CN105465322A - Random-tooth-difference inner gear driving double-roller block type automobile differential - Google Patents

Abstract

The utility model relates to an internal gear with arbitrary tooth difference driving a double-roller block type automobile differential, which belongs to the technical field of mechanical transmission. The invention provides a new type of automobile differential gear. The outer tooth inner center wheel of the outer gear is a straight bevel gear and the inner gear is an inner gear. The power is input from the bevel gear outside the inner center wheel with outer teeth, and transmitted to the double roller block through the inner gear of the inner center wheel with outer teeth, and then the double roller block transmits the power to the left axle frame fixedly connected with the left wheel and the The right half-shaft multi-phase outer cam fixedly connected to the right wheel enables the left and right rear wheels to realize differential speed. The differential eliminates the planetary gear system in the traditional automotive differential, and the double roller blocks are in multi-tooth mesh with the external tooth inner center wheel, left half shaft frame and right half shaft multi-phase outer cam. The pure rolling contact between the roller blocks and the left axle frame makes the differential compact in structure, small in size, light in weight, multi-tooth meshed, large in overlap, strong in bearing capacity and high in transmission efficiency, and can be widely used in differential applications. Various wheeled vehicles with gearboxes, such as automobiles, engineering vehicles, etc.

Description

Arbitrary Tooth Difference Internal Gear Driven Double Roller Block Type Automotive Differential

technical field

The invention relates to a double-roller block type automobile differential driven by an internal gear with any tooth difference, which is used for the differential speed of wheeled vehicles and belongs to the technical field of mechanical transmission.

Background technique

At present, the commonly used automotive differentials use a planetary gear system composed of multiple straight-toothed bevel gears to achieve the purpose of differential speed. Although this system can realize the differential speed of the left and right axle shafts of the car, there are many components in the system. , the axial and radial dimensions are large, the volume is large, and the weight is heavy, especially for heavy-duty vehicles, in order to achieve differential speed and transmit sufficient power, the volume and weight will be further increased; straight bevel gear transmission is also It has the disadvantages of low coincidence, low bearing capacity, low transmission efficiency, difficult processing of straight bevel gears, and poor manufacturability.

Contents of the invention

The object of the present invention is: in order to overcome the above-mentioned shortcomings existing in the existing automobile differential, the present invention provides a simple and compact structure, small axial and radial dimensions, light weight, high coincidence degree, large bearing capacity, and high transmission efficiency. A new type of automotive differential - an internal gear with any tooth difference drives a double roller block type automotive differential.

