CN217207608U

CN217207608U - Anti-gluing low-noise quasi-zero backlash torque vector differential mechanism

Info

Publication number: CN217207608U
Application number: CN202220960710.9U
Authority: CN
Inventors: 焦继松; 赵文楚; 王小乾; 苟文星; 赵军华; 戴辉
Original assignee: Pacific Precision Powertrain Co ltd; Jiangsu Pacific Precision Forging Co Ltd
Current assignee: Pacific Precision Powertrain Co ltd; Jiangsu Pacific Precision Forging Co Ltd
Priority date: 2022-04-25
Filing date: 2022-04-25
Publication date: 2022-08-16
Anticipated expiration: 2032-04-25

Abstract

The utility model relates to the technical field of differential mechanisms, in particular to an anti-gluing low-noise quasi-zero backlash torque vector differential mechanism, which comprises a large-end differential shell and a small-end differential shell which are detachably connected; the large end difference shell and the small end difference shell are enclosed to form an installation cavity; a first half shaft gear and a second half shaft gear are coaxially and rotatably arranged on the inner side of the mounting cavity, and a plurality of planet gears are meshed and connected between the first half shaft gear and the second half shaft gear; a first half shaft gear is positioned at one end close to the small end differential shell, a second half shaft gear is positioned at one end close to the large end differential shell, and a flat gasket and an elastic element are respectively arranged between the first half shaft gear and the small end differential shell and between the second half shaft gear and the large end differential shell; the elastic element is positioned on one side of the flat gasket, which is close to the first axle gear. The requirement of quasi-zero backlash can be met, gear jamming caused by rotation of the gear set is prevented, and gear shifting impact or meshing impact is absorbed by the differential mechanism after loading is guaranteed.

Description

Anti-gluing low-noise quasi-zero backlash torque vector differential mechanism

Technical Field

The utility model relates to a differential mechanism technical field especially relates to an accurate zero side gap torque vector differential mechanism of anti veneer low noise.

Background

As is well known, a typical differential assembly is composed of a differential shell, a half axle gear, a planetary shaft, a planetary gear gasket, a half axle gear gasket, a pin and other parts, is used as an essential unit of an automobile power transmission system, and is used for realizing the movement of left and right half axles of an automobile at different rotating speeds and avoiding the slip phenomenon of wheels. The performance of the differential directly influences the performance of the whole vehicle, and the differential is a key component in the differential, and the distribution of the torque and the strength of each component directly determine the steering performance, the trafficability characteristic and the reliability of the vehicle.

With the introduction of macro policies such as energy conservation and emission reduction, carbon synthesis and carbon peak reaching, the market of new energy vehicles mainly represented by pure electric vehicles is vigorously developed to promote the revolution of the vehicle transmission system, and brand-new requirements of the differential on structural design, functional requirements and the like are caused. The first is that: the design development of the new energy automobile gearbox is developed towards miniaturization and light weight; in sharp contrast, the new energy automobile has higher and higher requirements on torque, namely, the torque bearing ratio in unit volume is improved; secondly, the following steps: the high-speed slip working condition of the new energy automobile is much more harsh than that of the traditional fuel oil automobile, and the case that the bevel gear set is glued and locked frequently occurs under the running working condition; thirdly, the method comprises the following steps: due to the simplification of a power transmission structure of the new energy vehicle, the function of the differential in a power system transmission chain is more prominent, the noise of the differential is a main source of the transmission system, and the design of reducing the noise of the differential is a great problem of the new energy vehicle. Research confirms that the differential assembly clearance is the first major source causing the differential motion noise, and the general solution is to achieve the purpose of reducing the assembly clearance (which can be reduced from about 1.5 degrees to about 1 degree) by a method of strictly controlling the tolerance of each sub-part and improving the precision grade of a bevel gear, but obviously, the method increases the manufacturing cost, and the phenomenon of rotation locking is easily caused after the differential assembly clearance is reduced, thereby limiting the possibility of further reduction of the clearance: assembly backlash below 1 ° has been difficult to achieve.

