CN111998042A

CN111998042A - Bead tooth meshing mechanism and speed change device adopting same

Info

Publication number: CN111998042A
Application number: CN202011000659.9A
Authority: CN
Inventors: 肖多娇
Original assignee: Individual
Current assignee: Individual
Priority date: 2020-09-22
Filing date: 2020-09-22
Publication date: 2020-11-27

Abstract

A ball tooth meshing mechanism and a speed change device adopting the same relate to a meshing transmission mechanism and a speed changer. The ball gear transmission device comprises a box body, wherein a rotating disc is arranged in the box body, 1 to a plurality of ball annular gear rings which are formed by a plurality of balls with the same size in an equidistant mode are arranged on the rotating disc, a driving shaft capable of driving the rotating disc to rotate is arranged on the rotating disc in the radius direction of the rotating disc, a driven shaft driven by the rotating disc is arranged in the other radius direction of the rotating disc, and a first ball meshing gear and a second ball meshing gear which can slide on the driving shaft and the driven shaft in the shaft and can be meshed with the ball annular gear rings on the rotating disc are arranged on the driving shaft and the driven shaft respectively. The invention overcomes the limitation of the prior art, has extremely simple structure, compact structure, large speed change range, wide application range, can realize the power output of large torque and low rotating speed, can also realize the power output of small torque and high rotating speed, can be used for the speed change of various machines, and is particularly suitable for the speed change of pure electric vehicles.

Description

Bead tooth meshing mechanism and speed change device adopting same

Technical Field

The invention relates to a meshing transmission mechanism and a speed changer, in particular to a bead tooth meshing mechanism and a speed changer adopting the bead tooth meshing mechanism.

Background

The meshing transmission mechanism is the most basic mechanism in machinery, and mainly comprises straight tooth meshing, bevel tooth meshing, worm gear meshing, herringbone tooth meshing and the like, and has the limitation that teeth of the meshing transmission mechanism can only be distributed on a cylinder and cannot be distributed on a rotating plane, and further cannot realize the meshing of the rotating plane teeth and the straight tooth gears.

The existing various machines including the speed variator used for automobile and internal combustion engine have two categories of step speed variator and stepless speed variator. The step-variable transmission is a gear transmission and is composed of gear assemblies with different gear ratios, and different gear ratio transmission is realized by switching gear assemblies with different sizes.

As disclosed in chinese patent publication No.: CN111396516A (2020.07.10) discloses a planetary gear transmission device for an electric vehicle, which comprises: the brake device comprises a first rotating shaft, a second rotating shaft, a third rotating shaft, a fourth rotating shaft, a box body, a first planetary gear set, a second planetary gear set, a first brake and a second brake; the sun gear of the first planetary gear set is arranged on a first rotating shaft, the planet carrier is arranged on a second rotating shaft, the gear ring is positioned on a third rotating shaft, the sun gear of the second planetary gear set is arranged on the first rotating shaft, the planet carrier is arranged on the third rotating shaft, the gear ring is arranged on a fourth rotating shaft, the first brake is connected with the third rotating shaft and the box body, the second brake is connected with the fourth rotating shaft and the box body, the driving motor inputs power into the first rotating shaft, and the second rotating shaft outputs the power to the wheels. The two gears with different speed ratios are realized, a compact structure is kept, and meanwhile, a large transmission ratio is obtained, so that the gear is particularly suitable for electric automobiles. But has the disadvantages of complex structure, relatively large volume, high manufacturing cost, larger friction coefficient and lower transmission efficiency.

The continuously variable transmission comprises a metal V belt friction type continuously variable transmission, a gear pump type continuously variable transmission, a hydraulic continuously variable transmission and a chain transmission continuously variable transmission, the working principles of the continuously variable transmission are different, the technical difficulty is higher compared with a gear transmission, and the manufacturing cost is higher.