The technical solution adopted by the present invention to solve the technical problem is: a kind of arbitrary tooth difference internal gear drive double roller block type automobile differential, mainly composed of external tooth inner center wheel (1), left axle frame (2) , tapered roller bearing (3), right half shell (4), double roller block (5), right half shaft multi-phase outer cam (6), deep groove ball bearing (7), screw (8), deep groove The ball bearing (9), the sleeve washer (11), and the deep groove ball bearing (12) are characterized in that: the planetary gear system of the traditional automobile differential is abandoned and replaced by "outer tooth inner center wheel one pair Roller block—multi-phase external cam” system, which mainly includes external gear inner center wheel (1), left half shaft frame (2), double roller block (5), right half shaft multi-phase external cam (6 ), realize the differential speed with this system, and constitute the differential gear; the outside of the external tooth inner center wheel (1) is a straight bevel gear, and the inside is an internal gear with a plurality of protruding parts, and the number of the protruding parts is is the number of teeth of the external tooth inner center wheel (1), denoted as Z ₁ , so the external tooth inner center wheel (1) is not only a bevel gear of the final reducer, but also an inner gear in the differential mechanism, and the outer tooth inner center The wheel (1) organically integrates the main reducer and the differential, and the outer gear inner center wheel (1) and the right half shell (4) are fixedly connected into a whole by screws (8) and are formed by a pair of tapered rollers. The bearing (3) is supported on the frame; the left axle frame (2) is a sleeve structure, which is installed in the internal gear of the external gear inner center wheel (1), and there is a Z along the circumference of the sleeve structure. ₂ radial guide grooves, double roller blocks (5) are housed in the guide grooves, the left end of the left half shaft frame (2) is the left half shaft, and the left half shaft frame (2) passes through the left half shaft and the left rear wheel ( 13) are fixedly connected, the left axle frame (2) is supported by a pair of deep groove ball bearings (12) in the inner center wheel (1) of the outer teeth; the right axle multi-phase outer cam (6) has three mutually forming The three-phase external cam with an included angle of 120° and the axially symmetrical convex part is completely balanced in its own mass, and its contour curve is a cosine curve. The multi-phase external cam (6) of the right half shaft is embedded in the left half shaft frame (2 ) in the sleeve structure, the right end of the right half shaft multi-phase outer cam (6) is the right half shaft, and the right half shaft multi-phase outer cam (6) is fixedly connected with the right rear wheel (14) through the right half shaft, The left end of the multi-phase outer cam (6) on the right half shaft is supported in the left half shaft frame (2) through the deep groove ball bearing (9), and the right end is supported on the right half shell (4) through the deep groove ball bearing (7). Inside; the above-mentioned double roller block (5) is made up of bracket block (15), pin (16), needle roller (17), needle roller sleeve (18), and the two ends of pin (16) and bracket block (15) The holes on both sides are tightly fitted, and the two needle roller sleeves (18) are supported by pins (16) and form a rolling connection relationship with the support block (15) through the needle rollers (17); the double roller blocks ( The two needle roller sleeves (18) of 5) can roll radially on the inner wall of the radial guide groove of the sleeve structure of the left axle frame (2), so that the double roller blocks (5) and the left axle frame (2) form a rolling connection, and the arc-shaped outer surfaces of the two ends of the double roller block (5) are respectively connected with the multi-phase outer cam (6) of the right half shaft. The outer cam profile of the external tooth inner center wheel (1) meshes with the inner gear tooth profile of the outer tooth inner center wheel (1) to form a high pair; the inner gear tooth profile curve of the outer tooth inner center wheel (1) is the double roller block (5) on the one hand Rotating with the left half shaft frame (2), on the other hand, during the process of moving in the radial guide groove of the left half shaft frame (2), the envelope line of a series of positions on the arc-shaped outer surface of the inner end; the outer tooth _The difference between the number of teeth Z1 of the inner center wheel ( ₁ ) and the number Z2 of the double roller blocks (5) is 3.

Other unmentioned places of differential gear of the present invention, all adopt prior art as the connection etc. of left axle frame (2), right half axle multi-phase outer cam (6) and vehicle wheel.

Compared with prior art, main inventive point of the present invention is:

① The present invention replaces the planetary gear system of the traditional automobile differential with the system of "external tooth inner center wheel-double roller blocks-multiphase outer cam". The system mainly includes outer tooth inner center wheel, left axle frame, Double roller blocks, multi-phase outer cams on the right half shaft, this system realizes the differential speed and constitutes the differential gear.