SUMMERY OF THE UTILITY MODEL

Technical problem to be solved

The utility model provides a not enough to prior art, the utility model provides an anti veneer low noise quasi-zero backlash moment of torsion vector differential mechanism can reach the requirement of quasi-zero backlash, and the gear card that causes when preventing the gear train from rotating dies, guarantees simultaneously that differential mechanism absorbs behind the loading and shifts and strike or the meshing is strikeed.

(II) technical scheme

In order to achieve the above object, an embodiment of the present application provides an anti-gluing low-noise quasi-zero backlash torque vector differential, which includes a large end differential case and a small end differential case that are detachably connected; the large end difference shell and the small end difference shell are enclosed to form an installation cavity; a first half shaft gear and a second half shaft gear are coaxially and rotatably arranged on the inner side of the installation cavity, and a plurality of planet gears are connected between the first half shaft gear and the second half shaft gear in a meshing manner; the first half shaft gear is positioned at one end close to the small end differential shell, a first shaft connecting hole concentric with the rotation axis of the first half shaft gear is formed in the small end differential shell, the second half shaft gear is positioned at one end close to the large end differential shell, and a second shaft connecting hole concentric with the rotation axis of the second half shaft gear is formed in the large end differential shell; flat gaskets and elastic elements are respectively arranged between the first half shaft gear and the small end difference shell and between the second half shaft gear and the large end difference shell; the elastic element is positioned on one side of the flat gasket, which is close to the first axle gear.

Preferably, an annular mounting part is formed at one end of the small end difference shell close to the large end difference shell; the mounting part is positioned on the inner side of the large-end difference shell; a cross-shaped mounting shaft assembly is detachably mounted on the inner side of the mounting part; the mounting shaft assembly is rotatably connected with a plurality of planetary gears.

Preferably, a horizontal fixed disc is formed on the outer side of the mounting part, and the fixed disc is parallel to the mounting shaft assembly; the fixed disc, the large-end difference shell and the main reduction gear are detachably and fixedly connected.

Preferably, the mounting shaft assembly comprises a long linear shaft and two short linear shafts; the middle part of the long straight shaft is sleeved with a shaft sleeve, and short shaft connecting holes are respectively formed on the outer side of the shaft sleeve and perpendicular to the two sides of the long straight shaft; one ends of the two short straight shafts close to the long straight shaft are respectively inserted into the short shaft connecting holes; four third axle connecting holes are formed in the mounting portion, and the outer ends of the long straight shaft and the short straight shaft are connected with the third axle connecting holes respectively.

Preferably, the elastic member comprises a general spring or a belleville spring.

Preferably, a step is formed on one side of the large end difference shell close to the small end difference shell, and the mounting part abuts against the step.

Preferably, the mounting portion is provided with four first mounting holes penetrating through the mounting portion, and each first mounting hole is communicated with one third shaft connecting hole; the first mounting hole is vertical to the mounting shaft assembly; second mounting holes are formed in one ends, located in the third shaft connecting holes, of the long straight shaft and the short straight shaft respectively, the first mounting holes and the second mounting holes can rotate to the concentric position, and the first mounting holes and the second mounting holes penetrate through the first mounting holes and the second mounting holes and are connected with locking pins.

(III) advantageous effects

The utility model provides an anti accurate zero backlash moment of torsion vector differential mechanism of veneer low noise through setting up in inboard plain washer and the elastic element of installation cavity, can accomplish 0 ~0.2 with the differential mechanism assembly clearance, reaches the requirement of accurate zero backlash promptly. The flat gasket is used for adjusting the gap, the common flat gasket can also protect the differential case and prevent the differential case from being abraded, and the elastic element is used for preventing the gear from being locked when the gear set rotates and ensuring that the differential absorbs gear shifting impact or meshing impact after the differential case is loaded during loading.

Drawings

Fig. 1 is a cross-sectional view of an anti-gluing low-noise quasi-zero backlash torque vector differential mechanism of the present invention;

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

FIG. 3 is a schematic view of a protruded differential case in an anti-gluing low-noise quasi-zero backlash torque vector differential mechanism of the present invention;

figure 4 is the utility model discloses an anti veneer low noise is accurate zero side clearance torque vector differential mechanism outstanding erection axle subassembly's schematic diagram.

