CN113202910A - Low-cost inter-wheel differential structure - Google Patents
Low-cost inter-wheel differential structure Download PDFInfo
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- CN113202910A CN113202910A CN202110434476.6A CN202110434476A CN113202910A CN 113202910 A CN113202910 A CN 113202910A CN 202110434476 A CN202110434476 A CN 202110434476A CN 113202910 A CN113202910 A CN 113202910A
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- 239000000463 material Substances 0.000 claims description 20
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- 230000007246 mechanism Effects 0.000 abstract description 8
- 230000005540 biological transmission Effects 0.000 description 11
- 229910000851 Alloy steel Inorganic materials 0.000 description 9
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- 239000003638 chemical reducing agent Substances 0.000 description 7
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- 230000004323 axial length Effects 0.000 description 3
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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
- F16H48/38—Constructional details
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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
- F16H48/40—Constructional details characterised by features of the rotating cases
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Abstract
The invention relates to a low-cost differential mechanism structure between wheels, which comprises a left differential shell, a driven bevel gear and a right differential shell which are coaxially arranged, wherein the end surface of the left differential shell is fixedly connected with the end surface of the right differential shell; one end of the transition disc, which faces to the right differential shell, is provided with an outward extending spigot, and the outward extending spigot is tightly embedded between the driven bevel gear and the right differential shell. By adding the transition disc, the length diameter of the driven bevel gear can be shortened, and the proportion in the length diameter direction is relatively coordinated. The overhanging tang of transition dish provides the rigidity for driven bevel gear and supports, has solved the relatively poor problem of driven bevel gear rigidity.
Description
Technical Field
The invention relates to the technical field of heavy-duty automobile driving devices, in particular to a low-cost inter-wheel differential structure.
Background
The wheel differential is widely applied to drive axles of medium and heavy-duty automobiles. The currently commonly used inter-wheel differential comprises a driven bevel gear, a left differential case, a driven bevel gear connecting bolt, a right differential case, a left differential case connecting bolt, a right differential case connecting bolt, a side gear, a planetary gear and a cross shaft, and is shown in fig. 2.
The left differential shell and the right differential shell of the inter-wheel differential are matched through radial rabbets and connected with connecting bolts to form an overall mounting framework of the differential; the driven bevel gear is matched with the right shell through a radial spigot, and the mounting end face is attached to the end face of the left differential shell and connected with the left differential shell through a connecting bolt; the right shell is of an integral spherical structure, a cross shaft hole is drilled in the spherical surface and used for assembling a cross shaft, and four planet wheels are uniformly distributed and assembled on the shaft neck of the cross shaft; the left half shaft gear and the right half shaft gear are respectively assembled in inner holes of the left differential shell and the right differential shell, and bevel gear transmission is adopted between the planetary gear and the left half shaft gear as well as between the planetary gear and the right half shaft gear; when the vehicle runs, the engine transmits power to the driving bevel gear through the transmission shaft, and the driving bevel gear and the driven bevel gear are in meshed transmission to drive the driven bevel gear to run; the driven bevel gear drives the left differential shell, the right differential shell and the cross shaft to rotate; the cross shaft drives two half shaft gears to rotate through the planetary gear, the half shaft gears are connected with the automobile half shaft through the internal spline, and the automobile tire is driven to rotate through the half shaft.
However, in the application and development of the reducer assembly system, different gear ratio requirements may be provided by a finished vehicle customer, and in the case of determining the overall layout of the reducer assembly system, for the speed ratio expansion, the local arrangement of the gears is generally subject to the overall layout reduction. When the speed ratio required by a customer is larger, the driven bevel gear structure and the connection form with the differential shell are shown in fig. 3, the structure of the left differential shell is a universal fixed structure, and the major diameter of the driven bevel gear is generally increased to meet the requirement. However, the gear structure is thick and heavy, the material utilization rate is low, and the driven bevel gear is usually made of alloy steel 20CrMnTiH and has high cost; and the long diameter size of the driven bevel gear is prolonged, so that the proportion of the long diameter direction of the driven bevel gear is not coordinated, the matching seam allowance of the driven bevel gear and the right differential shell is shorter, and the rigidity of the gear is poorer.
Disclosure of Invention
The invention provides a low-cost differential structure between wheels aiming at the technical problems in the prior art, and solves at least one problem in the background technology.