②The outside of the external tooth inner center wheel is a straight bevel gear, and the inside is an internal gear with multiple protruding parts. The number of the protruding parts is the number of teeth of the external tooth inner center wheel. A bevel gear of the main reducer is also an internal gear in the differential mechanism. The outer-toothed inner center wheel organically integrates the main reducer and the differential. The outer-toothed inner center wheel and the right half shell are fixed by screws It is connected as a whole and supported on the frame by a pair of tapered roller bearings; the left half-shaft frame is a sleeve structure, which is installed in the inner gear of the external tooth inner center wheel and opened along the circumference of the sleeve structure. There are Z ₂ radial guide grooves, and double roller blocks are installed in the guide grooves. The left end of the left half shaft frame is the left half shaft, and the left half shaft frame is fixedly connected with the left rear wheel through the left half shaft frame. It is supported by a pair of deep groove ball bearings in the inner center wheel of the external teeth; the right half shaft multi-phase external cam is a three-phase external cam with three mutually symmetrical convex parts at an angle of 120°, and its own mass is completely Balanced, its contour curve is a cosine curve, the right half shaft multi-phase outer cam is embedded in the sleeve structure of the left half shaft frame, the right end of the right half shaft multi-phase outer cam is the right half shaft, and the right half shaft multi-phase outer cam The right half shaft is fixedly connected with the right rear wheel, the left end of the multi-phase outer cam of the right half shaft is supported in the left half shaft frame through a deep groove ball bearing, and the right end is supported in the right half shell through a deep groove ball bearing; The above-mentioned double roller block is composed of a bracket block, pins, needle rollers, and needle roller sleeves. The two ends of the pins are tightly fitted with the holes on both sides of the bracket block. The needle roller and the bracket block form a rolling connection; the two needle roller sleeves of the double roller block can roll radially on the inner wall of the radial guide groove of the sleeve structure of the left axle frame, so that the double roller block and the left The half shaft frames form a rolling connection, and the arc-shaped outer surfaces of the two ends of the double roller blocks mesh with the outer cam profile of the multi-phase outer cam of the right half shaft and the inner gear tooth profile of the outer tooth inner center wheel to form a high pair; the internal gear tooth profile curve of the external tooth inner center wheel is that the double roller block rotates with the left half shaft frame on the one hand, and on the other hand moves in the radial guide groove of the left half shaft frame. The envelope of a series of positions on the outer surface; the difference between the number of teeth Z ₁ of the inner center wheel of the outer teeth and the number Z ₂ of the double roller blocks is 3.

③The driving force is transmitted to the inner center wheel of the external teeth, and then transmitted to the left half shaft frame and the right half shaft multi-phase outer cam through the double roller block, so as to be transmitted to the left and right rear wheels, while the double roller block and the left half shaft frame There is a pure rolling friction connection between them, so the transmission efficiency of the differential gear of the present invention is high.

④Multi-tooth engagement between the double roller block and the external tooth inner center wheel, the left half shaft frame and the right half shaft multi-phase outer cam, so the coincidence degree is large, the bearing capacity is large, and high power and high torque differential speed can be realized transmission.

⑤The three protruding parts of the multi-phase outer cam on the right half shaft form an angle of 120° with each other and are arranged symmetrically with respect to the axis.

Compared with the existing conventional automobile differential, the present invention has the following beneficial technical effects:

1. Compact structure, small axial and radial dimensions, small volume and light weight

The present invention adopts the system of "external tooth inner center wheel-double roller block-multiphase outer cam" system to replace the planetary gear system of traditional automobile differential, and the axial and radial dimensions of the transmission device are small, so the present invention is inferior The gearbox is compact in structure, small in size and light in weight.

2. Large coincidence degree and high carrying capacity

In the present invention, the meshing of multiple pairs of teeth is simultaneously realized between the double-roller block and the multi-phase outer cam of the right half-shaft, the inner center wheel of the outer tooth, and the left half-axle frame, and at most 50% of the double-roller blocks can participate in the meshing work at the same time. High coincidence, high load capacity, can realize high power, high torque differential transmission.

3. High transmission efficiency

The pure rolling engagement between the double roller blocks and the left axle frame makes the transmission efficiency of the differential gear of the present invention high.

4. Good manufacturability and low production cost

Most of the parts in the differential gear of the present invention are circular, simple in shape, easier to process than bevel gears in the planetary gear system, good in manufacturability and low in production cost.

5. Balanced force, stable operation

The three protruding parts of the multi-phase outer cam on the right half shaft form an angle of 120° with each other and are arranged symmetrically with respect to the axis. The resultant force of inertial force and external force is zero, so the force of the differential is automatically balanced and the operation is stable.

