CN222085070U - Differentials, drive axles and vehicles - Google Patents

Abstract

The utility model discloses a differential, a drive axle and a vehicle, wherein the differential comprises a cross shaft, a planetary gear, a side gear and a side gear, a rotating shaft part is formed at the end part of the cross shaft, a gear hole is formed in the center of the planetary gear, the gear hole is sleeved on the rotating shaft part and can rotate relative to the rotating shaft part, the side gear is positioned on two sides of the planetary gear and meshed with the planetary gear, a first reducing section and a second reducing section are formed at two axial ends of the gear hole, the first reducing section and the second reducing section are connected at the middle part of the axial direction of the gear hole, one end of the first reducing section in the straight direction of the gear hole is gradually increased, and the other end of the second reducing section in the straight direction of the gear hole is gradually increased. The differential mechanism provided by the embodiment of the utility model has the advantages of improving the smoothness of connection, reducing the failure rate and the like.

Description

Differential mechanism, drive axle and vehicle

Technical Field

The utility model relates to the technical field of vehicles, in particular to a differential mechanism, a drive axle and a vehicle.

Background

The differential mechanism transmits different rotation speeds to the front and rear through shafts and the left and right half shafts through the rotation of the inner planetary gears around the cross shaft. However, when the fit clearance is too large, faults such as looseness and abnormal sound can be generated due to impact, when the fit clearance is too small, faults such as abrasion of the cross shaft and shaft diameter breakage can be generated when lubrication is poor, the fault rate of the differential mechanism is increased, and tight fit and lubrication effects cannot be considered.

Disclosure of utility model

The present utility model aims to solve at least one of the technical problems existing in the prior art. Therefore, an object of the present utility model is to provide a differential gear having advantages of improved smoothness of connection and reduced failure rate.

The utility model also provides a drive axle with the differential mechanism.

The utility model also provides a vehicle with the drive axle.

In order to achieve the aim, according to the embodiment of the utility model, a differential is provided, which comprises a cross shaft, a planetary gear, a side gear and a side gear, wherein a rotating shaft part is formed at the end part of the cross shaft, a gear hole is formed at the center of the planetary gear, the gear hole is sleeved on the rotating shaft part and can rotate relative to the rotating shaft part, the side gear is positioned at two sides of the planetary gear and meshed with the planetary gear, a first reducing section and a second reducing section are formed at two ends of the gear hole along the axial direction, the first reducing section and the second reducing section are connected at the middle part of the gear hole along the axial direction, one end of the first reducing section in the radial direction of the gear hole is gradually increased, and the other end of the second reducing section in the radial direction of the gear hole is gradually increased.

According to the differential mechanism provided by the embodiment of the utility model, the end part of the cross shaft is provided with four rotating shaft parts, the center of the planetary gear is provided with a gear hole, and the gear hole is sleeved on the rotating shaft parts and can rotate relative to the rotating shaft parts. The gear hole forms a variable gap between different axial positions of the gear hole and the planetary gear through forming a first variable diameter section and a second variable diameter section along the portions of the two ends of the axial direction, namely the gap between the gear hole and the two ends of the rotating shaft part is larger, and the gap in the middle of the axial direction is smaller. Therefore, for the connection mode of the cross shaft and the planet gears with medium gaps in the prior art, gradual change of the gaps can be realized at the two ends of the connection, the gaps between the first reducing section and the second reducing section and the rotating shaft part are larger at the two ends of the gear hole, the addition and the flow of lubricating oil can be realized, the lubricating oil can be better guided to flow to the axial middle part, the connection smoothness between the planet gears and the cross shaft in the rotation process is ensured, the friction and the resistance are reduced, and the transmission efficiency is improved. The gap between the gear hole and the axial middle part of the rotating shaft part is smaller, so that the stability of connection between the cross shaft and the planetary gear is ensured, the shaking effect caused by overlarge gap is reduced, the power is effectively transmitted, the differential function is realized, and the overall reliability of the differential mechanism is improved. In addition, in the planetary gear installation process, as the gaps between the two ends of the rotating shaft part and the gear holes are larger, the gaps between the rotating shaft part and the middle part of the rotating shaft part are gradually reduced, and the planetary gear is easier to install in place along the installation direction, so that the occurrence of loose conditions is reduced, and abnormal sound caused by the gaps is prevented.

Therefore, the differential mechanism provided by the embodiment of the utility model has the advantages of improving the smoothness of connection, reducing the failure rate and the like.