The technical scheme for solving the technical problems is as follows:
a low-cost inter-wheel differential structure comprises a left differential shell, a driven bevel gear and a right differential shell which are coaxially arranged, wherein the end face of the left differential shell is fixedly connected with the end face of the right differential shell, the driven bevel gear is sleeved on the periphery of the right differential shell and is fixedly connected with the end part of the left differential shell, an annular transition disc is coaxially arranged between the driven bevel gear and the left differential shell, the transition disc is sleeved on the periphery of the right differential shell and is matched with the right differential shell through a radial spigot, and the driven bevel gear, the transition disc and the left differential shell are fixedly connected; an outward extending spigot is arranged on one end, facing the right differential shell, of the transition disc, and the outward extending spigot is tightly embedded between the driven bevel gear and the right differential shell.
The invention has the beneficial effects that: by adding the transition disc, the length dimension of the driven bevel gear can be shortened, the proportion in the length direction is more coordinated, the structural design of the driven bevel gear becomes more reasonable, and the structure of the original left differential shell is not changed. The periphery of the right differential shell provides rigid support for the overhanging spigot of the transition disc, and the overhanging spigot of the transition disc provides rigid support for the driven bevel gear, so that the problem of poor rigidity of the driven bevel gear in the old scheme is solved.
On the basis of the technical scheme, the invention can be further improved as follows.
Further, the overhanging spigot on the transition disc is an annular concave spigot extending along the axial direction of the transition disc, the outer periphery of the overhanging spigot is abutted with the driven bevel gear, and the inner periphery of the overhanging spigot is abutted with the outer peripheral surface of the right differential shell.
The beneficial effect of adopting the further scheme is that: the overhanging tang on the transition dish is the tip location of the poor shell of right side, prevents to receive the reliability problem that takes place to connect between poor shell of left side, the poor shell of right side when external force is too big in the differential mechanism working process.
Further, the root of the extending spigot on the transition disc is provided with an inner fillet, the end part of the driven bevel gear, which is matched with the transition disc, is provided with an outer fillet, and when the driven bevel gear is installed in place, the inner fillet is attached to the outer fillet.
The beneficial effect of adopting the further scheme is that: the fillet of the root of the overhanging spigot on the transition disc is mutually attached to the excircle corner of the driven bevel gear, so that the strength and rigidity of the overhanging spigot are enhanced, and the supporting rigidity of the transition disc to the driven bevel gear is enhanced.
Furthermore, the differential mechanism structure further comprises a driven bevel gear connecting bolt, and the driven bevel gear connecting bolt is in threaded connection with the left differential shell, the transition disc and the driven bevel gear in sequence.
The beneficial effect of adopting the further scheme is that: poor shell, transition dish and driven bevel gear will be established ties in proper order through driven bevel gear connecting bolt, have guaranteed the connection stability between the three, prevent that the three from taking place radial offset at vehicle operation in-process.
Further, a radial convex spigot is arranged on the outer peripheral surface of the end part of the right differential shell, and the convex spigot of the right differential shell is mutually attached to the inner peripheral surface of the transition disc.
The beneficial effect of adopting the further scheme is that: the spigot at the position is matched and functionally complemented with the overhanging spigot of the transition disc, so that the connection stability and reliability between the right differential shell and the left differential shell are further improved.
Further, the thickness of the overhanging seam allowance is not less than 6 mm.
The beneficial effect of adopting the further scheme is that: the overhanging seam allowance has enough thickness to ensure the rigidity and the support of the overhanging seam allowance.
Further, the material of the transition disk is QT 500.
The beneficial effect of adopting the further scheme is that: the scheme improves the structure, the transition disc is additionally arranged between the driven bevel gear and the left differential shell, the QT500 material for the space is equivalent to replace the alloy steel material 20CrMnTiH, the using amount of the alloy steel material 20CrMnTiH in the old scheme is saved, the market price difference of the two materials is large, and therefore the product cost can be effectively reduced.