For example, chinese patent publication No. CN111255866A (2020.06.09) discloses a chain transmission stepless speed change device, which discloses the following technologies: the device mainly comprises a sliding seat base plate system, a sliding support, a chain wheel system, a speed regulation conical disc, a control system, a chain and a main shaft transmission system. The slide base plate system is one of the main devices of power input, output and intermediate power transmission, and is configured in pairs, two are a pair, one is power input and the other is power output, and can be cascaded, the output of the previous pair is used as the input of the next pair, the more the cascade number is, the larger the stepless speed change range is, and the total speed change ratio is the product of all stages of speed change ratios. The sliding support and chain wheel system is a chain wheel group supported by the sliding support, and mainly comprises a main sliding support, a secondary sliding support, a main chain wheel, a secondary chain wheel, a chain wheel limit nut, a chain wheel tension spring and the like. The speed regulating conic disc and control system as the main speed regulating controller consists of conic disc, bearing, displacement support, speed regulating pull wire, displacement controller, etc. The chain and main shaft transmission system is a main device for power input, power intermediate transmission and power output, and mainly consists of input shaft, output shaft, intermediate transmission shaft (two-pair or more linkage system), chain, guide chain wheel and tension chain wheel. The chain-driven stepless speed change device can be used in various mechanical devices requiring speed change, in particular in the field of automobiles, is connected with a planetary gear speed changer, can realize forward and reverse control, improves the speed change ratio range, can adapt to a larger torque system, has higher mechanical efficiency, can change speed smoothly and continuously, can be controlled in an open loop mode and a closed loop mode, and is simple and reliable in speed change control. But has the problems of complex structure, large volume, high cost and low transmission efficiency.

Disclosure of Invention

One of the purposes of the invention is to break through the limitation of the prior art and disclose a bead tooth meshing mechanism which can distribute teeth on a rotating plane and realize the meshing of the rotating plane teeth and a straight tooth gear.

The invention also aims to overcome the limitations of the prior art and discloses a speed change device which is simple in structure, small in size, large in speed change range and wide in application range, and is particularly suitable for pure electric vehicles.

One of the technical solutions of the present invention is: the bead tooth meshing mechanism comprises a driving gear and a driven gear, and is characterized in that the driven gear consists of a rotating disc and a concentric bead annular gear ring which is arranged on the rotating disc and consists of a plurality of beads with the same size at equal intervals, the driving gear is a bead meshing gear, and a concave arc-shaped structure corresponding to the beads is formed between two teeth of the bead meshing gear, so that the bead meshing gear can be meshed with the bead annular gear ring.

Further, the arc length L1 between the central points of two adjacent ball teeth on the concentric ball annular gear ring is equal to the arc length L2 between two teeth of the ball tooth wheel.

Further, the diameter of the concentric ball annular ring gear is Φ = L2 × the number of ball teeth ÷ pi.

The second technical solution of the invention is as follows: adopt ball tooth engagement mechanism's speed change gear, including the box, its special character lies in: the box body is internally provided with a rotating disc connected with an output shaft, the rotating disc is provided with 1 to a plurality of ball annular gear rings which are formed by a plurality of balls with the same size at equal intervals, and a first ball meshing gear which can be meshed with the ball annular gear rings and drives the rotating disc to rotate and is connected with a driving shaft is arranged on the rotating disc.

The third technical solution of the invention is: adopt ball tooth engagement mechanism's speed change gear, including the box, its special character lies in: the ball gear box is characterized in that a rotating disc is arranged in the box body, 1 to a plurality of ball annular gear rings which are formed by a plurality of balls with the same size at equal intervals are arranged on the rotating disc, and a first ball meshing gear which can be meshed with the ball annular gear rings and drives the rotating disc to rotate and is connected with a driving shaft and a second ball meshing gear which can be meshed with the ball annular gear rings and is driven by the rotating disc and connected with a driven shaft are arranged on the rotating disc.

Furthermore, the driving shaft is provided with a driving shaft sliding key, and the first ball-shaped gear wheel is matched with the driving shaft sliding key through a sliding key groove formed in a center hole of the first ball-shaped gear wheel and can slide on the driving shaft, so that the first ball-shaped gear wheel can be meshed with any ball-shaped annular gear ring of the rotating disc.