Description of drawings

The present invention will be further described below in conjunction with drawings and embodiments. However, it should be pointed out that the specific implementation modes of the present invention are not limited to the forms described in the following examples, and those skilled in the art can easily design other specific implementation modes without paying creative efforts. Therefore, the examples of specific implementations given below should not be understood as the protection scope of the present invention, and the protection scope of the present invention is limited to the given examples.

Fig. 1 is a schematic diagram of the structure of a double-roller block type automobile differential driven by an internal gear with any tooth difference;

Fig. 2 is A-A sectional view of Fig. 1;

Fig. 3 is a partial enlarged view of Fig. 2;

Fig. 4 is a schematic structural view of the external gear inner center wheel;

Fig. 5 is a structural schematic diagram of the multi-phase outer cam of the right half shaft;

Fig. 6 is a schematic structural view of the left axle frame;

Fig. 7 is the assembly drawing of double roller block;

Fig. 8 is the structural representation of support block;

Fig. 9 is a schematic diagram of the differential transmission of the double roller block type automobile differential driven by the internal gear with any tooth difference;

Fig. 10 is a schematic diagram of the relative positional relationship between the wheels and the differential when the car turns left.

The identification objects of the symbols in the above drawings are: 1. the inner center wheel with external teeth; 2. the left half shaft frame; 3. tapered roller bearing; 4. the right half shell; Cam; 7 deep groove ball bearing; 8 screw; 9 deep groove ball bearing; 10 driving straight bevel gear of final reducer; 11 sleeve washer; 12 deep groove ball bearing; 13 left rear wheel; 14 right rear wheel; 15 Bracket block; 16 pins; 17 needle rollers; 18 needle roller sleeves.

specific embodiment

As shown in Figures 1 to 8, the internal gear with any tooth difference drives the double roller block type automobile differential, which is mainly composed of the external gear inner center wheel (1), the left axle frame (2), the tapered roller bearing (3), Right half shell (4), double roller block (5), right half shaft multi-phase outer cam (6), deep groove ball bearing (7), screw (8), deep groove ball bearing (9), sleeve washer (11), composed of deep groove ball bearings (12), characterized in that: the planetary gear system of the traditional automobile differential is abandoned, and replaced by "external teeth, inner center wheel, double roller block, multi-phase outer cam ” system, the system mainly includes the external gear inner center wheel (1), the left axle frame (2), the double roller block (5), the right axle multi-phase outer cam (6), and the differential speed is realized by this system, Constitutes a differential; the outer tooth inner center wheel (1) is a straight bevel gear on the outside, and the inner is an inner gear with multiple protruding parts, and the number of the protruding parts is the outer tooth inner center wheel (1) The number of teeth is denoted as Z ₁ , so the external tooth inner center wheel (1) is not only a bevel gear of the final reducer, but also an internal gear in the differential mechanism, and the external tooth inner center wheel (1) connects the final drive and the The differential is organically integrated, the outer tooth inner center wheel (1) and the right half shell (4) are fixedly connected by screws (8) to form a whole and are supported on the frame by a pair of tapered roller bearings (3) ; The left axle frame (2) is a sleeve structure, and the sleeve structure is installed in the internal gear of the external tooth inner center wheel (1), and there are Z ₂ radial guide grooves along the circumference of the sleeve structure, and in the guide Double roller blocks (5) are housed in the groove, and the left end of the left semi-axle frame (2) is the left half shaft, and the left half shaft frame (2) is fixedly connected with the left rear wheel (13) by the left half shaft, and the left half shaft The frame (2) is supported by a pair of deep groove ball bearings (12) in the center wheel (1) of the external teeth; The three-phase external cam of the protruding part has its own mass completely balanced, and its contour curve is a cosine curve. The right end of the shaft multi-phase outer cam (6) is the right half shaft, and the right half shaft multi-phase outer cam (6) is fixedly connected together with the right rear wheel (14) by the right half shaft, and the right half shaft multi-phase outer cam (6 )’s left end is supported in the left axle frame (2) through a deep groove ball bearing (9), and the right end is supported in the right half shell (4) through a deep groove ball bearing (7); the above-mentioned double roller block (5 ) is composed of bracket block (15), pin (16), needle roller (17), needle roller sleeve (18), the two ends of pin (16) and the holes on both sides of bracket block (15) are tight Cooperate, the two needle roller sleeves (18) are supported by pins (16) and form a rolling connection relationship with the bracket block (15) through the needle rollers (17); the two needle roller sleeves of the double roller block (5) (18) can roll radially on the inner wall of the radial guide groove of the sleeve structure of the left axle frame (2), so that a rolling connection is formed between the double roller block (5) and the left axle frame (2), The arc-shaped outer surfaces at both ends of the double roller block (5) are respectively connected with the outer cam profile of the right half shaft multi-phase outer cam (6) and the outer tooth inner center wheel (1) The tooth profiles of the internal gears mesh with each other to form a high pair; the tooth profile curve of the internal gear of the external tooth inner center wheel (1) is that the double roller block (5) rotates with the left axle frame (2) on the one hand, and on the other hand In the process of moving in the radial guide groove of the left axle frame (2), the envelope of _a series of positions on the arc-shaped outer surface of the inner end; The number Z2 of sub-blocks ( ₅ ) differs by three.