Furthermore, the differential mechanism structure also comprises a cross shaft, four planet gears, a left half shaft gear and a right half shaft gear, wherein the planet gears, the left half shaft gear and the right half shaft gear are all bevel gears, an inner spherical surface for mounting the planet gears is arranged in the right differential shell, four cross shaft holes for mounting the cross shaft are formed in the inner spherical surface, the four cross shaft holes are uniformly distributed on the inner spherical surface in a circumferential manner, and the plane where the four cross shaft holes are located is vertical to the axial direction of the drive axle; the shaft end of the cross shaft penetrates through the cross shaft hole and is matched with the inner circumferential surface of the outward extending spigot of the transition disc, and the four planetary gears are respectively arranged on the four shaft necks of the cross shaft and can respectively rotate around the axes of the shafts on which the planetary gears are respectively arranged; the left half axle gear and the right half axle gear are respectively arranged on two sides of the cross shaft and are respectively meshed with the four planet gears.
The beneficial effect of adopting the further scheme is that: the driving bevel gear of the automobile main reducer is meshed with the driven bevel gear, when an automobile runs, the driving bevel gear of the main reducer drives the driven bevel gear to rotate, and because the left differential shell and the right differential shell are fixedly connected with the driven bevel gear, the cross shafts in the left differential shell, the right differential shell and the right differential shell synchronously rotate along with the driven bevel gear, and the cross shafts drive the planetary gears installed on four shaft necks of the cross shafts to rotate. The planetary gears are respectively meshed with the left half shaft gear and the right half shaft gear to drive the left half shaft gear and the right half shaft gear to rotate along the circumferential direction of the drive axle. One end of the left half shaft/the right half shaft of the drive axle is correspondingly connected with the left half shaft gear/the right half shaft gear respectively, and the other end of the left half shaft/the right half shaft of the drive axle is connected with wheels, so that the automobile is driven to run. Bevel gear transmission is adopted between the planetary gears and the left and right half shaft gears, when torque is transmitted, great axial acting force is generated along the axes of the planetary gears and the two half shaft gears (namely the left and right half shaft gears), and relative motion is generated between the planetary gears and the differential case (namely the left and right differential cases). During the operation of the automobile, the right differential shell and the transition disc jointly provide reliable positioning and supporting for the cross shaft.
When the automobile runs straight, the planetary gear only revolves, the planetary gear shaft equally distributes the torque to the two half-axle gears, the rotating speed of the two half-axle gears is constantly equal to that of the differential case, the torque transmitted to the left wheel and the right wheel is also equal, and the rotating speed of the left wheel and the right wheel is equal.
When the automobile runs in a turn, the planetary gear also rotates while revolving, one half shaft rotates by an angle, the torques of the two half shafts cannot be evenly distributed, one half shaft is inevitably high in rotation speed, the other half shaft is inevitably low in rotation speed, and the automobile smoothly runs in a turn.
Drawings
FIG. 1 is a schematic view of the overall structure of the present invention;
FIG. 2 is a schematic cross-sectional view taken along line A-A of FIG. 1 (with internal structural components removed);
FIG. 3 is a schematic view of a transition disk according to the present invention;
FIG. 4 is a schematic diagram of a conventional inter-wheel differential;
fig. 5 is a schematic structural view of a conventional high-speed-ratio inter-wheel differential.
In the drawings, the components represented by the respective reference numerals are listed below:
1. driven bevel gear, 2, transition disc, 201, overhanging spigot, 3, left differential shell, 4, driven bevel gear connecting bolt, 5, left differential shell connecting bolt, right differential shell, 601, convex spigot, 602, cross shaft hole, 7, cross shaft, 8, planetary gear, 9, left half shaft gear, 10, right half shaft gear, alpha, internal angle, beta and external angle.
Detailed Description
The principles and features of this invention are described below in conjunction with the following drawings, which are set forth by way of illustration only and are not intended to limit the scope of the invention.
