical gear is the same as the outer diameter of the matching position of the driving cylindrical gear of the input shaft, and the driving cylindrical gear are matched and assembled together, so that the driving cylindrical gear can freely rotate on the input shaft; the modules of the bevel teeth of the driving cylindrical gear and the planet gear are equal, the pitch cone angles are complementary, the axes are mutually vertical, the pitch cone points are superposed, and the meshing and the relative rotation relation of straight bevel teeth are realized by meshing; the inner diameter of the thrust bearing is the same as the outer diameter of the driving cylindrical gear mounting position of the input shaft, the thrust bearing and the driving cylindrical gear are mounted together in a matching mode, the upper end face and the lower end face of the thrust bearing are parallel to the corresponding matching end faces of the input shaft and the driving cylindrical gear respectively, the thrust bearing, the driving cylindrical gear and the driving cylindrical gear are abutted together, and an axial gap of 0.8-1.2mm is reserved between the thrust bearing and the driving cylindrical gear, so that the meshing gap adjustment of the planet wheel, the rear half shaft wheel and the driving cylindrical gear is realized, meanwhile, the axial limit of the driving cylindrical gear is realized, and the planet wheel, the rear half shaft wheel and the driving cylindrical gear rotate mutually; the inner diameter of the sliding meshing sleeve is the same as the outer diameter of the matching position of the sliding meshing sleeve of the input shaft, the sliding meshing sleeve and the input shaft are matched to realize radial limiting, and the input shaft drives the sliding meshing sleeve to rotate freely.
Furthermore, the driving cylindrical gear is provided with a limiting flange at the inner hole of the bevel gear side, and the limiting flange is used for limiting the unilateral axial anti-falling of the driving cylindrical gear inner hole bushing.
Furthermore, the driving cylindrical gear is provided with a limiting groove at the inner hole of the meshing gear side, and the limiting groove is used for limiting the axial anti-falling of the other side of the driving cylindrical gear inner hole bush.
Furthermore, the driving cylindrical gear is provided with meshing teeth, and the number of the meshing teeth is 10-15, and the meshing teeth are uniformly distributed along the circumference; the meshing teeth are in inverted cone structures which are symmetrical along the center of the teeth, namely, the tooth flank is not vertical to the tooth bottom surface but has an camber angle of 2-3 degrees; the structure of the meshing teeth of the sliding meshing sleeve is the same as that of the meshing teeth, and the external dimensions are the same.
Furthermore, the spherical surface of the planet wheel is an eccentric ball structure which is symmetrical along the center of the inner hole.
Furthermore, the inner hole of the planet wheel is of a three-section structure.
The invention has prominent substantive characteristics and remarkable progress: 1. the driving cylindrical gear is provided with limiting structures for the bushing on two sides of the inner hole, so that the problem of the bushing falling off from any side is effectively solved; 2. the engaging teeth of the driving cylindrical gear and the sliding engaging sleeve are arranged in inverted cone structures, so that the problem that the engaging teeth are separated from the rear of a differential lock padlock existing in the market is effectively solved; 3. the arrangement of the spherical eccentric ball structure of the planet wheel ensures that the matching of the outer spherical surface of the planet wheel and the inner spherical surface of the shaft difference shell is a matching relation with larger gaps at two sides and smaller gaps in the middle, thereby not only ensuring the effective limit between the two spherical surfaces, but also ensuring that lubricating oil can enter from two sides more easily and the spherical surfaces can be lubricated well; 4. the setting of the hole syllogic structure of planet wheel makes the hole of planet wheel and the cooperation of cross axle diameter be the both sides clearance slightly bigger, the little cooperation relation in intermediate space, and it is spacing to have guaranteed effectual shaft hole between the two equally, still makes the two obtain more excellent lubrication, has effectively solved the axle difference that exists in a large number in the market and has ground the trouble.
Drawings
FIG. 1 is a schematic structural view of the present invention;
FIG. 2 is a schematic view of the configuration of the meshing teeth of the drive spur gear of the present invention;
fig. 3 is a schematic structural diagram of the planetary gear of the invention.
