CN104214304B - Curved tooth not rounded bevel gear limited slip differential - Google Patents

Abstract

Spiral tooth non-conical gear anti-slip differential, the housing supports a transmission shaft, left half shaft, right half shaft and planet carrier through bearings. The front end of the transmission shaft is a spiral bevel gear, which is meshed with the spiral bevel gear for transmission, and the spiral bevel gear and the planet carrier are installed together by bolts. The first planetary spiral non-conical gear and the second planetary spiral non-conical gear are symmetrically arranged inside the planet carrier, and the first planetary spiral non-conical gear and the second planetary spiral non-conical gear are simultaneously connected with the left half shaft spiral non-conical gear It meshes with the right side shaft spiral non-conical gear. The left half-shaft spiral non-conical gear and the right half-shaft spiral non-conical gear are respectively engaged with the left half shaft and the right half shaft through splines. It has the characteristics of large coincidence degree of spiral bevel gear, stable transmission, high bearing capacity and high friction coefficient. Spiral non-conical gears can be processed on a spiral tooth CNC milling machine, which has the advantages of high processing efficiency, high processing accuracy, high tooth surface finish, and low overall cost.

Description

Spiral tooth non-conical gear limited slip differential

technical field

The invention relates to an automobile differential, in particular to a spiral-toothed non-conical gear anti-slip differential.

Background technique

The differential enables the vehicle to freely distribute the torque of the wheels on both sides during driving, so that it can turn normally or pass through uneven roads. Its performance is directly related to the handling performance, passing performance, and safety performance of the vehicle. It is an important part of the car transmission system.

At present, there are mainly two types of differentials, one is ordinary differentials, and the other is limited slip differentials. Ordinary differentials rely on the bevel gear planetary gear train to distribute torque, and rely on the friction of the transmission system to obtain a certain locking coefficient. The locking coefficient is small. When one side of the wheel is on a low-adhesion road surface, The wheel turns at high speed while the other wheel stops turning, causing the vehicle to lose drive.

The anti-slip differential uses some special methods, such as mechanical self-locking, friction, hydraulic power, and electronic active control to increase the locking coefficient. Its main forms and products are: 1. Torsen differential: use a pair of worm gears instead of planetary gears to increase the locking coefficient. The disadvantage is that the transmission efficiency of the entire differential system is reduced and the fuel consumption is high; 2. The friction plate differential Gear: Use centrifugal force to push the friction plate to increase the friction coefficient between the planetary wheels. The disadvantage is that the components are severely worn and the service life is low; 3. Electronic active control differential: it is locked by electronic active control, but due to The driving conditions of the car are relatively poor, and the stability and durability of the control system are difficult to guarantee; 4. Non-circular gear ratio differential: At present, domestic patents mention two differentials, one is a three-week joint barrier differential One is a single-cycle differential with a transmission ratio of 2 (patent No. CN101886659). The three-column differential has many disadvantages, such as a small range of transmission ratio, a short change period, and easy pulsation. The single-section anti-slip differential overcomes the above-mentioned shortcomings, but since only two planetary wheels can be arranged, its strength is reduced and its carrying capacity is limited. Both of the above differentials are based on straight-toothed non-conical gears, which are difficult to machine.

Contents of the invention

The object of the present invention is to provide a non-conical gear non-slip differential with spiral teeth, which not only has the characteristics of transmission ratio transmission of straight non-conical gears, but also has the characteristics of large coincidence degree of spiral bevel gears, stable transmission, high bearing capacity, and low friction. High coefficient characteristics, etc. Spiral non-conical gears can be generated and processed on a spiral tooth CNC milling machine, and can be ground and lapped. It has the advantages of high processing efficiency, high processing accuracy, high tooth surface finish, and low overall cost.