Fig. 4 shows a component structure of a conventional inter-wheel differential mentioned in the background art. The bevel gear differential mechanism comprises a driven bevel gear 1, a left differential shell 3, a driven bevel gear connecting bolt 4, a right differential shell 6, a left differential shell connecting bolt 5, a right differential shell connecting bolt, a half axle gear, a planetary gear 8 and a cross shaft 7. The left differential shell 3 and the right differential shell 6 are connected with a left differential shell connecting bolt and a right differential shell connecting bolt 5 through radial spigot matching to form an overall mounting framework of the differential mechanism. Driven bevel gear 1 and right side poor shell 6 pass through radial tang cooperation, and driven bevel gear 1's installation terminal surface and the laminating of the 3 terminal surfaces of left side poor shell are continuous with left side poor shell 3 with driven bevel gear connecting bolt 4. The right shell is of an integral spherical structure, a cross shaft hole 602 is drilled in the spherical surface and used for assembling a cross shaft 7, and four planetary gears 8 are uniformly distributed on the shaft neck of the cross shaft 7 in a circumferential manner; the left and right half shaft gears 10 are respectively assembled in the inner holes of the left and right differential shells 6, and the planetary gear 8, the left half shaft gear 9 and the right half shaft gear 10 are in bevel gear transmission. When the vehicle runs, the engine transmits power to the driving bevel gear through the transmission shaft and the speed reducer, and the driving bevel gear is meshed with the driven bevel gear 1 for transmission to drive the driven bevel gear 1 to run; the driven bevel gear 1 drives the left-right difference shell 6 and the cross shaft 7 to rotate; the cross shaft 7 drives two half shaft gears to rotate through the planetary gear 8, the half shaft gears are connected with the automobile half shaft through internal splines, and the automobile tires are driven to rotate through the half shaft.
The speed ratio of the inter-wheel differential is equal to the number of the driven bevel gears/the number of the driving bevel gears, generally, the speed ratio is 3.91-6.33, and is a large speed ratio section, and the speed ratio is 3.64-2.44, and is a small speed ratio section. The larger the speed ratio is, the smaller the tooth number of the driving bevel gear is, and the smaller the tooth number is, the smaller the diameter of the corresponding driving bevel gear is; the smaller the diameter of the drive bevel gear, the closer the driven bevel gear is to the drive bevel gear. However, the position of the mounting surface of the driven bevel gear is generally invariant with the speed ratio, and is the same for all speed ratios, and is determined by the overall reduction scheme arrangement. For the reasons, for the large speed ratio, under the condition that the number of the driven bevel gears is not changed, the radial direction of the driven bevel gears can be very high due to the fact that the positions of the installation surfaces need to be matched with the gear surface of the driving bevel gears, and the driving bevel gears can be perfectly meshed for transmission. Accordingly, the axial direction (i.e., the long diameter direction) of the driven bevel gear is extended to a sufficient length to allow the radial direction of the driven bevel gear to reach a desired height.
When the speed ratio requirement is great, because driven bevel gear 1 structure needs the overall layout who adapts to the final drive assembly, driven bevel gear 1 extends sufficient length to 6 directions of differential shell right and can cooperate the transmission with the drive bevel gear of final drive, this conventional inter-wheel differential can not satisfy the demand this moment. For a high-speed-ratio inter-wheel differential, the driven bevel gear 1 is structured and connected with a differential housing as shown in fig. 5, and the long diameter of the driven bevel gear 1 is generally increased to meet the requirement. However, the gear structure is thick and heavy, the material utilization rate is low, and the driven bevel gear 1 is usually made of alloy steel 20CrMnTiH, so that the cost is high; and the proportion of the long diameter direction is not coordinated, the radial spigot of the driven bevel gear 1 matched with the right differential shell 6 is shorter, one end of the driven bevel gear 1 is suspended, when the driven bevel gear 1 is in meshing transmission with the driving bevel gear, the end part of the driven bevel gear 1 cannot be supported well, and the rigidity of the gear is poorer.
The low-cost differential structure between wheels as shown in fig. 1-2 comprises a left differential shell 3, a driven bevel gear 1 and a right differential shell 6 which are coaxially arranged, wherein the end surface of the left differential shell 3 is fixedly connected with the end surface of the right differential shell 6 through a left differential shell connecting bolt and a right differential shell connecting bolt 5, and the driven bevel gear 1 is sleeved on the periphery of the right differential shell 6 and is fixedly connected with the end part of the left differential shell 3 through a connecting piece. Driven bevel gear 1 with the coaxial annular transition dish 2 that is equipped with between the poor shell 3 in a left side, 2 covers of transition dish are established the poor shell 6 in the right side the periphery, and with the poor shell 6 in the right side cooperates through radial tang, driven bevel gear 1 the transition dish 2 with the poor shell 3 in a left side sets gradually and through driven bevel gear connecting bolt 4 fixed connection. As shown in fig. 2 and 3, an outward extending spigot 201 is provided on one end of the transition disc 2 facing the right differential case 6, and the outward extending spigot 201 is tightly inserted between the driven bevel gear 1 and the right differential case 6. The axial length of the male end 201 is not less than the axial length of the inner peripheral surface of the driven bevel gear 1.