In the figure: the planetary gear transmission mechanism comprises an input shaft 1, a cross shaft 2, a planet wheel 3, a spherical surface 31, an inner hole 32, a rear half shaft wheel 4, a driving cylindrical gear 5, a limiting rib 51, a limiting groove 52, a meshing tooth 53, a thrust bearing 6, a shaft difference shell 7 and a sliding meshing sleeve 8.
Detailed Description
For a better understanding and appreciation of the invention, reference will now be made in detail to specific embodiments thereof, which are illustrated in the accompanying drawings; the examples are given solely for the purpose of illustration and are not intended to limit the scope of the invention.
As shown in fig. 1, 2 and 3, an inner-limiting double anti-drop interaxial differential structure assembly comprises an input shaft 1, a cross shaft 2, a planet wheel 3, a rear half shaft wheel 4, a driving cylindrical gear 5, a thrust bearing 6, a shaft difference shell 7 and a sliding meshing sleeve 8; the inner diameter of the cross shaft 2 is the same as the outer diameter of the cross shaft matching position of the input shaft 1, the cross shaft 2 and the input shaft are matched and fixed together through a spline, and the input shaft 1 drives the cross shaft 2 to rotate freely; the inner diameter of the planet wheel 3 is the same as the outer diameter of the cross shaft 2, the planet wheel 3 and the cross shaft 2 are assembled together in a matching mode through a shaft hole, the planet wheel 3 freely rotates on the cross shaft 2, and the number of the planet wheels 3 is 4; the spherical surface 31 of the planet wheel 3 is of an eccentric ball structure which is symmetrical along the center of an inner hole, and the inner hole 32 of the planet wheel is processed into a three-section structure, namely, the inner hole is divided into 3 sections in the length direction, the lengths of the 3 sections are basically equal, and compared with the size of the middle aperture, the apertures of the two sides are 0.05-0.1mm larger; the inner diameter of the spherical surface of the shaft difference shell 7 is the same as the outer diameter of the spherical surface of the planet wheel 3, the shaft difference shell 7 and the planet wheel 3 are assembled together in a matching way through the inner diameter and the outer diameter of the spherical surface, and the shaft difference shell 7 floats on the planet wheel 3 and is limited by the planet wheel 3 in the axial direction and the radial direction; the inner diameter of the rear half shaft wheel 4 is the same as the outer diameter of the rear half shaft wheel matching position of the input shaft 1, and the rear half shaft wheel 4 and the input shaft 1 are matched and assembled together through a shaft hole, so that the rear half shaft wheel 4 can freely rotate on the input shaft 1; the back half shaft wheel 4 and the planet wheel 3 have the same module of the bevel gear, the pitch cone angles are complementary, the shaft axes are mutually vertical, the pitch cone points are superposed, and the meshing together realizes the mutual meshing and relative rotation relationship of straight bevel gear; the inner diameter of the driving cylindrical gear 5 is the same as the outer diameter of the driving cylindrical gear matching position of the input shaft 1, and the driving cylindrical gear 5 and the input shaft 1 are matched and assembled together through a shaft hole, so that the driving cylindrical gear 5 can freely rotate on the input shaft 1; the modules of the bevel teeth of the driving cylindrical gear 5 and the planetary gear 3 are equal, the pitch cone angles are complementary, the axial leads are mutually vertical, the pitch cone points are superposed, and the meshing and the relative rotation relation of straight bevel teeth are realized by meshing; a limiting flange 51 is processed at the inner hole of the driving cylindrical gear 5 at the side of the bevel gear and is used for limiting the unilateral axial anti-falling of the inner hole bush of the driving cylindrical gear 5; a limiting groove 52 is processed on an inner hole of the driving cylindrical gear 5 on the side of the meshing gear, and after the bushing is pressed into the driving cylindrical gear 5, the top end of the bushing is pressed into the limiting groove 52, so that the anti-falling limiting on the other side of the bushing is realized; processing engaging teeth 53 on the driving cylindrical gear 5, wherein the number of the engaging teeth 53 is 10-15, and the engaging teeth are uniformly distributed along the circumference; the