KR101272526B1 - Rear axle for high power engine - Google Patents

Abstract

PURPOSE: A rear axle for a large output engine is provided to replace an existing double deceleration rear axle by reversing a rotation direction through the connection of a single ring gear and a planetary gear set and to disperse a load by connecting two ring gears to a pinion gear. CONSTITUTION: A rear axle for a large output engine comprises a drive pinion(101), a first main ring gear(102), a second main ring gear(103), a planetary gear ring gear(104), a carrier, and a planetary gear sun gear(106). The drive pinion is rotatably installed by interlocking with a propeller shaft. The first main ring gear is directly fixed to a right wheel differential case(110). The first main ring gear rotates with the drive pinion. The second main ring gear is opposed to the first main ring gear and rotates with the drive pinion. The planetary gear ring gear is integrated with the second main ring gear and rotates with the second main ring gear. The carrier rotates with the planetary gear ring gear. The planetary gear sun gear rotates with the carrier and is fixed to a left wheel differential case(109).

Description

Rear axle for high power engines {Rear axle for high power engine}

TECHNICAL FIELD The present invention relates to a rear axle for a high power engine, and more particularly to a rear axle for a high power engine suitable for transmitting the output of a high powered engine to a wheel.

The rear axle used in the driving device of the vehicle transmits the output of the engine coming in through the transmission to the wheels.

The rear axle applied to commercial vehicles is classified into single reduction and double reduction depending on the type, and the short reduction rear axle is applied to a general vehicle.

FIG. 12 shows an example of such a conventional short reduction rear axle. As shown in FIG. 12, the short reduction rear axle includes a pinion gear for transmitting a driving force from the propulsion shaft and a ring gear connected to the pinion gear. . The ring gear is connected to the axle shaft and connected to the wheel, and the ring gear and the pinion gear are covered and protected by the axle case. Since the structure of the rear axle is installed on the bottom of the vehicle, it is necessary to secure a ground level above a certain level.

On the other hand, when the engine is high output, the load on the rear axle gear is increased, so the axle gear size should be increased.

However, the axle gear size is limited by the axle gear size due to the ground clearance limit of the axle case surrounding the gear. Therefore, in the related art, a double reduction rear axle configured to decelerate in two stages as a rear axle suitable for a high power engine is used.

This double deceleration rear axle is also referred to as hub reduction, the specific configuration of which is shown in FIG.

Referring to FIG. 13, a conventional double deceleration rear axle is provided with a primary deceleration gear for deceleration in one stage at a central portion thereof, and a pair of hubs for deceleration in two stages along a direction in which the axle shaft extends to both sides thereof. Is installed. That is, as shown in the enlarged view of FIG. 13, the hub is provided with a planetary gear set for deceleration in two stages.

The specific configuration of the planetary gear set is as shown in FIG. 14, and as the ring gear acts as an input to the fixed sun gear, the drive of the support is output as the output along the same rotational direction as the ring gear. This is done.

The conventional double deceleration rear axle structure has the advantage of maintaining the ground clearance at the center of the axle case by forming a structure in which re-deceleration is performed through the hubs on both sides, but the planetary gear set is applied to both hub portions to reduce the weight. Excessively increased, resulting in a deterioration of vehicle fuel economy and a significant increase in the manufacturing cost of the rear axle.

Accordingly, the present invention has been made to solve the above problems, to be suitable for a vehicle equipped with a high-power engine, two ring gears are connected from the pinion gear to distribute the load applied to the gears, while two ring gears One of them aims to provide a simple rear axle for a high-power engine that can replace the existing double-retarded rear axle by reversing the direction of rotation through connection with a planetary gear set.