By adding the transition disc 2, the length dimension of the driven bevel gear 1 can be shortened, the proportion in the length direction is more coordinated, the structural design of the driven bevel gear 1 becomes more reasonable, and the original structure of the left differential shell 3 is not changed. The periphery of the right differential shell 6 provides rigid support for the overhanging spigot 201 of the transition disc 2, and the overhanging spigot 201 of the transition disc 2 provides rigid support for the driven bevel gear 1, so that the problem that the rigidity of the driven bevel gear 1 is poor in the old scheme is solved.
On the basis of the technical scheme, the invention can be further improved as follows.
In this embodiment, the overhanging dog-ear 201 of the transition disk 2 is an annular concave dog-ear extending in the axial direction of the transition disk 2, the outer circumference of the overhanging dog-ear 201 abuts against the driven bevel gear 1, and the inner circumference of the overhanging dog-ear 201 abuts against the outer circumferential surface of the right differential case 6.
The overhanging seam allowance 201 on the transition disc 2 is used for positioning the end part of the right differential shell 6, so that the problem of reliability of connection between the left differential shell 3 and the right differential shell 6 when the differential mechanism is subjected to overlarge external force in the working process is solved.
In this embodiment, the root of the extending spigot 201 on the transition disc 2 is provided with an internal fillet α, the end of the driven bevel gear 1, which is matched with the transition disc 2, is provided with an external fillet β, and when the driven bevel gear 1 is installed in place, the internal fillet α and the external fillet β are attached to each other.
The fillet alpha of the root part of the overhanging spigot 201 on the transition disc 2 is mutually attached to the external fillet beta on the driven bevel gear 1, so that the strength and rigidity of the overhanging spigot 201 are enhanced, and the supporting rigidity of the transition disc 2 to the driven bevel gear 1 is enhanced.
In this embodiment, the differential mechanism structure further includes a driven bevel gear connecting bolt 4, and the driven bevel gear connecting bolt 4 is in threaded connection with the left differential case 3, the transition disc 2 and the driven bevel gear 1 in sequence.
In this embodiment, a radial male end 601 is provided on the outer peripheral surface of the end portion of the right differential case 6, and the male end 601 of the right differential case 6 and the inner peripheral surface of the transition disc 2 are attached to each other.
The spigot is matched and functionally complemented with the overhanging spigot 201 of the transition disc 2, so that the connection stability and reliability between the right differential shell 6 and the left differential shell 3 are further improved, and the rigidity of the driven bevel gear 1 is enhanced.
In this embodiment, the thickness of the overhanging seam allowance 201 is not less than 6 mm.
The projecting seam allowance 201 is provided with a sufficient thickness to ensure rigidity and support of the projecting seam allowance 201.
In this embodiment, the material of the transition disk 2 is QT 500.
The scheme improves the structure, the transition disc 2 is additionally arranged between the driven bevel gear 1 and the left differential shell 3, the QT500 material for the space is equivalent to replace an alloy steel material 20CrMnTiH, the using amount of the alloy steel material 20CrMnTiH in the old scheme is saved, the market price difference of the two materials is large, and therefore the product cost can be effectively reduced.
In this embodiment, the differential structure further includes a cross shaft 7, four planet gears 8, a left side gear 9, and a right side gear 10, where the planet gears 8, the left side gear 9, and the right side gear 10 are all bevel gears. The structure of the cross shaft 7, the four planet gears 8, the left side gear 9 and the right side gear 10 and the matching relationship among the cross shaft, the four planet gears 8, the left side gear 9 and the right side gear 10 adopt the prior art, are not shown in fig. 1, and can be referred to fig. 2 and 3. An inner spherical surface for mounting the planetary gear 8 is arranged in the right differential shell 6, four cross shaft holes 602 for mounting the cross shaft 7 are formed in the inner spherical surface, the four cross shaft holes 602 are circumferentially and uniformly distributed on the inner spherical surface, and the plane where the four cross shaft holes 602 are located is perpendicular to the axial direction of the drive axle; the shaft end of the cross shaft 7 penetrates through the cross shaft hole 602 and is matched with the inner circumferential surface of the outward extending spigot 201 of the transition disc 2, and the four planet gears 8 are respectively arranged on the four shaft necks of the cross shaft 7 and can respectively rotate around the axes of the shafts on which the planet gears are respectively arranged; the left half-shaft gear 9 and the right half-shaft gear 10 are respectively arranged on two sides of the cross shaft 7 and are respectively meshed with the four planet gears 8.