engaging teeth 53 are processed into an inverted cone structure which is symmetrical along the center of the teeth, i.e. the flank surface is not perpendicular to the bottom surface of the teeth but has an camber angle of 2-3 degrees; the inner diameter of the thrust bearing 6 is the same as the outer diameter of the driving cylindrical gear mounting position of the input shaft 1, the thrust bearing and the driving cylindrical gear are mounted together in a matched mode through shaft holes, the upper end face and the lower end face of the thrust bearing are parallel to the corresponding matched end faces of the input shaft 1 and the driving cylindrical gear 5 respectively, the thrust bearing, the driving cylindrical gear and the driving cylindrical gear are abutted together, and an axial gap of 0.8-1.2mm is reserved between the thrust bearing and the driving cylindrical gear, so that the planetary gear 3, the rear half shaft wheel 4 and the driving cylindrical gear 5 are adjusted in meshing gaps, the driving cylindrical gear 5 is axially limited, and the planetary gear, the rear half shaft wheel and the driving cylindrical gear rotate mutually; the inner diameter of the sliding meshing sleeve 8 is the same as the outer diameter of the matching position of the sliding meshing sleeve of the input shaft 1, the sliding meshing sleeve and the sliding meshing sleeve are matched through splines to realize radial limiting, and the input shaft 1 drives the sliding meshing sleeve 8 to rotate freely; the meshing teeth of the sliding meshing sleeve 8 are identical in structure with the meshing teeth 53 and are equal in external dimension.
The invention relates to an inner-limiting double-anti-drop inter-axle differential mechanism structure assembly which is a necessary structure in a main speed reducer assembly of a drive axle intermediate axle, wherein during work, the front end of an input shaft receives torque transmitted by a transmission shaft, and under the support of front and rear bearings of the input shaft, rotation is transmitted to a cross shaft through spline connection, a planet wheel and a shaft difference shell are driven to rotate together, and a sliding meshing sleeve also rotates at a constant speed along with the input shaft; due to the existence of the differential function, when the padlock is not used, the driving cylindrical gear and the meshing teeth of the sliding meshing sleeve are in a separated state, and at the moment, the driving cylindrical gear and the rear half-shaft wheel have a rotation speed difference; when a padlock is needed under a special working condition, the driving cylindrical gear is meshed with the meshing teeth of the sliding meshing sleeve, the rotating speed difference between the driving cylindrical gear and the rear half shaft wheel is eliminated, the driving cylindrical gear and the rear half shaft wheel rotate at the same speed along with the input shaft, the driving cylindrical gear has a self-locking function due to the inverted cone structure of the meshing teeth, namely the two meshing teeth cannot fall off easily once meshed, and in addition, the lining sleeve of the driving cylindrical gear can still be firmly kept in a non-falling state in a long-term use process due to the existence of the limiting blocking edge and the limiting groove.
In addition, in a differential state, the planet wheel rotates on the cross shaft, and the inner hole of the planet wheel is of a 3-section structure, so that the lubrication condition is greatly improved and the abrasion of the shaft hole is reduced on the premise that the original limit requirement is ensured for the planet wheel and the cross shaft; in the same way, due to the existence of the eccentric ball structure of the spherical surface of the planet wheel, the lubrication condition is greatly improved on the premise that the original spherical surface limit requirement is ensured for the planet wheel and the shaft difference shell, the abrasion between the spherical surfaces is reduced, and the abrasion resistance inside the whole interaxial differential is effectively improved.
It should be understood that technical features not described in detail in the specification belong to the prior art. Although the present invention has been described with respect to the above embodiments, the above embodiments are merely illustrative and not restrictive, and those skilled in the art can now appreciate that many more modifications can be made without departing from the spirit and scope of the invention as defined in the appended claims.