The technical scheme that the present invention realizes above-mentioned purpose is:

The spiral tooth non-conical gear anti-slip differential includes a housing, which is characterized in that the housing supports a transmission shaft, a left half shaft, a right half shaft and a planet carrier through bearings. The front end of the transmission shaft is the first spiral bevel gear, which is engaged with the second spiral bevel gear for transmission, and the second spiral bevel gear and the planet carrier are installed together by bolts. The first planetary spiral non-conical gear and the second planetary spiral non-conical gear are symmetrically arranged inside the planetary carrier, and the first planetary spiral non-conical gear and the second planetary spiral non-conical gear are simultaneously connected with the left half shaft spiral non-conical gear It meshes with the right side shaft spiral non-conical gear. The left half-shaft spiral non-conical gear and the right half-shaft spiral non-conical gear are respectively meshed with the left half shaft and the right half shaft through splines.

According to the above scheme, the left half-shaft spiral non-conical gear and the right half-shaft spiral non-conical gear are exactly the same, the change period of its tooth shape is 2, its radial tooth shape is a spiral tooth system, and the end face tooth shape is Involute teeth.

According to the above scheme, the first planetary spiral non-conical gear and the second planetary spiral non-conical gear are also exactly the same, the intermediate shaft is offset to one end of the gear body, and the change of its tooth shape is a cycle, and its tooth shape For the arc tooth system.

According to the above scheme, the number of teeth of the first planetary spiral non-conical gear and the second planetary spiral non-conical gear is 8-12 according to the strength requirements, and the number of teeth of the left side shaft spiral non-conical gear is the first planetary spiral 2 times of the non-conical gear, the number of teeth of the right side shaft spiral non-conical gear is twice the number of teeth of the second planetary spiral non-conical gear.

The transmission ratio of the planetary spiral non-conical gear and the half shaft spiral non-conical gear adopts the function In the formula is the rotation angle of the planetary gear, a and b are undetermined coefficients, and satisfy

The beneficial effects of the present invention are:

1. The variable speed ratio planetary non-conical gear mechanism is adopted. When the planetary gear rotates, the transmission ratio between the transmission shaft and the half shafts on both sides will change, so that the minimum potential energy position of the differential will change, and the speed ratio of the two half shafts will be limited. Within a certain range, the skidding of the vehicle is limited and the passing performance of the vehicle is improved.

2. Using spiral non-conical gears, combining the characteristics of variable transmission ratio of non-conical gears with the characteristics of high load capacity and high coincidence of spiral bevel gears, only two planetary gears can meet the strength requirements (ordinary differential The device arranges 4 planetary gears to meet the load requirements).

3. Spiral non-conical gears can be generated and processed on the spiral tooth CNC milling machine, and can be ground and lapped. It has the advantages of high processing efficiency, high processing accuracy, high tooth surface finish, and low overall cost.

Description of drawings

Fig. 1 is a structural schematic diagram of the present invention.

Fig. 2 is the front view of the non-conical gear with half-shaft spiral teeth of the present invention.

Fig. 3 is a plan view of the non-conical gear with half-axis spiral teeth of the present invention.

Fig. 4 is a front view of the planetary spiral non-conical gear of the present invention.

Fig. 5 is a top view of the planetary spiral non-conical gear of the present invention.

detailed description

As shown in FIG. 1 , the spiral tooth non-conical gear anti-slip differential includes a housing, which is characterized in that: the housing 9 supports the drive shaft 0 , the left half shaft 8 , the right half shaft 3 and the planetary carrier 6 through bearings. The front end of the transmission shaft is the first spiral bevel gear, which is engaged with the second spiral bevel gear 5 for transmission, and the second spiral bevel gear 5 and the planet carrier 6 are installed together by bolts. The first planetary spiral tooth non-conical gear 1 and the second planetary spiral non-conical gear 4 are symmetrically arranged inside the planet carrier, and the first planetary spiral non-conical gear 1 and the second planetary spiral non-conical gear 4 are simultaneously aligned with the left half shaft arc Teeth non-conical gear 7 meshes with right side shaft spiral non-conical gear 2. The left half-shaft spiral non-conical gear 7 and the right half-shaft spiral non-conical gear 2 are respectively meshed with the left half shaft 8 and the right half shaft 3 through splines. The left half-shaft spiral non-conical gear 7 is exactly the same as the right half-shaft spiral non-conical gear 2, and its front view and top view are shown in Figure 2 and Figure 3 respectively. , the radial tooth shape is arc tooth system, and the end face tooth shape is involute tooth. The first planetary spiral tooth non-conical gear 1 and the second planetary spiral tooth non-conical gear 4 are also exactly the same, the intermediate shaft is offset to one end of the gear body, and the change of its tooth shape is a period, in order to be consistent with the half shaft spiral tooth non-conical When the gears mesh correctly, the tooth shape is arc-toothed, and its front view and top view are shown in Figure 4 and Figure 5 respectively.