Furthermore, a driven shaft sliding key is arranged on the driven shaft, and the second ball-shaped gear wheel is matched with the driven shaft sliding key through a sliding key groove formed in a central hole of the second ball-shaped gear wheel and can slide on the driven shaft, so that the second ball-shaped gear wheel can be meshed with any ball-shaped annular gear ring of the rotating disc.

Furthermore, the included angle between the driven shaft and the driving shaft can be 180 ℃, or 90 ℃ or other angles.

Further, the number of the ball annular gear rings is at least 1, generally 2-10, and commonly 3-5 according to the requirement.

Furthermore, the ball is a solid ball, and the height of the ball on the rotating disc ensures the normal meshing and the normal power transmission with the corresponding ball-engaging wheel

Furthermore, the ball is a solid sphere, and the height of the rotating disc can be 70% -30% of the original height, and is generally 60% -50%.

Furthermore, a first shifting fork capable of enabling the first ball gear to slide is sleeved on the first ball gear, and a second shifting fork capable of enabling the second ball gear to slide is arranged on the second ball gear.

Furthermore, the rotating disc is provided with a central hole, a rotating disc bearing is arranged in the central hole, a support column is arranged in the rotating disc bearing, a central bearing seat is arranged at the top of the support column, and a first driving shaft bearing and a first driven shaft bearing which operate independently are arranged in the central bearing seat.

Furthermore, a first bearing seat and a second bearing seat are arranged on the side wall of the box body, a second driving shaft bearing is arranged in the first bearing seat, and a second driven shaft bearing is arranged in the second bearing seat.

Furthermore, a large thrust bearing is arranged between the rotating disc and the inner bottom of the box body, a small thrust bearing is arranged in the middle of the large thrust bearing, a large lantern ring clamped in the upper portion of the large thrust bearing and a small lantern ring clamped in the upper portion of the small thrust bearing are arranged at the bottom of the rotating disc, a large fixing ring clamped outside the lower portion of the large thrust bearing and a small fixing ring clamped outside the lower portion of the small thrust bearing are arranged on the inner bottom surface of the box body, and the bottom surface of the rotating disc is supported by the top surface of the thrust bearing.

Furthermore, a box cover is arranged on the box body, and a moving groove corresponding to the movement track of the shifting fork is formed in the box cover.

By adopting the technical scheme, the bead tooth meshing mechanism can arrange the bead teeth on a plane to form concentric bead annular gear rings with different diameters and sizes, which can be meshed with the straight-tooth gear, so that a novel meshing transmission mode is provided for machinery, and the gear ring is simple in structure, easy to machine, low in cost and wide in application. The speed change device adopting the bead tooth meshing mechanism overcomes the problems in the prior art, has extremely simple structure, and reduces the number of parts by about 90 percent; the structure is compact, and the volume is only about one tenth of that of the prior art; the driving shaft and the driven shaft are simultaneously meshed with a concentric ball annular gear ring formed by balls on a rotating disc for transmission, so that the speed change gear is obviously increased, if the number of the concentric ball annular gear rings is increased, the speed change gear can be close to the stepless speed change, and the speed change range is several times of the stepless speed change gear; the invention can realize the power output with large torque and low rotating speed, can also realize the power output with small torque and high rotating speed, has wide application range, can be used for the speed change of various machines, and is particularly suitable for the speed change of pure electric vehicles.

Drawings

FIG. 1 is a schematic front view of a ball and tooth engagement mechanism according to the present invention;

FIG. 2 is a schematic top view of the ball and tooth engagement mechanism of the present invention;

FIG. 3 is a perspective view of one embodiment of a transmission incorporating a ball and tooth engagement mechanism according to the present invention;

FIG. 4 is one of the schematic cross-sectional views of an embodiment of the transmission of the present invention employing a ball and tooth engagement mechanism;

FIG. 5 is a schematic, disassembled view of an embodiment of the transmission incorporating the ball and tooth engagement mechanism of the present invention;

FIG. 6 is a second perspective view of an embodiment of the transmission of the present invention employing a ball and tooth engagement mechanism;