Claims (6)
1. An inner-limiting double anti-drop interaxial differential structure assembly is characterized by comprising an input shaft (1), a cross shaft (2), a planet wheel (3), a rear half shaft wheel (4), a driving cylindrical gear (5), a thrust bearing (6), an axle difference shell (7) and a sliding meshing sleeve (8);
the inner diameter of the cross shaft (2) is the same as the outer diameter of the cross shaft matching position of the input shaft (1), the inner diameter and the outer diameter are matched to realize radial limiting, and the input shaft (1) drives the cross shaft (2) to rotate freely; the inner diameter of the planet wheel (3) is the same as the outer diameter of the cross shaft (2), the planet wheel (3) and the cross shaft (2) are assembled together, and the planet wheel (3) freely rotates on the cross shaft (2); the inner diameter of the spherical surface of the shaft difference shell (7) is the same as the outer diameter of the spherical surface of the planet wheel (3), the shaft difference shell and the planet wheel are assembled together in a matched mode through the inner diameter and the outer diameter of the spherical surface, and the shaft difference shell (7) floats on the planet wheel (3) and is limited in the axial direction and the radial direction of the planet wheel (3); the inner diameter of the rear half shaft wheel (4) is the same as the outer diameter of the rear half shaft wheel matching position of the input shaft (1), and the rear half shaft wheel and the input shaft are matched and assembled together, so that the rear half shaft wheel (4) can freely rotate on the input shaft (1); the modules of the bevel teeth of the rear half shaft wheel (4) and the planet wheel (3) are equal, the pitch cone angles are complementary, the shaft axes are mutually vertical, the pitch cone points are superposed, and the meshing is realized so as to realize the mutual meshing and relative rotation relationship of straight bevel teeth; the inner diameter of the driving cylindrical gear (5) is the same as the outer diameter of the driving cylindrical gear matching position of the input shaft (1), and the driving cylindrical gear are matched and assembled together, so that the driving cylindrical gear (5) can freely rotate on the input shaft (1); the driving cylindrical gear (5) and the planet gear (3) have the same module of bevel teeth, complementary pitch cone angles, mutually vertical shaft axes and coincident pitch cone points, and the meshing realizes the mutual meshing and relative rotation relationship of straight bevel teeth; the inner diameter of the thrust bearing (6) is the same as the outer diameter of the driving cylindrical gear mounting position of the input shaft (1), the thrust bearing and the driving cylindrical gear are mounted together in a matching way, the upper end surface and the lower end surface of the thrust bearing are respectively parallel to the corresponding matching end surfaces of the input shaft (1) and the driving cylindrical gear (5), the thrust bearing, the driving cylindrical gear and the driving cylindrical gear are abutted together and leave an axial gap of 0.8-1.2mm, the meshing gap adjustment of the planet wheel (3), the rear half shaft wheel (4) and the driving cylindrical gear (5) is realized, meanwhile, the axial limit of the driving cylindrical gear (5) is also realized, and the three rotate mutually; the inner diameter of the sliding meshing sleeve (8) is the same as the outer diameter of the matching position of the sliding meshing sleeve of the input shaft (1), the sliding meshing sleeve and the sliding meshing sleeve are matched to realize radial limiting, and the input shaft (1) drives the sliding meshing sleeve (8) to rotate freely.
2. The structural assembly of a differential mechanism between two anti-drop shafts with internal limit according to claim 1 is characterized in that the driving cylindrical gear (5) is provided with a limit rib (51) at the inner hole of the bevel gear side for limiting the single-side axial anti-drop of the inner hole bushing of the driving cylindrical gear (5).
3. The structural assembly of a differential mechanism between two anti-drop shafts of an internal limit according to claim 1, characterized in that the driving cylindrical gear (5) is provided with a limiting groove (52) at the inner hole of the meshing tooth side for limiting the axial anti-drop of the other side of the inner hole bush of the driving cylindrical gear (5).
4. The differential mechanism structure assembly with the inner limit and the double anti-drop off interaxle according to claim 1, wherein the driving cylindrical gear (5) is provided with meshing teeth (53), and the number of the meshing teeth (53) is 10-15 and is uniformly distributed along the circumference; the meshing teeth (53) are in inverted cone structures which are symmetrical along the center of the teeth, namely, the tooth flank is not vertical to the tooth bottom surface but has an camber angle of 2-3 degrees; the meshing teeth of the sliding meshing sleeve (8) are the same as the meshing teeth (53) in structure and have the same external dimension.