In order to achieve the above object, the present invention and the axle case; A drive pinion connected to the propulsion shaft; A first main ring gear fixed to the differential case and rotating in engagement with the drive pinion; A second main ring gear installed to face the first main ring gear and rotating in engagement with the pinion gear; A ring gear for the planetary gear which is fixed to the second main ring gear and rotates together with the second main ring gear; A carrier engaged with the ring gear for the planetary gear and rotatably mounted to the axle case; And a sun gear for a planetary gear mounted to the differential case so as to rotate in engagement with the carrier, wherein the axle shaft is rotated by rotating the first main ring gear fixed to the differential case and the sun gear for the planetary gear according to the rotation of the driving pinion. It provides a rear axle for high power engines configured to

In addition, the axle case provides a rear axle for a high-power engine, characterized in that the first support for the carrier is rotatably mounted.

In addition, the first support has a circular outer circumferential surface, and provides a rear axle for a high-power engine, characterized in that the annular bearing set is mounted on the circular outer circumferential surface.

In addition, the first main ring gear provides a rear axle for a high-power engine, characterized in that rotatably mounted on the first support with the bearing set in between.

In addition, the axle case provides a rear axle for a high-power engine, characterized in that it comprises a second support for fixing the other end of the carrier fixed by the first support.

In addition, the carrier is composed of a first carrier and a second carrier formed to rotate integrally about the concentric rotation axis, the first carrier meshes with the ring gear for the planetary gear, the second carrier is the sun gear for the planetary gear It provides a rear axle for a high power engine, characterized in that it is engaged with.

In addition, the second carrier provides a rear axle for a high power engine, characterized in that it is formed to have a smaller radius than the first carrier.

In addition, the first carrier and the second carrier provides a rear axle for the engine, characterized in that the planetary gear ring gear and the planetary gear sun gear is formed to have a speed ratio of 1: 1.

The rear axle for the high power engine according to the present invention can be configured to share the engine output by 1/2 in each of the two main ring gears connected to the pinion gears and to transmit them to the axle shaft. Therefore, in the rear axle for the high power engine according to the present invention, as two main ring gears are installed, the stress value applied to the gear is reduced to 1/2 based on the same output torque, so that the gear size can be designed small. There is this.

In addition, in the present invention, as the size of the gear of the rear axle is reduced, the size of the axle case surrounding it becomes smaller, which has the effect of solving the ground clearance problem of a vehicle equipped with a high-power engine.

In addition, in the rear axle for the high-power engine according to the present invention, a pair of planetary gear sets installed in the hub can be removed to reduce the speed of the second stage, thereby reducing the weight and reducing the manufacturing cost required for the rear axle production. Can be saved.

In addition, in the rear axle for the high-power engine according to the present invention, the load applied to each ring gear is reduced to 1/2, so that the durability is greatly improved as compared to the structure supported by one ring gear. The durability improvement effect is expected to have an effect of 51 times the fatigue life on the basis of the same input torque.

Figure 1 illustrates in detail the structure of the axle case in the rear axle for a high power engine according to the present invention,
FIG. 2 is an enlarged view of a part of the rear axle for the high power engine in FIG. 1;
3 illustrates a structure in which the second main ring gear and the ring gear for the planetary gear are integrated.
4 (a) and 4 (b) show an axle case of a rear axle for a high power engine according to the present invention.
FIG. 5 shows a rear axle for a high power engine including the axle cases of FIGS. 4 (a) and 4 (b), and FIG. 5 (a) is a perspective view seen from the right wheel side, and FIG. It is a perspective view seen from the left wheel side,
Figure 6 illustrates a specific configuration of the planetary gear set connected to the first main ring gear in the present invention,
7 shows that the sun gear for the planetary gear is integrally formed on the left wheel side differential case,
8 (a), (b) and (c) show that the first main ring gear, the second main ring gear and the planetary gear set rotate in accordance with the rotation of the drive pinion in the rear axle for the high power engine according to the present invention. Specifically,
9 is a conceptual diagram for calculating the radius of rotation of the first carrier and the second carrier in the planetary gear set in the present invention,
10 illustrates a power transmission system using a rear axle for a high power engine according to the present invention in sequence,
11 shows data for the correlation between lifetime and maximum stress,
12 shows an example of a conventional short reduction rear axle,
13 shows an example of a conventional double deceleration rear axle,
FIG. 14 shows the planetary gear set included in the double reduction rear axle of FIG. 13.