According to some embodiments of the utility model, the gear hole is formed with an equal diameter section between the first and second variable diameter sections, the diameter of the equal diameter section remains unchanged, and the diameters of the first and second variable diameter sections are not smaller than the diameter of the equal diameter section.

According to some embodiments of the utility model, the axial dimensions of the first and second reducing segments are each smaller than the axial dimensions of the constant diameter segment.

According to some embodiments of the utility model, the inner contour lines of the longitudinal sections of the first and second reducing segments are each configured as an arc.

According to some embodiments of the utility model, the diameter of the arc formed by the inner longitudinal section contour of the first reducing section is greater than the diameter of the arc formed by the inner longitudinal section contour of the second reducing section.

According to some embodiments of the utility model, an outer circumferential surface of the rotating shaft portion of the cross shaft is configured with an oil guiding plane extending along an axial direction thereof, and an oil guiding gap is formed between the oil guiding plane and the gear hole.

According to some embodiments of the utility model, the oil guiding plane is formed on two diametrically opposite sides of the cross.

According to some embodiments of the utility model, the cross is configured with a first step at a root of the spindle portion, and the gear hole is configured with a second step that mates with the first step.

An embodiment according to a second aspect of the utility model provides a drive axle comprising a final drive, a drive axle housing, and a differential according to the above embodiment of the utility model mounted in the final drive, the final drive being connected to the drive axle housing by fasteners, and the planetary gears being in driving connection with the side gears.

The drive axle provided by the embodiment of the utility model has the advantages of improving the smoothness of connection, reducing the failure rate and the like by utilizing the differential mechanism provided by the embodiment of the utility model.

An embodiment according to a second aspect of the utility model proposes a vehicle comprising a drive axle according to the above-described embodiment of the utility model.

According to the vehicle disclosed by the embodiment of the utility model, the advantages of improving the smoothness of connection, reducing the failure rate and the like are achieved by utilizing the drive axle disclosed by the embodiment of the utility model.

Additional aspects and advantages of the utility model will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the utility model.

Drawings

The foregoing and/or additional aspects and advantages of the utility model will become apparent and may be better understood from the following description of embodiments taken in conjunction with the accompanying drawings in which:

FIG. 1 is a schematic view of the structure of a planetary gear of a differential according to an embodiment of the present utility model;

FIG. 2 is an enlarged partial schematic view of FIG. 1A;

FIG. 3 is a schematic structural view of a spider of a differential according to an embodiment of the present utility model;

fig. 4 is a schematic structural view of a spider shaft portion of a differential according to an embodiment of the present utility model.

Reference numerals:

cross 100, planetary gear 200, spindle portion 110, gear hole 210, first diameter-changing section 211,

A second reducing section 212, an equal diameter section 213, an oil guiding plane 101, a first step 102, and a second step 202.

Detailed Description

Embodiments of the present utility model are described in detail below, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to like or similar elements or elements having like or similar functions throughout. The embodiments described below by referring to the drawings are illustrative only and are not to be construed as limiting the utility model.

In the description of the present utility model, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "axial", "radial", "circumferential", etc. indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings are merely for convenience in describing the present utility model and to simplify the description, and do not indicate or imply that the device or element being referred to must have a specific orientation, be configured and operated in a specific orientation, and therefore should not be construed as limiting the present utility model.

In the description of the utility model, a "first feature" or "second feature" may include one or more of such features.

In the description of the utility model, "a plurality" means two or more, and "a number" means one or more.

A differential 1 according to an embodiment of the present utility model is described below with reference to the drawings.

As shown in fig. 1-4, a differential in accordance with an embodiment of the present utility model includes a cross 100, a planetary gear 200, and a side gear.

The end of the cross 100 is configured with a shaft portion 110. The planetary gear 200 is provided with a gear hole 210 at the center, and the gear hole 210 is sleeved on the rotating shaft 110 and is rotatable relative to the rotating shaft 110. The side gears are located on both sides of the planetary gears 200, and the side gears are engaged with the planetary gears 200. Wherein, a first reducing section 211 and a second reducing section 212 are formed at two axial ends of the gear hole 210, the first reducing section 211 and the second reducing section 212 are connected at the axial middle of the gear hole 210, the diameter of the first reducing section 211 gradually increases towards one end of the gear hole 210, and the diameter of the second reducing section 212 gradually increases towards the other end of the gear hole 210.