FIG. 7 is a second schematic cross-sectional view of an embodiment of the transmission of the present invention employing a ball and tooth engagement mechanism;

FIG. 8 is a second exploded perspective view of the transmission embodiment of the present invention employing a ball and tooth engagement mechanism;

FIG. 9 is one of the schematic views of the rotatable disk of the transmission of the present invention employing a ball and tooth engagement mechanism;

FIG. 10 is a second schematic view of the rotating disc of the transmission employing the ball and tooth engagement mechanism of the present invention;

FIG. 11 is a third schematic view of a rotating disk of the transmission incorporating the ball and tooth engagement mechanism of the present invention;

FIG. 12 is a schematic structural view of a transmission housing employing a ball and tooth engagement mechanism according to the present invention.

Reference numerals: 1-case lid, 2-case lid screw, 3-drive shaft, 4-first ball gear, 5-turn disc, 6-case, 7-fixed part, 8-ball, 9-pillar, 10-central bearing seat, 11-second ball gear, 12-driven shaft, 13-driven shaft sliding key, 14-ball ring gear, 15-second fork, 16-drive shaft sliding key, 17-first fork, 18-moving groove, 19-second drive shaft bearing, 20-large fixed ring, 21-large collar, 22-inner bottom, 23-small fixed ring, 24-small thrust bearing, 25-large thrust bearing, 26-first driven shaft bearing, 27-second driven shaft bearing, 28-first drive shaft bearing, 29-rotating disc bearing, 30-second bearing seat, 31-central hole, 32-small collar, 33-first bearing seat.

Detailed Description

In order that the invention may be more clearly understood, a particular embodiment thereof will now be described in further detail with reference to figures 1-12.

Embodiment 1: the bead tooth meshing mechanism comprises a driving gear and a driven gear, wherein the driven gear is composed of a rotating disc 5 and a concentric bead annular gear ring 14 which is arranged on the rotating disc 5 and is composed of a plurality of beads 8 with the same size in an equidistant mode, the driving gear is a bead meshing gear, and a concave arc-shaped structure corresponding to the beads 8 is formed between two teeth of the bead meshing gear, so that the bead meshing gear can be meshed with the bead annular gear ring 14.

The arc length L1 between the central points of two adjacent ball teeth on the concentric ball annular gear ring 14 is equal to the arc length L2 between two teeth of the ball tooth wheel.

The diameter Φ of the concentric ball annular ring gear 14 = the arc length L2 between two teeth of the ball-engaging wheel × the number of ball teeth of the concentric ball annular ring gear ÷ pi.

The tooth ratio of the bead gear to the concentric bead ring gear is the diameter of the bead gear divided by the diameter of the center line of the concentric bead ring gear.

The width H1 of the ball gear is larger than the diameter of the ball and smaller than the spacing width H between two adjacent concentric ball annular gear rings.

The shape and the size of the concave circular arc between the two teeth of the ball-point engaging wheel are matched with the arc shape and the size of the ball point.

The arc shape of the ball 8 can be arc shape or elliptic arc shape.

The ball 8 is a solid ball and the height above the rotating disc ensures normal engagement and normal power transfer with the corresponding ball-engaging wheel.

The ball 8 is a solid ball, and the height of the rotating disc can be 70% -30% of the original height, and is generally 60% -50%.

The ball teeth are arranged on the plane to form concentric ball annular gear rings with different diameters, and the straight gear is processed into a concave arc structure matched with the ball teeth, so that the straight gear is meshed with the ball teeth. Because the ball teeth on the ball annular gear rings with different diameters are the same parameter ball teeth, the same straight gear can be meshed with the ball annular gear rings with different diameters for transmission, a new meshing transmission mode is provided for machinery, and the transmission mechanism is simple in structure, easy to machine, low in cost and wide in application.

Embodiment 2: adopt ball tooth engagement mechanism's speed change gear, including box 6, be equipped with the rolling disc 5 of connecting the output shaft in box 6, be equipped with 1 to a plurality of ball annular ring gears 14 of constituteing by a plurality of equidimension ball equidistance on rolling disc 5, be equipped with on rolling disc 5 can mesh and drive rolling disc 5 pivoted first ball tooth wheel 4 of connecting driving shaft 3 with ball annular ring gear 14. The output shaft of the rotating disc 5 may be output by a central shaft.