The present invention relates to a rear axle of a new structure suitable for a commercial vehicle equipped with a high-power engine, wherein two ring gears of the rear axle are connected to the pinion gear to distribute the load, while one of the two ring gears is a planetary gear set. By inverting the direction of rotation through the connection with, the rear axle for a high-power engine with a simple structure can replace the existing double deceleration rear axle.

Particularly, these two ring gears are installed to face each other on both side wheels with respect to the center drive pinion. In the present specification, a ring gear engaged with the drive pinion toward the right wheel side is called a first main ring gear and is driven to the left wheel side. The ring gear meshed with the pinion is called the second main ring gear.

In this regard, the position and mounting form of the first main ring gear and the second main ring gear may be appropriately changed according to the design. In the rear axle for the high power engine according to the present invention, the first main ring gear is located on the right wheel side. It is provided, and the 2nd main ring gear is not limited only to the case where it is installed in the left wheel side, It also includes the case where a 1st main ring gear is provided in the left wheel side, and a 2nd main ring gear is provided in the right wheel side.

However, in the present specification, as a preferred embodiment of the present invention, the ring gear directly installed on the differential case on the right wheel side is called the first main ring gear, and is provided on the differential case on the left wheel side with a bearing interposed therebetween. An embodiment defined as two main ring gears will be exemplified, and a concrete configuration of a rear axle for a high power engine according to the present invention will be described in detail with reference to these embodiments.

The terminology used herein is for the purpose of describing particular example embodiments only and is not intended to be limiting of the present invention. The singular expressions include plural expressions unless the context clearly dictates otherwise. In this application, the terms “comprises” or “having” are intended to indicate that there is a feature, number, step, action, component, part, or combination thereof described in the specification, and one or more other It is to be understood that the present invention does not exclude the possibility of the presence or the addition of features, numbers, steps, operations, components, parts, or a combination thereof.

In addition, the term 'integrally formed' in the present specification means that it is formed in a state capable of moving integrally, and does not mean that it is integrally manufactured.

Hereinafter, a preferred embodiment of the present invention will be described in detail with reference to the accompanying drawings.

FIG. 1 illustrates in detail the structure of the axle case 113 in the rear axle for a high power engine according to the present invention, and FIG. 2 is an enlarged view of a portion of FIG. 1.

1 and 2, the rear axle for a high power engine according to the present invention includes a drive pinion 101 installed to be rotatable in conjunction with a propulsion shaft for transmitting a driving force from the engine. The drive pinion 101 rotates as the propulsion shaft rotates, and two ring gears are engaged with the drive pinion 101.

These two ring gears are installed to face each other on both side wheels on the left and right, respectively, about the drive pinion 101. In this embodiment, the ring gear meshed with the drive pinion 101 toward the right wheel side is called the first main ring gear 102, and the ring gear meshed with the drive pinion 101 with the left wheel side is called the second main ring gear 103. do.

The first main ring gear 102 is directly fixed to the right wheel side differential case 110 and rotates according to the rotation of the drive pinion 101 which transmits the driving force from the propulsion shaft, while rotating the differential case to connect the axle shaft. 112 is configured to rotate.

On the other hand, a second main ring gear 103, which is another ring gear meshing with the drive pinion 101, is provided opposite to the first main ring gear 102. The second main ring gear 103 is located opposite the first main ring gear 102 and rotates together with the first main ring gear 102 by a drive pinion 101.

Unlike the first main ring gear 102, the second main ring gear 103 is not directly fixed on the differential case, and is connected to the planetary gear set installed therein so that the planetary gear set is left-side differential case. It is configured to be fixed to.

The planetary gear set is to reverse the rotation direction of the second main ring gear 103, the planetary gear ring gear 104 formed integrally with the second main ring gear 103, and the planetary gear ring The left wheel side differential case 109 is configured to rotate according to the rotation of the gear 104 and the sun gear 106 for the planetary gear.

The configuration of the left wheel side including this second main ring gear 103 and the planetary gear set is shown in more detail in the enlarged view of FIG. 2.