For example, the two ends of the gear hole 210 form a first reducing section 211 and a second reducing section 212, the diameters of the positions between the first reducing section 211 and the second reducing section 212 are kept unchanged, and the centers of the first reducing section 211 and the second reducing section 212 coaxially extend to realize the diameter-changing structure of the gear hole 210.

According to the differential of the embodiment of the present utility model, four rotating shaft portions 110 are configured at the end portions of the cross shaft 100, a gear hole 210 is configured at the center of the planetary gear 200, and the gear hole 210 is sleeved on the rotating shaft portions 110 and can rotate relative to the rotating shaft portions 110. The portions of the gear hole 210 at both ends in the axial direction form variable gaps between axially different positions of the gear hole 210 and the planetary gear 200 by forming the first variable diameter section 211 and the second variable diameter section 212, that is, the gaps between the gear hole 210 and both ends of the rotating shaft portion 110 are larger, and the gaps in the axial middle portion are smaller. Therefore, for the connection mode of the cross shaft 100 and the planetary gear 200 with medium gaps in the prior art, gradual change of the gaps can be realized at the two ends of the connection, and the gaps between the first reducing section 211 and the second reducing section 212 and the rotating shaft part 110 are larger at the two end parts which are gradually close to the gear hole 210, so that the addition and the flow of lubricating oil can be realized, the lubricating oil can be better guided to flow to the axial middle part, the connection smoothness between the planetary gear 200 and the cross shaft 100 in the rotation process is ensured, the friction and the resistance are reduced, and the transmission efficiency is improved. The gap between the gear hole 210 and the axial middle part of the rotating shaft part 110 is smaller, so that the stability of the connection between the cross shaft 100 and the planetary gear 200 is ensured, the shaking effect caused by overlarge gap is reduced, the power is effectively transmitted, the differential function is realized, and the integral reliability of the differential is improved. In addition, in the installation process of the planetary gear 200, because the gaps between the two ends of the rotating shaft part 110 and the gear holes 210 are larger, the gaps gradually shrink towards the middle of the rotating shaft part 110, and the planetary gear 200 is easier to install in place along the installation direction, so that the occurrence of the loose condition is reduced, and abnormal noise caused by the existence of the gaps is prevented.

Therefore, the differential mechanism provided by the embodiment of the utility model has the advantages of improving the smoothness of connection, reducing the failure rate and the like.

In some embodiments of the present utility model, as shown in fig. 2, the gear hole 210 is formed with an equal diameter section 213 between the first variable diameter section 211 and the second variable diameter section 212, the diameter of the equal diameter section 213 remains unchanged, and the diameters of the first variable diameter section 211 and the second variable diameter section 212 are not smaller than the diameter of the equal diameter section 213.

Because the first reducing section 211 and the second reducing section 212 have larger sizes, the diameter of the equal-diameter section 213 is smaller, and the equal-diameter section 213 can be more tightly matched with the rotating shaft 110, so that the shaking and abnormal noise phenomenon can be avoided in the operation process of the differential mechanism. Through the proper size design of the constant diameter section 213, the mutual friction and interference between the parts can be effectively reduced, the stable matching and operation between the parts are maintained, and the working efficiency and the service life of the differential mechanism are improved. Meanwhile, the sizes of the first reducing section 211 and the second reducing section 212 are gradually increased towards the two ends, so that more lubricating oil can be respectively contained at the two ends of the differential mechanism while proper gaps are ensured, and the lubricating oil is ensured to be lubricated in place. By accommodating more lubrication oil through the larger gap between the two end portions of the rotating shaft portion 110, wear and friction between the parts can be reduced, energy loss can be reduced, the service life of the differential can be prolonged, and stability and reliability of the transmission system can be ensured.

In some embodiments of the present utility model, as shown in FIG. 2, the axial dimensions of both the first and second variable diameter sections 211, 212 are less than the axial dimensions of the constant diameter section 213.

Wherein R1 in fig. 2 represents the axial dimension of the first reducing section, and R2 represents the axial dimension of the second reducing section. Thus, the constant diameter section 213 may extend a longer length, better fitting in the middle of the shaft portion 110. The contact area of the gear hole 210 and the rotating shaft portion 110 is large, and the stability of rotation of the planetary gear 200 is improved. The axial dimensions of the first reducing section 211 and the second reducing section 212 are smaller, so that the wobble of the planetary gear 200 is reduced, the guiding distance of the first reducing section 211 and the second reducing section 212 to the lubricating oil is shorter, and the lubricating oil only needs to be guided to the equal-diameter section 213 from two ends.