In the drawings, the reference numbers:

100. a large end difference shell; 110. a second shaft connection hole; 120. a step;

200. a small end differential shell; 210. a first shaft connection hole; 220. an installation part; 221. a third shaft connecting hole; 222. a first mounting hole; 230. fixing the disc;

300. a mounting cavity; 400. a first half-shaft gear; 500. a second side gear; 600. a planetary gear; 610. mounting a shaft assembly; 611. a long straight shaft; 612. a short straight axis; 613. a shaft sleeve; 613a, short shaft connection holes; 614. a second mounting hole; 615. locking the pin; 700. a main reduction gear; 800. a flat gasket; 900. an elastic element.

Detailed Description

The technical solutions in the embodiments of the present invention will be described clearly and completely with reference to the accompanying drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only some embodiments of the present invention, not all embodiments. Based on the embodiments in the present invention, all other embodiments obtained by a person skilled in the art without creative work belong to the protection scope of the present invention.

Examples

The utility model provides an anti-gluing low-noise quasi-zero backlash torque vector differential, which is shown in figures 1-4 and comprises a large-end differential shell 100 and a small-end differential shell 200 which are detachably connected; the large end difference shell 100 and the small end difference shell 200 enclose to form an installation cavity 300; a first side gear 400 and a second side gear 500 are coaxially and rotatably arranged inside the mounting cavity 300; a plurality of planetary gears 600 are engaged and connected between the first side gear 400 and the second side gear 500; a main reduction gear 700 is provided on the outer sides of the large end difference housing 100 and the small end difference housing 200. Among them, the first side gear 400, the second side gear 500, and the planetary gears 600 are all bevel gears. In operation, the side gears output torque and the planetary gears 600 transmit torque. And the outer sides of the large end difference shell 100 and the small end difference shell 200 are sleeved through bearings, so that an axial line two-end differential transmission structure is realized, wherein power for driving the differential transmission is provided by a main reduction gear 700 on the outer side.

It should be noted that, in the above description, the coaxial line means that the first side gear 400 and the second side gear 500 are rotatable about two shafts on the same axis.

The first side gear 400 is located near one end of the small end differential case 200, the small end differential case 200 is provided with a first shaft connecting hole 210 concentric with the rotation axis of the first side gear 400, the second side gear 500 is located near one end of the large end differential case 100, and the large end differential case 100 is provided with a second shaft connecting hole 110 concentric with the rotation axis of the second side gear 500. The first and

second side gears

400 and 500 are coupled to the inner side through the first and second

shaft coupling holes

210 and 110.

A flat gasket 800 and an elastic element 900 are respectively arranged between the first side gear 400 and the small end differential case 200 and between the second side gear 500 and the large end differential case 100; the elastic member 900 is located on a side of the flat gasket 800 adjacent to the first half gear 400. Specifically, the elastic element 900 includes a common spring or a belleville spring, or other elastic elements 900 with elastic function, which is illustrated as a spring in this embodiment.

During assembly, the angle clearance of the differential assembly is between 0 and 0.2 degrees, such as 0.05 degree, by selecting the common flat gasket 800, theoretically, the spring is not compressed under the clearance, but due to the manufacturing precision limit of each sub-part of the assembly, particularly the existence of gear cycle slip, the actual angle value fluctuates, the situation of negative clearance may occur, the spring is compressed to offset the negative clearance, the locking of the gear during operation is prevented, the smoothness of gear meshing transmission is ensured, the noise of gear transmission is obviously improved, and on the other hand, the application of the elastic elements 900 such as the spring also enables the impact noise of vehicle gear shifting to be obviously reduced. Particularly, if a certain new energy vehicle type has a high requirement on noise and a general requirement on anti-gluing performance, the gap angle is 0-0.2 degrees on the side close to 0, even the gap angle can be 0, and if a certain new energy vehicle type has a high requirement on anti-gluing performance and a general requirement on noise, the gap angle is 0-0.2 degrees on the side close to 0.2 degrees, which are determined by the actual vehicle type working conditions.