The working principle of the differential in the present invention is: when the driven bevel gear of the main reducer, that is, the external tooth inner center wheel (1) is driven and rotates at a constant angular velocity, due to the inner gear of the outer tooth inner center wheel (1) Generate thrust on the double roller block (5), forcing the double roller block (5) to move in the radial guide groove of the left half shaft frame (2) and push the left half shaft frame (2) to rotate, at the same time through the double roller The contact between block (5) and the multi-phase outer cam (6) of the right half shaft will also promote the rotation of the multi-phase outer cam (6) of the right half shaft, thereby forming a two-degree-of-freedom differential system, and the left half shaft frame (2 ) and the motion and power on the multi-phase outer cam (6) of the right axle shaft are passed to the left and right rear wheels that are connected with it respectively. The right half-shaft polyphase outer cam (6) and the left half-axle frame (2) rotate respectively under the effect of driving force, but their respective motion states are uncertain, determined by the different road surfaces and curve conditions of the left and right rear wheels. When the car runs straight on a straight road, the wheels on the left half shaft frame (2) and the wheels on the right half shaft multi-phase outer cam (6) have no speed difference, the left half shaft frame (2) and the right half shaft more The rotating speed of phase outer cam (6) is identical, promptly differential gear does not have differential speed effect. At this time, the components in the differential remain relatively stationary, and the torque is input from the outer gear inner center wheel (1), and is transmitted to the left axle frame (2) and the right half axle multi-phase through the double roller blocks (5) on average. Outer cam (6). When the car is turning or driving on an uneven road, and there is a speed difference between the left and right wheels at the back, the double roller block (5) is driven by the inner center wheel (1) of the outer teeth, and on the one hand drives the left axle frame (2) and the right axle frame (2). The half-shaft polyphase outer cam (6) rotates, and on the other hand, it moves radially in the radial guide groove of the left half-shaft frame (2) while rotating with the left half-shaft frame (2), so as to ensure that the left half-shaft frame ( 2) and the right half-shaft multi-phase outer cam (6) can realize the differential speed without breaking away from the transmission. Moreover, due to the effect of the torque produced by the double roller blocks (5) on the left side axle frame (2) and the multi-phase outer cam (6) of the right half shaft, the driving wheel with a slow speed can obtain a speed faster than that of the speed. More torque on the drive wheels.