The working principle is as follows:
a driving bevel gear of a main speed reducer of an automobile is meshed with a driven bevel gear 1, when the automobile runs, the driving bevel gear of the main speed reducer drives the driven bevel gear 1 to rotate, and as a left differential shell 3 and a right differential shell 6 are fixedly connected with the driven bevel gear 1, cross shafts 7 in the left differential shell 3, the right differential shell 6 and the right differential shell 6 synchronously rotate along with the driven bevel gear 1, and the cross shafts 7 drive planetary gears 8 installed on four shaft necks of the cross shafts to rotate. The planetary gears 8 are engaged with the left and right side gears 9 and 10, respectively, to drive the left and right side gears 9 and 10 to rotate in the circumferential direction of the drive axle. One end of the left half shaft/the right half shaft of the drive axle is correspondingly connected with the left half shaft gear 9/the right half shaft gear 10 respectively, and the other end is connected with wheels, so that the automobile is driven to run. The planetary gears 8 and the left and right side gears 9 and 10 are in bevel gear transmission, when torque is transmitted, great axial force is applied along the axes of the planetary gears 8 and the two side gears (namely the left and right side gears 9 and 10), and relative motion is generated between the planetary gears 8 and the differential housings (namely the left and right differential housings 3 and 6). The right differential housing 6 and the transition plate 2 together provide reliable positioning and support for the cross-shaft 7 during operation of the vehicle.
When the automobile runs straight, the planet gear 8 only revolves, the shaft of the planet gear 8 equally distributes the torque to the two side gears, the rotating speed of the two side gears is constantly equal to that of the differential case, the torque transmitted to the left wheel and the right wheel is also equal, and the rotating speed of the left wheel and the right wheel is equal. When the automobile runs in a turn, the planetary gear 8 also rotates while revolving, one half shaft rotates by an angle, the torques of the two half shafts cannot be evenly distributed, one half shaft is inevitably high in rotation speed and the other half shaft is inevitably low in rotation speed, two wheels run in a differential mode, and the automobile smoothly runs in a turn.
In the driving process of the automobile, the overhanging spigot 201 of the transition disc 2 provides rigid support for the driven bevel gear 1 and the right differential shell 6, and the overhanging spigot 201 is matched with the protruding spigot 601 at the end part of the right differential shell 6, so that the connection between the left differential shell 6 and the right differential shell 6 is more reliable. The material of the transition disc 2 is QT500, and the material of the gear is alloy steel 20 CrMnTiH. The transition disc 2 is arranged between the driven bevel gear 1 and the left differential shell 3, so that the axial length of the driven bevel gear 1 can be properly reduced, the long-diameter proportion of the driven bevel gear 1 is more coordinated, and the problem of poor rigidity of the gear is solved; meanwhile, the QT500 material is used for replacing an alloy steel material 20CrMnTiH in the space which is equivalent to the reduced space of the driven bevel gear 1, and the market price difference of the two materials is large, so that the product cost can be effectively reduced; compared with an alloy steel material 20CrMnTiH, the material density of QT500 is lower, so that the light-weight design of the differential assembly is facilitated. The fillet alpha of the root part of the overhanging spigot 201 on the transition disc 2 is mutually attached to the external fillet beta on the driven bevel gear 1, so that the strength and rigidity of the overhanging spigot 201 are enhanced, and the supporting rigidity of the transition disc 2 to the driven bevel gear 1 is enhanced.
The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the invention, and any modifications, equivalents, improvements and the like that fall within the spirit and principle of the present invention are intended to be included therein.