An annular mounting part 220 is formed at one end of the small end difference shell 200 close to the large end difference shell 100; the mounting portion 220 is located inside the large end differential shell 100; a cross-shaped mounting shaft assembly 610 is detachably mounted on the inner side of the mounting part 220; the mounting shaft assembly 610 is rotatably coupled to a plurality of planetary gears 600.

A horizontal fixed disk 230 is formed outside the mounting part 220, and the fixed disk 230 is parallel to the mounting shaft assembly 610; the fixed disk 230, the large end difference shell 100 and the main reduction gear 700 are detachably and fixedly connected. In particular, the fixing may be performed by a pin, or other detachable fixing methods, which are not limited herein.

Further, a step 120 is formed on the side of the large end difference housing 100 close to the small end difference housing 200, and the mounting portion 220 abuts on the step 120.

Through the installation department 220 that sets up, realize the poor shell of big end 100 and the poor shell 200 of tip and dismantle the connection, through the poor shell of big end 100 and the poor shell 200 of tip that can dismantle the connection, can conveniently install first side gear 400, second side gear 500, planetary gear 600 and installation axle assembly 610 to the installation cavity 300 inboard. Meanwhile, the manufacturing precision of each sub-part is ensured.

Specifically, the mounting shaft assembly 610 includes a long straight shaft 611 and two short straight shafts 612; a shaft sleeve 613 is sleeved in the middle of the long straight shaft 611, and short shaft connecting holes 613a are respectively formed at the outer side of the shaft sleeve 613 and at the two sides perpendicular to the length direction of the long straight shaft 611; one ends of the two short linear shafts 612 close to the long linear shaft 611 are respectively inserted into the short shaft connecting holes 613 a. The mounting portion 220 is formed with four third shaft connection holes 221, and the outer ends of the long straight shaft 611 and the short straight shaft 612 are connected to the third shaft connection holes 221, respectively. Through the arrangement, the long straight shaft 611 and the short straight shaft 612 can be fixedly connected, and the planetary gears 600 can be supported.

The long straight axis 611 and the short straight axis 612 are fixed in the following manner: the mounting portion 220 is provided with four first mounting holes 222 penetrating therethrough, wherein the first mounting holes 222 are parallel to the axial direction of the mounting portion 220; each first mounting hole 222 is communicated with one third shaft connecting hole 221; the first mounting hole 222 vertically mounts the shaft assembly 610. Second mounting holes 614 are respectively formed in one ends of the long straight shaft 611 and the short straight shaft 612, which are located in the third shaft connecting hole 221, the first mounting hole 222 and the second mounting hole 614 can rotate to a concentric position, and a locking pin 615 penetrates through the first mounting hole 222 and the second mounting hole 614 to be connected with the first mounting hole and the second mounting hole 614.

The utility model provides an anti accurate zero backlash torque vector differential mechanism of veneer low noise through setting up in 300 inboard plain washer 800 and elastic element 900 of installation cavity, can accomplish 0 ~0.2 with the differential mechanism assembly clearance, reaches the requirement of accurate zero backlash promptly. Wherein, ordinary flat gasket 800's effect is the adjustment clearance, and ordinary flat gasket 800 can also play the protection differential case, prevents its phenomenon of wearing and tearing, and elastic element's effect prevents on the one hand that the gear train from leading to the fact when rotating the gear card and dies, and on the other hand guarantees that differential mechanism absorbs the impact of shifting or the meshing impact after the loading receives the load.

In the description of the present invention, it should be noted that the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", "front", "rear", and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, and are only for convenience of description and simplification of description, but do not indicate or imply that the device or element referred to must have a specific orientation, be constructed in a specific orientation, and be operated, and thus, should not be construed as limiting the present invention. Furthermore, the terms "first," "second," and "third" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.

In the description of the present invention, it should be noted that, unless otherwise explicitly stated or limited, the terms "mounted," "connected" and "connected" are to be construed broadly and may include, for example, a fixed connection, a detachable connection, an integral connection, a mechanical connection, an electrical connection, a direct connection, an indirect connection via an intermediate medium, and a connection between two elements. The specific meaning of the above terms in the present invention can be understood in specific cases to those skilled in the art. In the case of conflict, the embodiments and features of the embodiments of the present invention can be combined with each other.