In order to illustrate the differential speed characteristic of the differential gear of the present invention, assume that the rotational speeds of the left and right wheels behind the automobile are respectively n ₂ and n ₆ , and the rotational speed of the outer gear inner center wheel (1) is n ₁ , then it can be obtained from Fig. 9:

$\frac{{\mathrm{<span\; class="notranslate">\; no</span>}}_{\mathrm{<span\; class="notranslate">\; 2</span>}}<span\; class="notranslate">\; -</span>{\mathrm{<span\; class="notranslate">\; no</span>}}_{\mathrm{<span\; class="notranslate">\; 6</span>}}}{{\mathrm{<span\; class="notranslate">\; no</span>}}_{\mathrm{<span\; class="notranslate">\; 1</span>}}<span\; class="notranslate">\; -</span>{\mathrm{<span\; class="notranslate">\; no</span>}}_{\mathrm{<span\; class="notranslate">\; 6</span>}}}<span\; class="notranslate">\; =</span>\frac{{\mathrm{<span\; class="notranslate">\; Z</span>}}_{\mathrm{<span\; class="notranslate">\; 1</span>}}}{{\mathrm{<span\; class="notranslate">\; Z</span>}}_{\mathrm{<span\; class="notranslate">\; 2</span>}}}<span\; class="notranslate">\; -</span><span\; class="notranslate">\; -</span><span\; class="notranslate">\; -</span><span\; class="notranslate">\; (</span>\mathrm{<span\; class="notranslate">\; 1</span>}<span\; class="notranslate">\; )</span>$

In the formula, Z ₂ is the number of double roller blocks (5); Z ₁ is the number of teeth of the external tooth inner center wheel (1).

If the car is going to turn left, the axes of the two front wheels of the car and the axes of the two rear wheels of the car meet at point P under the action of the steering mechanism (Fig. 10), and the whole car can be regarded as turning around point P . Under the condition that the wheels and the ground do not slip, the rotational speed of the two rear wheels should be proportional to the radius of the curve, as can be obtained from Figure 10:

$\frac{{\mathrm{<span\; class="notranslate">\; no</span>}}_{\mathrm{<span\; class="notranslate">\; 2</span>}}}{{\mathrm{<span\; class="notranslate">\; no</span>}}_{\mathrm{<span\; class="notranslate">\; 6</span>}}}<span\; class="notranslate">\; =</span>\frac{<span\; class="notranslate">\; (</span>\mathrm{<span\; class="notranslate">\; r</span>}<span\; class="notranslate">\; -</span>\mathrm{<span\; class="notranslate">\; L</span>}<span\; class="notranslate">\; )</span>}{<span\; class="notranslate">\; (</span>\mathrm{<span\; class="notranslate">\; r</span>}<span\; class="notranslate">\; +</span>\mathrm{<span\; class="notranslate">\; L</span>}<span\; class="notranslate">\; )</span>}<span\; class="notranslate">\; -</span><span\; class="notranslate">\; -</span><span\; class="notranslate">\; -</span><span\; class="notranslate">\; (</span>\mathrm{<span\; class="notranslate">\; 2</span>}<span\; class="notranslate">\; )</span>$

In the formula, r is the average radius of the curve; L is half of the rear track.

Simultaneously solve formula (1) and formula (2), get:

${\mathrm{<span\; class="notranslate">\; no</span>}}_{\mathrm{<span\; class="notranslate">\; 2</span>}}<span\; class="notranslate">\; =</span>\frac{<span\; class="notranslate">\; (</span>\mathrm{<span\; class="notranslate">\; r</span>}<span\; class="notranslate">\; -</span>\mathrm{<span\; class="notranslate">\; L</span>}<span\; class="notranslate">\; )</span>{\mathrm{<span\; class="notranslate">\; Z</span>}}_{\mathrm{<span\; class="notranslate">\; 1</span>}}}{{\mathrm{<span\; class="notranslate">\; Z</span>}}_{\mathrm{<span\; class="notranslate">\; 1</span>}}\mathrm{<span\; class="notranslate">\; r</span>}<span\; class="notranslate">\; +</span><span\; class="notranslate">\; (</span>{\mathrm{<span\; class="notranslate">\; Z</span>}}_{\mathrm{<span\; class="notranslate">\; 1</span>}}<span\; class="notranslate">\; -</span>\mathrm{<span\; class="notranslate">\; 2</span>}{\mathrm{<span\; class="notranslate">\; Z</span>}}_{\mathrm{<span\; class="notranslate">\; 2</span>}}<span\; class="notranslate">\; )</span>\mathrm{<span\; class="notranslate">\; L</span>}}{\mathrm{<span\; class="notranslate">\; no</span>}}_{\mathrm{<span\; class="notranslate">\; 1</span>}}<span\; class="notranslate">\; -</span><span\; class="notranslate">\; -</span><span\; class="notranslate">\; -</span><span\; class="notranslate">\; (</span>\mathrm{<span\; class="notranslate">\; 3</span>}<span\; class="notranslate">\; )</span>$

${\mathrm{<span\; class="notranslate">\; no</span>}}_{\mathrm{<span\; class="notranslate">\; 6</span>}}<span\; class="notranslate">\; =</span>\frac{<span\; class="notranslate">\; (</span>\mathrm{<span\; class="notranslate">\; r</span>}<span\; class="notranslate">\; +</span>\mathrm{<span\; class="notranslate">\; L</span>}<span\; class="notranslate">\; )</span>{\mathrm{<span\; class="notranslate">\; Z</span>}}_{\mathrm{<span\; class="notranslate">\; 1</span>}}}{{\mathrm{<span\; class="notranslate">\; Z</span>}}_{\mathrm{<span\; class="notranslate">\; 1</span>}}\mathrm{<span\; class="notranslate">\; r</span>}<span\; class="notranslate">\; +</span><span\; class="notranslate">\; (</span>{\mathrm{<span\; class="notranslate">\; Z</span>}}_{\mathrm{<span\; class="notranslate">\; 1</span>}}<span\; class="notranslate">\; -</span>\mathrm{<span\; class="notranslate">\; 2</span>}{\mathrm{<span\; class="notranslate">\; Z</span>}}_{\mathrm{<span\; class="notranslate">\; 2</span>}}<span\; class="notranslate">\; )</span>\mathrm{<span\; class="notranslate">\; L</span>}}{\mathrm{<span\; class="notranslate">\; no</span>}}_{\mathrm{<span\; class="notranslate">\; 1</span>}}<span\; class="notranslate">\; -</span><span\; class="notranslate">\; -</span><span\; class="notranslate">\; -</span><span\; class="notranslate">\; (</span>\mathrm{<span\; class="notranslate">\; 4</span>}<span\; class="notranslate">\; )</span>$

Under certain vehicle parameters and driving conditions, n ₁ , Z ₁ , Z ₂ , and L are all known. Therefore, n ₂ and n ₆ only vary with the turning radius r. Therefore, the differential device of the present invention has a differential function, and a vehicle equipped with the differential device can pass through curves with any radius.

The present invention can be widely applied to all wheeled vehicles that need a differential, such as automobiles, engineering vehicles and the like.

Claims (3)