Embodiment 3: adopt change gear of pearl tooth engagement mechanism, including box 6, be equipped with rolling disc 5 in box 6, be equipped with 1 to a plurality of pearl annular ring gears 14 of constituteing by 8 equidistance of a plurality of equidimensions of ball on rolling disc 5, be equipped with on rolling disc 5 can mesh and drive rolling disc 5 pivoted first pearl tooth wheel 4 of being connected driving shaft 3 with pearl annular ring gear 14 and can mesh with pearl annular ring gear 14 and be connected second pearl tooth wheel 11 by driven shaft 12 that rolling disc 5 driven.

Furthermore, the driving shaft 3 is provided with a driving shaft sliding key 16, and the first ball-and-pinion type wheel 4 is matched with the driving shaft sliding key 16 through a sliding key groove arranged on a central hole of the driving shaft and can slide on the driving shaft so as to be meshed with any ball-and-ring type gear ring 14 of the rotating disc 5.

Furthermore, a driven shaft sliding key 13 is arranged on the driven shaft 12, and the second ball gear 11 is matched with the driven shaft sliding key 13 through a sliding key groove arranged on a central hole of the second ball gear and can slide on the driven shaft 12 so as to be meshed with any ball annular gear ring 14 of the rotating disc 5.

The included angle between the driven shaft 12 and the driving shaft 3 can be 180 ℃, or 90 ℃, or any other angle.

The number of the ball annular gear rings 14 is at least 1, generally 2-10, and commonly 3-5 according to the requirement.

The width H1 of the ball gear is larger than the diameter of the ball 8 and smaller than the spacing width H between two adjacent concentric ball annular gear rings.

The shape and the size of the concave circular arc between the two teeth of the ball-point engaging wheel are matched with the arc shape and the size of the ball 8.

The arc shape of the ball 8 can be arc shape or elliptic arc shape.

The ball 8 is a solid ball and the height above the rotating disc 5 is such as to ensure normal engagement and normal power transmission with the corresponding ball-engaging wheel.

The ball 8 is a solid sphere and can be 70-30%, typically 60-50% of the original height (diameter) above the rotating disc 5.

The first ball-point gear 4 is sleeved with a first shifting fork 17 which can enable the first ball-point gear to slide, and the second ball-point gear 11 is provided with a second shifting fork 15 which can enable the second ball-point gear to slide.

The rotating disc 5 is provided with a central hole 31, a rotating disc bearing 29 is arranged in the central hole 31, a support column 9 is arranged in the rotating disc bearing 29, a central bearing seat 10 is arranged at the top of the support column 9, and a first driving shaft bearing 28 and a first driven shaft bearing 26 which operate independently are arranged in the central bearing seat 10.

A first bearing seat 33 and a second bearing seat 30 are provided on the side wall of the housing 6, a second driving shaft bearing 19 is provided in the first bearing seat 33, and a second driven shaft bearing 27 is provided in the second bearing seat 30.

A large thrust bearing 25 is arranged between the rotating disc 5 and the inner bottom 22 of the box body 6, a small thrust bearing 24 is arranged in the middle of the large thrust bearing 25, a large lantern ring 21 clamped in the upper portion of the large thrust bearing 25 and a small lantern ring 33 clamped in the upper portion of the small thrust bearing 24 are arranged at the bottom of the rotating disc 5, a large fixing ring 20 clamped on the outer side of the lower portion of the large thrust bearing 25 and a small fixing ring 23 clamped on the outer side of the lower portion of the small thrust bearing 24 are arranged on the inner bottom surface of the box body 6, and the bottom surface of the rotating disc 5 is supported by the top surface of.

The box body 6 is provided with a box cover 1, and the box cover 1 is provided with a moving groove 18 corresponding to the moving direction of the shifting fork.

The driving shafts can be arranged in a plurality of numbers, and a plurality of power can be input simultaneously.