In some embodiments of the present utility model, as shown in fig. 2, the inner contour lines of the longitudinal sections of the first and second variable diameter sections 211 and 212 are each configured in an arc shape.

The first and second variable diameter sections 211 and 212 each form a gradual gap with the shaft portion 110. The arc-shaped inner contour line can better guide lubricating oil to flow to the middle part, optimize lubrication between the cross shaft 100 and the planetary gear 200, improve the smoothness of connection between the cross shaft 100 and the planetary gear 200, reduce abrasion between parts and prolong the service life of the differential mechanism. And, the transition between the first reducing section 211 and the second reducing section 212 and the equal diameter section can be smoother, which is beneficial to the assembly and rotation stability of the planetary gear 200

In some embodiments of the present utility model, the diameter of the arc formed by the longitudinal section inner contour of the first reducing section 211 is greater than the diameter of the arc formed by the longitudinal section inner contour of the second reducing section 212. In other words, the diameter of the first variable diameter section 211 has a smaller tendency, and the diameter of the second variable diameter section 212 has a larger tendency. Wherein, first reducing section 211 and constant diameter section smooth transition link to each other, and second reducing section 212 and constant diameter section smooth transition link to each other, through the radian that designs first reducing section 211 and second reducing section 212 longitudinal section respectively, and the diameter change range of second reducing section 212 is bigger at the end of packing into, can hold more lubricating oil at planetary gear 200 root, more fully lubricate, when guaranteeing planetary gear 200 rotation stability, help reducing the friction between the spare part.

In some embodiments of the present utility model, as shown in fig. 3 and 4, the outer circumferential surface of the rotating shaft portion of the cross 100 is configured with an oil guiding plane 101 extending in the axial direction thereof, and an oil guiding gap is formed between the oil guiding plane 101 and the gear hole 210. The presence of the oil guiding plane 101 helps to guide the flow of the lubricating oil in the axial direction and form an effective lubricating film on the outer peripheral surface of the rotating shaft portion of the cross 100, reducing the direct contact of the metal surfaces, helping to reduce friction and wear, and improving the service life of the components. Meanwhile, the structure of the oil guide gap can promote better flow of lubricating oil, so that the differential mechanism moves more stably, and comfort and stability of a vehicle are improved.

In some embodiments of the present utility model, as shown in fig. 3 and 4, oil guiding planes 101 are formed on diametrically opposite sides of the cross 100. For example, the oil guiding plane 101 extends along two radial sides of the cross 100, so as to help the lubricating oil form a uniform lubricating film on the entire outer peripheral surface of the cross 100, and provide a more comprehensive and uniform lubricating effect. This helps reduce friction and wear, protects the cross-shaft 100 surface from damage, improves work efficiency, and prolongs the service life of the components.

Meanwhile, the wear and damage risks of parts can be reduced through uniform lubrication and effective cooling, and the maintenance and replacement cost is reduced. Through optimizing the lubrication system design, the service life of the differential mechanism can be prolonged, the maintenance frequency is reduced, and the maintenance cost of the vehicle is reduced.

In some embodiments of the present utility model, as shown in fig. 1 and 3, the cross 100 is configured with a first step 102 at the root of the spindle portion and the gear hole 210 is configured with a second step 202 that mates with the first step 102.

The right position between the cross 100 and the gear hole 210 can be ensured by the cooperation between the first step part 102 and the second step part 211, and the cross 100 and the planetary gear 200 can be effectively fixed at the right position by the structural design of the first step part 102 and the second step part 202, so that the normal operation of the transmission system is ensured. And through the cooperation design of first step portion 102 and second step portion 202, can effectively reduce the clearance between cross axle 100 and the planetary gear 200, improve transmission system's precision and stability, reduce clearance can reduce friction and wearing and tearing, can reduce the relative movement between the spare part simultaneously, reduce energy loss, improve transmission efficiency, help the vehicle to run more steadily and reliably under various road conditions.

A transaxle according to an embodiment of the present utility model is described below.

The driving axle comprises a main speed reducer, a driving axle housing and the differential mechanism according to the embodiment of the utility model, wherein the differential mechanism is arranged in the main speed reducer, the main speed reducer is connected with a driving axle housing fastener, and the planetary gear is in transmission connection with the side gear.