1. The internal gear with any tooth difference drives the double-roller block type automobile differential, which is mainly composed of the external tooth inner center wheel (1), the left side axle frame (2), the tapered roller bearing (3), the right half shell (4 ), double roller block (5), right half-shaft multi-phase outer cam (6), deep groove ball bearing (7), screw (8), deep groove ball bearing (9), sleeve washer (11), deep Groove ball bearing (12), characterized in that: the planetary gear system of the traditional automobile differential is abandoned, and replaced by the system of "external teeth, inner center wheel, double roller block, multi-phase outer cam". It mainly includes the inner center wheel with external teeth (1), the left axle frame (2), double roller blocks (5), and the multi-phase outer cam (6) of the right axle, and realizes the differential speed with this system to form a differential gear; The outside of the external tooth inner center wheel (1) is a straight bevel gear, and the inside is an internal gear with multiple protruding parts. The number of the protruding parts is the number of teeth of the external tooth inner center wheel (1), which is denoted as Z ₁ , so the external-toothed inner sun gear (1) is not only a bevel gear of the main reducer, but also an inner gear in the differential mechanism, and the outer-toothed inner sun gear (1) organically connects the final drive and the differential Integrate into one body, the outer tooth inner center wheel (1) and the right half shell (4) are fixedly connected by screws (8) to form a whole and supported on the frame by a pair of tapered roller bearings (3); the left half shaft frame (2) is a sleeve structure, the sleeve structure is installed in the internal gear of the external tooth inner center wheel (1), Z ₂ radial guide grooves are opened along the circumference of the sleeve structure, and double rollers are installed in the guide grooves. Sub-block (5), the left end of the left half-axle frame (2) is the left half-axle, and the left half-axle frame (2) is fixedly connected with the left rear wheel (13) by the left half-axle, and the left half-axle frame (2) is formed by A pair of deep groove ball bearings (12) are supported in the external gear inner center wheel (1); the right half-shaft multi-phase external cam (6) is a three-phase cam with three mutually symmetrical bulging parts at an angle of 120° and axial symmetry. Outer phase cam, its own mass is completely balanced, and its contour curve is a cosine curve. The multiphase outer cam (6) of the right half shaft is embedded in the sleeve structure of the left half shaft frame (2), and the multiphase outer cam of the right half shaft The right end of (6) is the right half-shaft, and the multi-phase outer cam (6) of the right half-shaft is fixedly connected together with the rear wheel (14) on the right by the right half-shaft, and the left end of the multi-phase outer cam (6) of the right half-shaft passes through the deep The groove ball bearing (9) is supported in the left half shaft frame (2), and the right end is supported in the right half shell (4) through the deep groove ball bearing (7); the above-mentioned double roller block (5) is supported by the bracket block ( 15), pin (16), needle roller (17), needle roller sleeve (18), the two ends of the pin (16) and the holes on both sides of the bracket block (15) are tightly fitted, and the two rollers The needle sleeves (18) are all supported by pins (16) and form a rolling connection relationship with the support block (15) through the needle rollers (17); the two needle roller sleeves (18) of the double roller block (5) can be The inner wall of the radial guide groove of the sleeve structure of the left axle frame (2) rolls radially, so that a rolling connection is formed between the double roller blocks (5) and the left axle frame (2), and the double roller blocks ( 5) The arc-shaped outer surfaces at both ends are respectively connected with the outer cam profile of the right half-shaft multi-phase outer cam (6) and the inner gear teeth of the outer tooth inner center wheel (1) The profiles mesh with each other to form a high pair; the internal gear tooth profile curve of the external tooth inner center wheel (1) is that the double roller block (5) rotates with the left axle frame (2) on the one hand, and on the other hand In the process of moving in the radial guide groove of the pedestal ( ₂ ), the envelope line of a series of positions on the arc-shaped outer surface of the inner end; ) the number Z ₂ differs by 3. 2. The internal gear with any tooth difference according to claim 1 drives a double-roller block type automobile differential, characterized in that: the double-roller block and the right half-shaft multi-phase outer cam, the outer tooth inner center wheel, the left half Multiple pairs of gears mesh with each other at the same time between the shaft frames, and up to 50% of the double roller blocks can participate in the meshing work at the same time. The degree of overlap is high, the bearing capacity is high, and high-power, high-torque differential transmission can be realized. 3. The internal gear with any tooth difference according to claim 1 drives the double roller block type automobile differential, characterized in that: the pure rolling engagement between the double roller block and the left axle frame, so the differential speed of the present invention High transmission efficiency.