Claims (8)
1. A low-cost inter-wheel differential structure comprises a left differential shell (3), a driven bevel gear (1) and a right differential shell (6) which are coaxially arranged, wherein the end face of the left differential shell (3) is fixedly connected with the end face of the right differential shell (6), the driven bevel gear (1) is sleeved on the periphery of the right differential shell (6) and is fixedly connected with the end part of the left differential shell (3), the low-cost inter-wheel differential structure is characterized in that an annular transition disc (2) is coaxially arranged between the driven bevel gear (1) and the left differential shell (3), the transition disc (2) is sleeved on the periphery of the right differential shell (6) and is matched with the right differential shell (6) through a radial spigot, and the driven bevel gear (1), the transition disc (2) and the left differential shell (3) are fixedly connected; an outward extending spigot (201) is arranged at one end, facing the right differential shell (6), of the transition disc (2), and the outward extending spigot (201) is tightly embedded between the driven bevel gear (1) and the right differential shell (6).
2. A low-cost inter-wheel differential structure according to claim 1, characterized in that the male end (201) of the transition disc (2) is an annular female end extending in the axial direction of the transition disc (2), the outer periphery of the male end (201) abuts against the driven bevel gear (1), and the inner periphery of the male end (201) abuts against the outer periphery of the right differential case (6).
3. A low-cost inter-wheel differential structure according to claim 2, characterized in that the projecting spigots (201) are provided with fillets (α) at the root portions of the transition discs (2), and the ends of the driven bevel gears (1) that are fitted to the transition discs (2) are provided with fillets (β), the fillets (α) and the fillets (β) being in abutment when the driven bevel gears (1) are in place.
4. A low-cost inter-wheel differential structure according to claim 1, characterized in that it further comprises a driven bevel gear connecting bolt (4), said driven bevel gear connecting bolt (4) being in threaded connection with said left differential case (3), said transition disc (2) and said driven bevel gear (1) in sequence.
5. A low-cost differential structure between wheels according to claim 1 or 4, characterized in that the end outer peripheral surface of the right differential case (6) is provided with a radial male joint (601), and the male joint (601) of the right differential case (6) and the inner peripheral surface of the transition disc (2) are mutually attached.
6. A low-cost inter-wheel differential structure according to claim 1, characterized in that the thickness of said over-extension spigot (201) is not less than 6 mm.
7. A low-cost inter-wheel differential structure according to claim 1, characterized in that the material of the transition disc (2) is QT 500.
8. The differential structure between wheels with low cost according to claim 1 is characterized by further comprising a cross axle (7), four planet gears (8), a left half axle gear (9) and a right half axle gear (10), wherein the planet gears (8), the left half axle gear (9) and the right half axle gear (10) are all bevel gears, an inner spherical surface for mounting the planet gears (8) is arranged in the right differential case (6), four cross axle holes (602) for mounting the cross axle (7) are formed in the inner spherical surface, the four cross axle holes (602) are uniformly distributed on the inner spherical surface in a circumferential manner, and the plane where the four cross axle holes (602) are located is perpendicular to the axial direction of the drive axle; the shaft end of the cross shaft (7) penetrates through the cross shaft hole (602) and is matched with the inner circumferential surface of the outward spigot (201) of the transition disc (2), and the four planetary gears (8) are respectively arranged on four shaft necks of the cross shaft (7) and can respectively rotate around the axes of the shafts on which the planetary gears are respectively arranged; the left half shaft gear (9) and the right half shaft gear (10) are respectively arranged on two sides of the cross shaft (7) and are respectively meshed with the four planet gears (8).
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| CN202110434476.6A CN113202910B (en) | 2021-04-21 | 2021-04-21 | Low-cost differential mechanism structure between wheels |
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| CN202110434476.6A CN113202910B (en) | 2021-04-21 | 2021-04-21 | Low-cost differential mechanism structure between wheels |
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| CN113202910A true CN113202910A (en) | 2021-08-03 |
| CN113202910B CN113202910B (en) | 2024-10-11 |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN116658588A (en) * | 2023-04-26 | 2023-08-29 | 陕西汉德车桥有限公司 | Method for arranging driven bevel gears of main speed reducer |
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| CN214743139U (en) * | 2021-04-21 | 2021-11-16 | 东风德纳车桥有限公司 | Low-cost inter-wheel differential structure |
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| GB1252520A (en) * | 1969-10-18 | 1971-11-03 | ||
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| US5591098A (en) * | 1995-02-09 | 1997-01-07 | Arb Corporation Limited | Locking differential |
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| CN116658588A (en) * | 2023-04-26 | 2023-08-29 | 陕西汉德车桥有限公司 | Method for arranging driven bevel gears of main speed reducer |
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|---|---|
| CN113202910B (en) | 2024-10-11 |
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