The driven shaft can be provided with a plurality of driven shafts, so that a plurality of powers can be output simultaneously.

During the design, according to the size of driving force earlier, design the size of the ball pinion teeth of a cogwheel and the diameter of ball 8, make it satisfy mechanical strength's needs at first, design the number of teeth of ball pinion, the quantity of ball ring gear ring and the number of teeth of ball ring gear ring again according to the needs of speed change scope.

The implementation mode overcomes the limitation of the prior art, the structure is extremely simple, and the number of parts is reduced by about 90%; the structure is compact, and the volume is only about one tenth of that of the prior art; the driving shaft and the driven shaft are simultaneously meshed with concentric ball annular gear rings on the rotating disc, wherein the concentric ball annular gear rings are different in diameter, so that the number of speed change gears is obviously increased; because the direction of the driven shaft can be changed in a large range, the power output in any direction can be realized theoretically; the addition of a driving shaft or a driven shaft can realize multiple power inputs or multiple power outputs. The invention can realize the power output with large torque and low rotating speed and the power output with small torque and high rotating speed due to the large speed change range, has wide application range, can be used for the speed change of various machines, and is particularly suitable for the speed change of pure electric vehicles.

Example 1: as shown in fig. 1-2, the bead-tooth engaging mechanism includes a driving gear and a driven gear, the driven gear is composed of a rotating disk 5 and a concentric bead ring-shaped gear ring 14 which is arranged on the rotating disk 5 and is composed of a plurality of equally spaced beads 8 with the same size, the driving gear is a bead-tooth wheel 4, and a concave arc-shaped structure corresponding to the beads 8 is formed between two teeth of the bead-tooth wheel 4, so that the driving gear can be engaged with the bead ring-shaped gear ring 14. The arc length L1 between the central points of two adjacent ball teeth on the concentric ball annular gear ring 14 is equal to the arc length L2 between two teeth of the ball tooth wheel. The ball 8 is a solid sphere and is at a height above the rotatable disc 5 to ensure proper engagement and proper power transfer with the corresponding ball-engaging wheel.

Example 2: as shown in fig. 1-2, the bead-tooth engaging mechanism includes a driving gear and a driven gear, the driven gear is composed of a rotating disk 5 and a concentric bead ring-shaped gear ring 14, which is arranged on the rotating disk 5 and is composed of 30 beads 8 with the same size at equal intervals, the driving gear is a bead-tooth wheel 4, and a concave arc-shaped structure corresponding to the beads 8 is formed between two teeth of the bead-tooth wheel 4, so that the driving gear can be engaged with the bead ring-shaped gear ring 14. The arc length L1 between the central points of two adjacent ball teeth on the concentric ball annular gear ring 14 is equal to the arc length L2 between two teeth of the ball tooth wheel. The diameter Φ = L2 × number of beads ÷ pi of concentric bead ring gear 14. The tooth ratio of the beaded wheel 4 to the concentric bead ring rim 14 is the diameter of the beaded wheel 4 divided by the diameter of the center line of the concentric bead ring rim 14. The ball 8 is a solid ball and the height h of the rotating disc 5 is 50% of the original height (diameter) of the solid ball.

Example 3: pearl tooth engagement mechanism, including driving gear and driven gear, driven gear comprises rolling disc 5, establishes that concentric circular bead ring gear 14 that 8 equidistance of 24 balls of the same size constitute on rolling disc 5 constitutes, the driving gear is pearl pinion, makes the concave circular arc shape structure corresponding with ball 8 between two teeth of pearl pinion, and the diameter of pearl pinion is 60mm, and the number of teeth is 12, realizes that pearl ring gear 14 meshes with the epaxial pearl pinion of transmission mutually. The arc length L1 between the center points of two adjacent ball teeth on the concentric ball annular gear ring 14 is equal to the arc length L2 between two teeth of the ball tooth wheel, and is 15.7 mm. Arc length between two teeth of the beaded wheel = diameter × pi ÷ number of teeth. The diameter of the ball spline gear was designed to be 6Omm with 12 teeth sets and the arc length between the two teeth =60 x 3.14 ÷ 12=15.7 mm. In the present embodiment, the gear ratio of the ball spline gear to the ball annular ring gear 14 is set to 1: 2, the number of teeth of the ball annular ring gear 14 is set to 24, and the size position of the ball annular ring gear 14, that is, the diameter Φ = L2 × the number of teeth of the ball ÷ pi =15.7mm × 24 ÷ pi =120 mm. If a ball annular gear ring is arranged, the diameter of the ball annular gear ring is determined according to the number of teeth of the ball to be arranged, the number of teeth of the ball can also be determined according to the diameter of the designed ball annular gear ring, and the diameter of the ball annular gear ring can be properly corrected during design because the number of teeth of the ball is only an integer. The ball 8 is a solid sphere and has a height above the rotating disc 5 of 70% of the original height (diameter).