5. The structural assembly of an internal-limiting double anti-drop interaxle differential according to claim 1, wherein the spherical surface (31) of the planet wheel (3) is an eccentric spherical structure that is symmetrical along the center of the inner hole.
6. The differential mechanism structure assembly with inner limit and double anti-drop off shafts as claimed in claim 1, characterized in that the inner hole (32) of the planet wheel (3) is of a three-section structure.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110965117.3A CN113623377B (en) | 2021-08-23 | 2021-08-23 | Internal limiting double-anti-drop interaxial differential mechanism structure assembly |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110965117.3A CN113623377B (en) | 2021-08-23 | 2021-08-23 | Internal limiting double-anti-drop interaxial differential mechanism structure assembly |
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| Publication Number | Publication Date |
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| CN113623377A true CN113623377A (en) | 2021-11-09 |
| CN113623377B CN113623377B (en) | 2024-01-16 |
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| CN202110965117.3A Active CN113623377B (en) | 2021-08-23 | 2021-08-23 | Internal limiting double-anti-drop interaxial differential mechanism structure assembly |
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Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE1480696A1 (en) * | 1964-05-09 | 1969-06-19 | Zahnradfabrik Friedrichshafen | Drive system for vehicles with four-wheel drive |
| US3492890A (en) * | 1965-12-29 | 1970-02-03 | Ferguson Res Ltd Harry | Four-wheel-drive motor vehicles |
| CN202520922U (en) * | 2012-03-28 | 2012-11-07 | 上汽依维柯红岩商用车有限公司 | Bridge case driving cylindrical gear assembly |
| CN108725569A (en) * | 2017-04-14 | 2018-11-02 | 株式会社捷太格特 | Transfer |
| CN209180310U (en) * | 2018-10-16 | 2019-07-30 | 北京福田戴姆勒汽车有限公司 | A kind of jackshaft retarder and the vehicle with it |
| CN110513462A (en) * | 2019-08-07 | 2019-11-29 | 一汽解放汽车有限公司 | A kind of inter-axle differential and vehicle with differential lock |
| CN210978432U (en) * | 2019-08-05 | 2020-07-10 | 中国第一汽车股份有限公司 | Automobile differential mechanism |
| CN212455405U (en) * | 2020-05-26 | 2021-02-02 | 山东蓬翔汽车有限公司 | Clean long-life type interaxial differential mechanism structure assembly |
-
2021
- 2021-08-23 CN CN202110965117.3A patent/CN113623377B/en active Active
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE1480696A1 (en) * | 1964-05-09 | 1969-06-19 | Zahnradfabrik Friedrichshafen | Drive system for vehicles with four-wheel drive |
| US3492890A (en) * | 1965-12-29 | 1970-02-03 | Ferguson Res Ltd Harry | Four-wheel-drive motor vehicles |
| CN202520922U (en) * | 2012-03-28 | 2012-11-07 | 上汽依维柯红岩商用车有限公司 | Bridge case driving cylindrical gear assembly |
| CN108725569A (en) * | 2017-04-14 | 2018-11-02 | 株式会社捷太格特 | Transfer |
| CN209180310U (en) * | 2018-10-16 | 2019-07-30 | 北京福田戴姆勒汽车有限公司 | A kind of jackshaft retarder and the vehicle with it |
| CN210978432U (en) * | 2019-08-05 | 2020-07-10 | 中国第一汽车股份有限公司 | Automobile differential mechanism |
| CN110513462A (en) * | 2019-08-07 | 2019-11-29 | 一汽解放汽车有限公司 | A kind of inter-axle differential and vehicle with differential lock |
| CN212455405U (en) * | 2020-05-26 | 2021-02-02 | 山东蓬翔汽车有限公司 | Clean long-life type interaxial differential mechanism structure assembly |
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|---|---|
| CN113623377B (en) | 2024-01-16 |
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