The main speed reducer is usually positioned in a drive axle and is responsible for increasing output torque by reducing input rotation speed so as to realize the adjustment and output of power by a transmission system. The final drive utilizes an internal gear assembly to transfer input power to other components of the drive axle. The differential is a key component in the drive axle, when the vehicle turns, the inner side wheels and the outer side wheels are required to have different rotating speeds, the differential can adjust the rotating speed difference of the wheels through the planetary gear system, the normal running of the wheels is ensured, and the damage of the drive components and the vehicle structure is reduced. The planetary gear is in transmission connection with the main speed reducer, so that power transmission is realized. The planetary gear system comprises a sun gear, a planet carrier and other components, and the power distribution and the rotation speed adjustment of the drive axle are realized through the gear cooperation between the sun gear, the planet gear and the planet carrier.

When power is transmitted into the main speed reducer, the main speed reducer can reduce the input power rotating speed and transmit the power rotating speed to the differential mechanism. The planetary gear system in the differential mechanism can adjust the rotation speed difference of wheels according to the running state and the steering condition of the vehicle, so that the normal running and steering of the vehicle are ensured. The driving axle can effectively adjust the power output through the transmission connection of the planetary gear and the main speed reducer, and the stability and the running performance of the vehicle are ensured.

According to the drive axle of the embodiment of the utility model, the differential mechanism of the embodiment of the utility model has the advantages of improving the smoothness of connection, reducing the failure rate and the like.

A vehicle according to an embodiment of the present utility model is described below.

A vehicle according to an embodiment of the present utility model includes a transaxle according to the above-described embodiment of the present utility model.

According to the vehicle of the embodiment of the utility model, by utilizing the drive axle according to the embodiment of the utility model, the advantages of improving the smoothness of connection, reducing the failure rate and the like are achieved.

Other constructions and operations according to embodiments of the present utility model are known to those of ordinary skill in the art and will not be described in detail herein.

In the description of the present specification, reference to the terms "one embodiment," "some embodiments," "illustrative embodiments," "examples," "specific examples," or "some examples," etc., means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the utility model. In this specification, schematic representations of the above terms do not necessarily refer to the same embodiments or examples.

Although embodiments of the present utility model have been shown and described, it will be understood by those skilled in the art that various changes, modifications, substitutions and alterations can be made therein without departing from the spirit and scope of the utility model as defined by the appended claims and their equivalents.

Claims (10)

1. A differential mechanism for a vehicle, comprising a differential mechanism, characterized by comprising the following steps:

A cross shaft, wherein a rotating shaft part is configured at the end part of the cross shaft;

The planetary gear is provided with a gear hole at the center, and the gear hole is sleeved on the rotating shaft part and can rotate relative to the rotating shaft part;

A side gear located on both sides of the planetary gear, the side gear being engaged with the planetary gear;

The gear hole comprises a gear hole body, wherein a first reducing section and a second reducing section are formed at two axial ends of the gear hole body, the first reducing section and the second reducing section are connected at the middle part of the gear hole body in the axial direction, the diameter of the first reducing section is gradually increased to one end of the gear hole body, and the diameter of the second reducing section is gradually increased to the other end of the gear hole body.

2. The differential of claim 1, wherein the gear bore defines an equal diameter section between the first and second variable diameter sections, the equal diameter section having a constant diameter, and wherein neither the first nor second variable diameter section has a diameter less than the equal diameter section.

3. The differential of claim 2, wherein the axial dimensions of the first and second reducing segments are each less than the axial dimensions of the constant diameter segments.

4. The differential of claim 1, wherein the inner contour of the longitudinal sections of the first and second reducing segments are each configured as an arc.

5. The differential of claim 4, wherein the diameter of the arc formed by the longitudinal section inner contour of the first reducing section is greater than the diameter of the arc formed by the longitudinal section inner contour of the second reducing section.

6. The differential of claim 1, wherein an outer peripheral surface of the rotating shaft portion of the cross is configured with an oil guiding plane extending in an axial direction thereof, and an oil guiding gap is formed between the oil guiding plane and the gear hole.

7. The differential of claim 6, wherein the oil guiding planes are formed on diametrically opposite sides of the cross.

8. The differential of claim 1, wherein the cross is configured with a first step at a root portion of the rotating shaft portion, and the gear hole is configured with a second step that mates with the first step.

9. A drive axle, comprising:

a main speed reducer;

a drive axle housing;

The differential of any one of claims 1-8 mounted in the final drive, the final drive being connected to the transaxle housing fastener and the planet gears being in driving connection with the side gears.

10. A vehicle comprising a drive axle according to claim 9.