Differential mechanism integrated with two-gear planet row speed reduction structure

Abstract

The utility model relates to a differential integrated with a two-gear planet row speed reduction structure, which comprises a power input shaft, a main power transmission gear ring, a sliding meshing sleeve, a fixed support, a gear ring and a differential shell, a sun gear is arranged at one end of the power input shaft, a planet gear is arranged between the sun gear and the gear ring, and the gear ring is arranged on the periphery of a gear ring support. A middle power transmission gear ring is arranged at one end of the gear ring support, a fixed support is arranged on the left side of the middle power transmission gear ring, a main power transmission gear ring is arranged on the right side of the middle power transmission gear ring, the periphery of the middle power transmission gear ring is connected with a sliding meshing sleeve through a spline, and the sliding meshing sleeve is in transmission connection with the fixed support or the main power transmission gear ring. The two-gear planet row speed reducing mechanism is integrally arranged on the basis of a conventional differential mechanism structure, namely, two-gear speed ratio adjustment of the differential mechanism is achieved, meanwhile, the speed ratio per hour at a low gear is remarkably increased, the dynamic property is more excellent, and therefore more excellent working condition applicability is achieved.

Description

Technical Field

[0001] The utility model relates to the technical field of new energy commercial vehicles, in particular to a differential integrated with a two-speed planetary gear reduction structure. Background Art

[0002] At present, with the development of new energy commercial vehicle technology and the continuous expansion of the market, low energy consumption, high efficiency, and lightweight have become the main development demands of the new energy commercial vehicle market. Therefore, integrated electric drive axles have been rapidly developed and applied. However, due to the relatively compact volume of conventional integrated electric drive axles, it is difficult for the reducer to achieve large reduction ratio transmission or reduction ratio adjustment, which seriously affects the power performance of the electric drive axle and limits the applicability of the electric drive axle in multiple working conditions.

[0003] To solve this problem, the common technical means include the following several solutions: One is to increase the number of transmission gear stages of the reduction box to increase the transmission reduction ratio. Although this solution can solve the problem of insufficient power performance of the electric drive axle, too many transmission stages will lead to an increase in friction loss, reduce the transmission efficiency, and increase energy consumption. The second is to increase the transmission ratio of the meshing gears without changing the number of gear transmission stages to improve the power performance of the electric drive axle. The disadvantage of this solution is that it will increase the volume of the reduction box, resulting in an increase in the structural size of the electric drive axle, which is not conducive to the layout of the vehicle structure. The third is to achieve large and small reduction ratio adjustment by means of the shifting structure of the AMT gearbox on the basis of the above two solutions. The structure is complex, the reliability is low, and the maintenance is inconvenient. Therefore, there is an urgent need to propose a solution that can increase the transmission reduction ratio of the reducer and improve the power performance of the electric drive axle without affecting the compact structure of the electric drive axle. Summary of the Utility Model

[0004] The purpose of the utility model is to provide a differential integrated with a two-speed planetary gear reduction structure in view of the deficiencies of the prior art.

[0005] The utility model is realized by adopting the following technical scheme:

[0006] A differential with a shifting function includes a power input shaft, a main power transmission gear ring, a sliding meshing sleeve, a fixed support, a gear ring, and a differential case. One end of the power input shaft is provided with a sun gear. A planetary gear is arranged between the sun gear and the gear ring. The gear ring is arranged on the outer periphery of a gear ring support. One end of the gear ring support is provided with an intermediate power transmission gear ring. A fixed support is arranged on the left side of the intermediate power transmission gear ring. A main power transmission gear ring is arranged on the right side of the intermediate power transmission gear ring. The outer periphery of the intermediate power transmission gear ring is connected to the sliding meshing sleeve through splines. The sliding meshing sleeve is in transmission connection with the fixed support or the main power transmission gear ring.

[0007] Furthermore, the differential case includes a right differential case and a left differential case, the right differential case and the left differential case are fixedly connected, and the inner cavity after the right differential case and the left differential case are fixedly connected is provided with half shaft gears and a cross shaft, and the cross shaft is provided with planetary bevel gears.

[0008] Furthermore, the right differential case includes a planetary reducer housing and a differential housing, a communication oil passage is provided between the planetary reducer housing and the differential housing, the planetary reducer housing is provided with a planetary wheel shaft mounting hole, and the planetary wheel shaft mounting hole is provided with a planetary wheel shaft.

[0009] Furthermore, the planetary wheel shaft is arranged in the planetary wheel shaft mounting hole and axially positioned by a limit pin.

[0010] Furthermore, the planetary gear is sleeved on the planetary wheel shaft, and a rolling assembly is provided between the planetary wheel shaft and the planetary gear.