As shown in FIG. 2, the second main ring gear 103 in this embodiment is mounted on the support of the axle case 113 with the bearing 111 interposed therebetween.

In addition, the second main ring gear 103 is configured to interlock with the planetary gear set located inward, as shown in Figure 2, the second main ring gear 103 is a planetary gear ring gear on the inner side 104 is integrally formed. The structure of the integrated second main ring gear 103 and the planetary gear ring gear 104 is shown in detail in FIG. 3.

As shown in FIG. 3, the second main ring gear 103 and the planetary gear ring gear 104 integrally rotate together as the driving pinion 101 rotates, and the planetary gear ring rotates at this time. Gear 104 is operated at the input of the planetary gear set.

Therefore, according to this embodiment, since the second main ring gear 103 rotates in conjunction with the ring gear 104 for the planetary gear integrally formed, the second main ring gear 103 by rotating the drive pinion 101 through the propulsion shaft 2 The sun gear 106 for the planetary gears may be rotated through the main ring gear 103 and the ring gear 104 for the planetary gears.

In addition, since the planetary gear set can rotate the planetary gear sun gear 106 in a direction opposite to the rotational direction of the planetary gear ring gear 104, the rotational direction can be reversed.

Meanwhile, the rear axle for a high power engine according to the present invention includes an axle case 113 that protects the inside of the rear axle and supports internal components such as gears. The structure including such axle case 113 is shown in detail in FIGS. 4 and 5.

First, FIGS. 4A and 4B show an axle case 113 of a rear axle for a high power engine according to the present invention, as shown in FIGS. 4A and 4B. Similarly, an opening for the propulsion shaft connected to the drive pinion 101 is formed, and a support for supporting the planetary gear set and the second main ring gear 103 is provided therein.

The support is manufactured in a fixed form inside the axle case 113, and the carrier is mounted to be rotatable.

In addition, the support is preferably composed of a pair of supports formed between the carriers, each support is configured to rotatably support both ends of the carrier.

The first support 107 located on the left wheel side of the pair of supports is configured such that the second main ring gear 103 can be mounted with the bearing 111 therebetween as described above. To this end, in the embodiment of the high axle engine rear axle according to the present invention, as shown in Figure 4, it can be configured to form a surface on which the bearing 111 can be installed along the outer peripheral surface of the first support 107. In addition, the first support 107 together with the second support 108 formed on the right side is firmly fixed so that the carrier does not leave the track.

In this regard, FIG. 5 illustrates a rear axle for a high power engine including the axle case 113 having the above structure, in which FIG. 5 (a) is a perspective view seen from the right wheel side, and FIG. 5 (b) is a left wheel. It is a perspective view seen from the side.

 As shown in FIGS. 5A and 5B, in the rear axle for a high power engine according to the present invention, a rear axle such as a first main ring gear 102 and a second main ring gear 103 is formed therein. It is configured to receive each component constituting the, and to surround them and to protect from external impact.

In particular, as in Fig. 5 (a), each of the carriers is mounted so as to be rotatably supported by the support, whereby the carrier rotates while being fixed to the support, while the rotational force from the ring gear 104 for the planetary gear is input. It is transmitted to the sun gear 106 for the planetary gear corresponding to the output.

6 shows a specific configuration of such a planetary gear set.

That is, as shown in Figure 6, the planetary gear set is a carrier that rotates in engagement with the planetary gear ring gear 104 and the planetary gear ring gear 104 integrally formed in the second main ring gear 103, And it consists of the sun gear 106 for planetary gears which are meshed with the said carrier and rotate.

Meanwhile, the sun gear 106 for the planetary gear is fixed on the left wheel side differential case 109 as shown in FIG. 7 so that the differential case can be rotated according to the rotation of the sun gear 106 for the planetary gear. It is composed.

Therefore, in the rear axle for the high-power engine according to the present invention, the sun gear 106 for the planetary gear and the first main ring gear to rotate integrally with the right wheel side differential case 110 rotate integrally with the left wheel side differential case 109. The axle shaft 112 is rotated by the 102.