When the vehicle is running straight, the transmission shaft 0 drives the planetary carrier 6 to rotate. Since the left half shaft 8 and the right half shaft 3 have the same adhesion force, the first planetary spiral non-conical gear 1 and the second planetary spiral non-conical gear 4 are opposite to each other. The planetary carrier 6 does not rotate, so that the left half-shaft spiral non-conical gear 7 and the right half-shaft spiral non-conical gear 2 all transmit power to the left half shaft 8 and the right half shaft 3 at the same speed as the planet carrier. When the vehicle is turning or driving on an uneven road, the traction force of the left and right axle shafts will no longer be the same. According to the principle of minimum potential energy, the first planetary spiral non-conical gear 1 and the second planetary spiral non-conical gear 4 will be The same speed and direction rotate relative to the planetary carrier 6, so that the left half-shaft spiral non-conical gear 7 and the right half-shaft spiral non-conical gear 2 rotate at different speeds, so that the two half shafts rotate at different speeds to pass Complicated road surfaces or turns. Since the first planetary spiral non-conical gear 1 and the second planetary spiral non-conical gear 4 and the left half-shaft spiral non-conical gear 7 and the right half-shaft spiral non-conical gear 2 are gear ratio transmissions, when the first planetary arc When the toothed non-conical gear 1 and the second planetary spiral non-conical gear rotate, the transmission ratio between the half shafts on both sides will also change, so that the minimum potential energy position of the devices on both sides will change, and the speed of the half shafts on both sides will change. The ratio is limited within a certain range, thereby overcoming slippage.

Claims (4)

1. A spiral tooth non-conical gear anti-slip differential, comprising a housing (9), characterized in that: the housing (9) is supported by a bearing with a transmission shaft (0), a left half shaft (8), a right half shaft Shaft (3) and planetary carrier (6); the front end of the transmission shaft is the first spiral bevel gear, which is meshed with the second spiral bevel gear (5) for transmission, and the second spiral bevel gear (5) and the planetary carrier (6 ) are installed together by bolts; the first planetary spiral non-conical gear (1) and the second planetary spiral non-conical gear (4) are arranged symmetrically inside the planet carrier, the first planetary spiral non-conical gear (1) and the second planetary spiral non-conical gear (1) and the second The planetary spiral non-conical gear (4) meshes with the left half-shaft spiral non-conical gear (7) and the right half-shaft spiral non-conical gear (2); the left half-shaft spiral non-conical gear (7) and the right half The shaft spiral tooth non-conical gear (2) is respectively meshed with the left half shaft (8) and the right half shaft (3) through splines. 2. The non-conical non-conical gear anti-slip differential according to claim 1, characterized in that: the non-conical non-conical gear (7) of the left half shaft and the non-conical non-conical gear (2) of the right half shaft are completely Similarly, the change period of its tooth shape is 2, its radial tooth shape is an arc tooth, and the end face tooth shape is an involute tooth. 3. The spiral tooth non-conical gear anti-slip differential according to claim 1, characterized in that: the first planetary spiral non-conical gear (1) and the second planetary spiral non-conical gear (4) are completely Similarly, the gear shaft is offset to one end of the gear body, and the change of its tooth shape is a cycle, and its tooth shape is an arc tooth system. 4. The spiral tooth non-conical gear anti-slip differential according to claim 1 or 3, characterized in that: the first planetary spiral non-conical gear (1) and the second planetary spiral non-conical gear (4 The number of teeth of ) is 8-12 according to the strength requirements, the number of teeth of the left half-shaft spiral non-conical gear (7) is twice the number of teeth of the first planetary spiral non-conical gear (1), and the right half-shaft spiral non-conical gear The number of teeth of (2) is 2 times of the number of teeth of the second planetary spiral non-conical gear (4).