The above-mentioned embodiments only express the embodiments of the present invention, and the description thereof is more specific and detailed, but not construed as limiting the scope of the present invention. It should be noted that, for those skilled in the art, without departing from the spirit of the present invention, several variations and modifications can be made, which are within the scope of the present invention. Therefore, the protection scope of the present invention should be subject to the appended claims.

Claims

1. The utility model provides an anti veneer low noise quasi-zero backlash torque vector differential mechanism which characterized in that: comprises a large end difference shell (100) and a small end difference shell (200) which are detachably connected; the large end difference shell (100) and the small end difference shell (200) enclose to form an installation cavity (300);

a first side gear (400) and a second side gear (500) are coaxially and rotatably arranged on the inner side of the mounting cavity (300), and a plurality of planet gears (600) are meshed and connected between the first side gear (400) and the second side gear (500);

the first half shaft gear (400) is positioned at one end close to the small end difference shell (200), a first shaft connecting hole (210) concentric with the rotation axis of the first half shaft gear (400) is formed in the small end difference shell (200),

the second side gear (500) is positioned at one end close to the large-end difference shell (100), and a second shaft connecting hole (110) concentric with the rotation central axis of the second side gear (500) is formed in the large-end difference shell (100);

a flat gasket (800) and an elastic element (900) are respectively arranged between the first side gear (400) and the small end difference shell (200) and between the second side gear (500) and the large end difference shell (100); the elastic element (900) is positioned on one side of the flat gasket (800) close to the first half shaft gear (400).

2. The glue-resistant low-noise quasi-zero backlash torque vector differential of claim 1, wherein: an annular mounting part (220) is formed at one end of the small end difference shell (200) close to the large end difference shell (100); the mounting part (220) is positioned inside the large end difference shell (100);

a cross-shaped mounting shaft assembly (610) is detachably mounted on the inner side of the mounting part (220);

the mounting shaft assembly (610) is rotatably connected to a plurality of the planetary gears (600).

3. The glue-resistant low-noise quasi-zero backlash torque vector differential of claim 2, wherein: a horizontal fixed disc (230) is formed on the outer side of the mounting part (220), and the fixed disc (230) is parallel to the mounting shaft assembly (610); the fixed disc (230), the large-end difference shell (100) and the main reduction gear (700) are detachably and fixedly connected.

4. The anti-seize, low noise, quasi-zero backlash torque vector differential of claim 2, wherein: the mounting shaft assembly (610) comprises a long straight shaft (611) and two short straight shafts (612);

a shaft sleeve (613) is sleeved in the middle of the long straight shaft (611), and short shaft connecting holes (613 a) are respectively formed in the outer side of the shaft sleeve (613) and perpendicular to the two sides of the long straight shaft (611);

one ends of the two short straight shafts (612) close to the long straight shaft (611) are respectively inserted into the short shaft connecting holes (613 a);

four third axle connecting holes (221) are formed in the mounting portion (220), and the outer ends of the long straight shaft (611) and the short straight shaft (612) are connected with the third axle connecting holes (221) respectively.

5. The glue-resistant low-noise quasi-zero backlash torque vector differential of claim 1, wherein: the elastic element (900) comprises a common spring or a belleville spring.

6. The glue-resistant low-noise quasi-zero backlash torque vector differential of claim 2, wherein: the large-end difference shell (100) is close to one side of the small-end difference shell (200) and is provided with a step (120), and the mounting part (220) abuts against the step (120).

7. The glue-resistant low-noise quasi-zero backlash torque vector differential of claim 4, wherein: four first mounting holes (222) penetrating through the mounting part (220) are formed in the mounting part, and each first mounting hole (222) is communicated with one third shaft connecting hole (221); the first mounting hole (222) is perpendicular to the mounting shaft assembly (610);

second mounting holes (614) are respectively formed in one ends, located in the third shaft connecting holes (221), of the long straight shaft (611) and the short straight shaft (612), the first mounting hole (222) and the second mounting hole (614) can rotate to the concentric position, and the first mounting hole (222) and the second mounting hole (614) penetrate through to be connected with locking pins (615).