In this regard, FIGS. 8A, 8B and 8C show the first main ring gear 102 and the second main ring gear according to the rotation of the drive pinion 101 in the rear axle for a high power engine according to the present invention. The 103 and the planetary gear set are shown to rotate specifically.

Referring to FIGS. 8 (a), 8 (b) and 8 (c), when the driving pinion 101 rotates in accordance with the rotation of the propulsion shaft, the first main ring gear 102 and the second gear meshed to both sides are first rotated. The main ring gear 103 rotates in association with the drive pinion 101.

At this time, the rotation direction of the first main ring gear 102 and the second main ring gear 103 is rotated in opposite directions as shown in Fig. 7 (a). Therefore, in the present embodiment, a planetary gear set is installed on the side of the second main ring gear 103 so that the rotational directions of the first and second main ring gear 103 coincide with the traveling direction of the vehicle. The direction of rotation of the gear 103 is reversed so that it can be transmitted to the axle shaft 112.

That is, as shown in FIG. 8 (b) showing what is viewed from the side of FIG. 8 (a), the ring gear for the planetary gear which rotates integrally with the second main ring gear 103 while rotating the carrier fixed on the support. The input of the 104 is transmitted to the planetary gear sun gear 106 side, wherein the rotation direction of the planetary gear sun gear 106 is the second main ring gear 103 and the planetary gear ring gear 104 Are opposite to the direction of rotation.

Therefore, the rotational direction of the planetary gear set may be reversed to match the rotational direction of the first main ring gear 102 shown in FIG. 8C.

On the other hand, when the carrier is fixed in this way and the rotation direction is reversed by using the planetary gear set having the sun gear as the output with the ring gear as the input, a reverse speed increase occurs when the rotation speed is increased.

Therefore, in the preferred embodiment of the present invention, in order to solve the problem of the increase in speed due to the planetary gear set, the carrier is configured such that two carriers having different radii are integrally formed on the concentric rotation axis.

The structure of such a carrier is also shown in detail in FIGS. 2 and 6. That is, referring to FIG. 2 and the like, the carrier in the present embodiment is integrally formed on the first carrier 105a meshed with the ring gear 104 for the planetary gear and the rotation axis concentric with the first carrier 105a. And a second carrier 105b meshed with the sun gear 106 for the planetary gear.

In addition, the first carrier 105a and the second carrier 105b have a radius of the first carrier 105a larger than that of the second carrier 105b in order to solve the speed increase problem. The rotational speed ratio of the ring gear 104 side and the planetary gear sun gear 106 side is set to be 1: 1.

Regarding the radius setting of the first and second carriers 105b, referring to FIG. 9, the radius P1 of the first carrier 105a and the radius P2 of the second carrier 105b are calculated by the following equation. do.

Therefore, if the radius R of the planetary gear ring gear 104 and the radius S of the planetary gear sun gear 106 are determined, the first carrier 105a and the second carrier 105b can be obtained using this equation. ), And the planetary gear set manufactured as described above has a final rotational ratio of 1: 1.

Therefore, in the rear axle for the high power engine according to the present invention, even if the first main ring gear 102 and the second main ring gear 103 interlocked with the drive pinion 101 rotate in different directions, the second main ring gear The rotation direction of the 103 can be reversed without increasing the speed so that the first main ring gear 102 and the planetary gear ring gear 104 for rotating the axle shaft 112 rotate at the same rotational direction and at the same speed. Can be configured.

10 illustrates a power transmission system using a rear axle for a high power engine having such a configuration.

That is, as shown in FIG. 10, in the rear axle for the high power engine according to the present invention, power is respectively supplied to the first main ring gear 102 and the second main ring gear 103 according to the rotation of the drive pinion 101. Will be delivered.

First, the driving force transmitted to the first main ring gear 102 side is transmitted to the right wheel side differential case 110 to rotate the axle shaft 112 and the wheel.