[0011] Furthermore, the ring gear and the ring gear bracket are connected by a spline and axially limited by a limit snap ring, and a support bearing is provided between the ring gear and the ring gear bracket.

[0012] Compared with the prior art, the utility model has the following beneficial technical effects:

[0013] 1. Compact structure: The planetary reduction structure is adopted, effectively realizing a smaller radial dimension. At the same time, the differential housing and the planetary reduction housing are integrally designed, effectively reducing the axial dimension of the differential.

[0014] 2. Two-speed transmission and excellent working condition adaptability: By integrating a two-speed planetary row reduction mechanism on the basis of the conventional differential structure, the two-speed ratio adjustment of the differential is realized. At the same time, the speed ratio increases significantly in the low-speed gear (the speed ratio is larger than that of the parallel shaft reduction planetary reduction), and the power performance is more excellent, thus realizing more excellent working condition adaptability. BRIEF DESCRIPTION OF THE DRAWINGS

[0015] Figure 1 is a structural schematic diagram of the utility model;

[0016] Figure 2 is a sectional structural schematic diagram of the utility model;

[0017] Figure 3 is a structural schematic diagram of the right differential case of the utility model;

[0018] Figure 4 is a schematic diagram of the differential transmission route of the utility model;

[0019] Figure 5 is a schematic diagram of the differential transmission route in the low-speed gear of the utility model;

[0020] Figure 6 This is a schematic diagram of the transmission route of the differential in high gear of the present utility model.

[0021] Reference numerals

[0022] 1. Power input shaft; 2. Driving force transmission gear ring; 3. Sliding engagement sleeve; 4. Fixed support; 5. Gear ring; 6. Right differential housing; 61. Differential housing; 62. Planetary reducer housing; 63. Connecting oil passage; 64. Planetary gear shaft mounting hole; 7. Left differential housing; 8. Intermediate power transmission gear ring; 9. Limit snap ring; 10. Gear ring support; 11. Planetary gear shaft; 12. Rolling assembly; 13. Planetary gear; 14. Limit pin; 15. Cross shaft; 16. Planetary bevel gear; 17. Half shaft gear; 18. Sun gear; 19. Support bearing. Specific embodiments

[0023] In order to enable those skilled in the art to better understand the technical solutions in the present utility model, the following will clearly and completely describe the technical solutions in the embodiments of the present utility model with reference to the accompanying drawings in the embodiments of the present utility model. Obviously, the described embodiments are only a part of the embodiments of the present utility model, rather than all the embodiments. Based on the embodiments of the present utility model, all other embodiments obtained by those of ordinary skill in the art without creative efforts shall fall within the protection scope of the present utility model.

[0024] Embodiment 1

[0025] As Figures 1 - 3 shown, a differential integrated with a two-speed planetary row reduction structure includes a power input shaft 1, a driving force transmission gear ring 2, a sliding engagement sleeve 3, a fixed support 4, a gear ring 5 and a differential housing. A sun gear 18 is provided at one end of the power input shaft 1. A planetary gear 13 is provided between the sun gear 18 and the gear ring 5. The gear ring 5 is provided on the outer periphery of the gear ring support 10. An intermediate power transmission gear ring 8 is provided at one end of the gear ring support 10. A fixed support 4 is provided on the left side of the intermediate power transmission gear ring 8. A driving force transmission gear ring 2 is provided on the right side of the intermediate power transmission gear ring 8. The outer periphery of the intermediate power transmission gear ring 8 is connected to the sliding engagement sleeve 3 through a spline. The sliding engagement sleeve 3 is in transmission connection with the fixed support 4 or the driving force transmission gear ring 2.

[0026] The differential housing includes a right differential housing 6 and a left differential housing 7. The right differential housing 6 and the left differential housing 7 are fixedly connected. The inner cavity after the right differential housing 6 and the left differential housing 7 are fixedly connected is provided with a half shaft gear 17 and a cross shaft 15. The cross shaft 15 is provided with a planetary bevel gear 16.

[0027] The right differential housing 6 includes a planetary reducer housing 62 and a differential housing 61. A connecting oil passage 63 is provided between the planetary reducer housing 62 and the differential housing 61. The planetary reducer housing 62 is provided with a planetary gear shaft mounting hole 64, and a planetary gear shaft 11 is arranged in the planetary gear shaft mounting hole 64.

[0028] The planetary gear shaft 11 is arranged in the planetary gear shaft mounting hole 64 and is axially positioned by a limit pin 14.

[0029] The planetary gear shaft 11 is sleeved with a planetary gear 13, and a rolling component 12 is provided between the planetary gear shaft 11 and the planetary gear 13.

[0030] The ring gear 5 and the ring gear bracket 10 are connected by a spline and axially limited by a limit snap ring 9. A support bearing 19 is provided between the ring gear 5 and the ring gear bracket 10.

[0031] Embodiment 2

[0032] The power transmission route of the present utility model is as follows:

[0033] When the power is disconnected, as Figure 4 shown, the sliding meshing sleeve 3 is in the middle position and meshes with the intermediate power transmission ring gear 8. The sun gear 18, the planetary gear 13, and the ring gear 5 are all in a free rotation state, and power transmission cannot be achieved, thus realizing power disconnection;

[0034] In the low gear, as Figure 5 shown, the sliding meshing sleeve 3 is in the left position, connecting the intermediate power transmission ring gear 8 with the fixed support 4, thereby fixing the ring gear 5 through the ring gear bracket 10; thus, the power is transmitted from the power input shaft 1 to the sun gear 18, and the transmission is decelerated through the meshing of the planetary gear 13 and the ring gear 5. Then, the planetary gear shaft 11 transmits the power to the right differential housing 6, and then the power is transmitted to the cross shaft 15 and the planetary bevel gear 16. Finally, the planetary bevel gear 16 distributes the power to the left and right half shaft gears 17 as required;

[0035] In the high gear, as Figure 6 shown, the sliding meshing sleeve 3 is in the right position, connecting the intermediate power transmission ring gear 8 with the main power transmission ring gear 2, thereby ensuring that the ring gear 5 and the power input shaft 1 have the same rotational speed, that is, the ring gear 5 and the sun gear 18 have the same rotational speed. At this time, the planetary reducer cannot play a decelerating role and only has a transmission role; thus, after the power is transmitted from the power input shaft 1 to the sun gear 18, the power is directly transmitted to the right differential housing 6 through the planetary gear shaft 11, and then the power is transmitted to the cross shaft 15 and the planetary bevel gear 16. Finally, the planetary bevel gear 16 distributes the power to the left and right half shaft gears 17 as required.

Claims

1. A differential with an integrated two-speed planetary gear reduction structure, characterized in that: The invention comprises a power input shaft (1), a main power transmission ring gear (2), a sliding meshing sleeve (3), a fixed support (4), a ring gear (5) and a differential case. A sun gear (18) is provided at one end of the power input shaft (1), a planetary gear (13) is provided between the sun gear (18) and the ring gear (5), the ring gear (5) is arranged on the outer periphery of a ring gear support (10), an intermediate power transmission ring gear (8) is provided at one end of the ring gear support (10), a fixed support (4) is provided on the left side of the intermediate power transmission ring gear (8), a main power transmission ring gear (2) is provided on the right side of the intermediate power transmission ring gear (8), the outer periphery of the intermediate power transmission ring gear (8) is connected to the sliding meshing sleeve (3) via a spline, and the sliding meshing sleeve (3) is drivingly connected to the fixed support (4) or the main power transmission ring gear (2).

2. The differential with integrated two-speed planetary gear reduction structure according to claim 1, characterized in that: The differential case comprises a right differential case (6) and a left differential case (7), wherein the right differential case (6) is fixedly connected to the left differential case (7), and an inner cavity after the right differential case (6) and the left differential case (7) are fixedly connected is provided with a half-axle gear (17) and a cross shaft (15), and the cross shaft (15) is provided with a planetary bevel gear (16).

3. The differential with integrated two-speed planetary gear reduction structure according to claim 2, characterized in that: The right differential housing (6) comprises a planetary reducer housing (62) and a differential housing (61), a connecting oil passage (63) is provided between the planetary reducer housing (62) and the differential housing (61), the planetary reducer housing (62) is provided with a planetary wheel shaft mounting hole (64), and the planetary wheel shaft mounting hole (64) is provided with a planetary wheel shaft (11).

4. The differential with integrated two-speed planetary gear reduction structure according to claim 3, characterized in that: The planetary wheel shaft (11) is arranged in the planetary wheel shaft mounting hole (64) and is axially positioned by a limiting pin (14).

5. The differential with integrated two-speed planetary gear reduction structure according to claim 4, characterized in that: The planetary gear (13) is sleeved on the planetary gear shaft (11), and a rolling assembly (12) is provided between the planetary gear shaft (11) and the planetary gear (13).

6. The differential with integrated two-speed planetary gear reduction structure according to claim 4, characterized in that: The gear ring (5) and the gear ring bracket (10) are connected via a spline and are axially limited by a limiting retaining spring (9); a supporting bearing (19) is provided between the gear ring (5) and the gear ring bracket (10).

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