On the other hand, the driving force transmitted to the second main ring gear 103 side reverses the rotation direction through the ring gear 104 for the planetary gear, and the gear ratio is corrected by the first carrier 105a and the second carrier 105b. As the rotation speed is corrected, the driving force is transmitted to the sun gear 106 for the planetary gear while maintaining the rotation speed of the ring gear 104 for the planetary gear. The driving force transmitted to the sun gear 106 for the planetary gear is transmitted to the axle shaft 112 through the left wheel side differential case to rotate the wheel.

Therefore, in the rear axle for the high-power engine having the first main ring gear 102 and the second main ring gear 103 meshed with the drive pinion 101 as described above, each of the first main ring gear 102 and the second Since the main ring gear 103 shares the engine output by 1/2 and transmits it to the axle shaft 112, the gear size can be designed small.

That is, since two ring gears are engaged with the drive pinion 101 to transmit power, the stress value is reduced to 1/2 based on the same torque, so that each gear can be designed smaller. In addition, as the gear size decreases, the size of the axle case 113 may also be reduced, thereby eliminating the ground clearance problem of the vehicle.

In particular, in FIG. 11, the correlation between the life and the maximum stress is shown on a logarithmic scale in relation to the fatigue life change according to the stress change received by each gear.

That is, when the fatigue life calculation formula is calculated according to the life graph of FIG. 11,

(N: number of cycles, σ: maximum stress, α: S-N slope (assuming 5.68 for the rear axle gear steel material))

Therefore, when the stress applied to the gear is reduced to 1/2, the fatigue life is increased by 51 times. In this technology, it can be seen that the fatigue life is improved by 51 times compared to the existing structure.

While the invention has been described with reference to the preferred embodiments, those skilled in the art will appreciate that modifications and variations of the elements of the invention may be made without departing from the scope of the invention. In addition, many modifications may be made to particular circumstances or materials without departing from the essential scope of the invention. Therefore, the invention is not limited to the details of the preferred embodiments of the invention, but will include all embodiments within the scope of the appended claims.

101: drive pinion 102: first main ring gear
103: second main ring gear 104: ring gear for planetary gears
105a: first carrier 105b: second carrier
106: sun gear for planetary gear 107: first support
108: second support 109: left wheel side differential case
110: right side wheel differential case 111: bearing
112: axle shaft 113: axle case

Claims (8)

An axle case;
A drive pinion connected to the propulsion shaft;
A first main ring gear fixed to the differential case and rotating in engagement with the drive pinion;
A second main ring gear installed to face the first main ring gear and rotating in engagement with the pinion gear;
A ring gear for the planetary gear which is fixed to the second main ring gear and rotates together with the second main ring gear;
A carrier engaged with the ring gear for the planetary gear and rotatably mounted to the axle case;
Sun gear for the planetary gear is mounted to the differential case to rotate in engagement with the carrier;
And a rear main axle configured to rotate the axle shaft by rotating the first main ring gear fixed to the differential case and the sun gear for the planetary gear according to the rotation of the drive pinion.
The method according to claim 1,
The axle case is a rear axle for a high power engine, characterized in that the first support for rotatably mounting the carrier is formed.
The method according to claim 2,
The first support has an outer circumferential surface formed in a circular shape, and an annular bearing set is mounted on the circular outer circumferential surface.
The method according to claim 3,
And the first main ring gear is rotatably mounted on the first support with the bearing set interposed therebetween.
The method according to any one of claims 2 to 4,
The axle case is a rear axle for a high power engine, characterized in that it comprises a second support for fixing the other end of the carrier fixed by the first support.
The method of claim 1, wherein the carrier comprises a first carrier and a second carrier formed to rotate integrally about the concentric rotation axis, the first carrier meshes with the ring gear for the planetary gear, the second carrier is the planetary group A rear axle for a high power engine, characterized in that it is fitted with a fish sun gear.
The method of claim 6,
And the second carrier has a smaller radius than the first carrier.
The method according to claim 6 or 7,
And the first carrier and the second carrier are formed such that the ring gear for the planetary gear and the sun gear for the planetary gear have a speed ratio of 1: 1.

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