The above embodiment can arrange the ball teeth on a plane by adopting the ball teeth to form concentric ball annular gear rings with different diameters, and the straight gear is processed into a concave arc structure matched with the ball teeth, so that the meshing of the straight gear and the ball teeth is realized. Because the ball teeth on the ball annular gear rings with different diameters are the same parameter ball teeth, the same straight gear can be meshed with the ball annular gear rings with different diameters for transmission, a new meshing transmission mode is provided for machinery, and the transmission mechanism is simple in structure, easy to machine, low in cost and wide in application.

Example 4: adopt ball tooth engagement mechanism's speed change gear, including box 6, be equipped with the rolling disc 5 of connecting the output shaft in box 6, be equipped with 1 ball annular ring gear 14 of constituteing by a plurality of equidistance of the ball of equidimension on rolling disc 5, be equipped with on rolling disc 5 and mesh wheel 4 with ball annular ring gear 14 and drive rolling disc 5 pivoted first ball of being connected driving shaft 3. The arc length L1 between the center points of two adjacent ball teeth on the concentric ball annular gear ring 14 is equal to the arc length L2 between two teeth of the ball tooth wheel. The diameter Φ = L2 ∗ bead tooth count ÷ pi of the concentric bead annular ring gear 14. The power transmission output of the rotating disc 5 can be directly output by a central shaft (refer to fig. 1), and the ball-and-socket wheel 4 is fixedly meshed with only 1 ball-and-socket ring gear 14, and the speed is changed into fixed speed change. The arc length L1 between the center points of two adjacent ball teeth on the concentric ball annular gear ring 14 is equal to the arc length L2 between two teeth of the ball tooth wheel. The diameter of the ball 8 is 18mm and the height of the rotating disk 5 is 10 mm. First pearl ring gear 4 number of teeth 15, ball annular ring gear number of teeth 60 can realize 4: 1, fixed deceleration.

Example 5: referring to fig. 3-8, the speed change device using the ball-and-tooth meshing mechanism comprises a box body 6, a rotating disk 5 is arranged in the

box body

6, 2 ball-and-ring gear rings 14 which are formed by a plurality of balls 8 with the same size at equal intervals are arranged on the rotating disk 5, a first ball-and-tooth wheel 4 which can be meshed with the ball-and-ring gear rings 14 and drives the rotating disk 5 to rotate and is connected with a driving shaft 3 and a second ball-and-tooth wheel 11 which can be meshed with the ball-and-ring gear rings 14 and is driven by the rotating disk 5 and connected with a driven shaft 12 are arranged on the rotating disk 5. The arc length L1 between the center points of two adjacent ball teeth on the concentric ball annular gear ring 14 is equal to the arc length L2 between two teeth of the ball engaging wheel, and the height of the ball 8 on the rotating disc 5 is 55% of the original height (diameter). The first ball meshing gear 4 is meshed with the large ball annular gear ring 14 to drive the rotating disc 5 to rotate, and the second ball meshing gear 11 is meshed with the small ball annular gear ring 14 and driven by the rotating disc 5. The diameter of the ball 8 is 18mm and the height of the rotating disk 5 is 9 mm. The number of teeth of the first bead meshing gear, the large ball annular gear ring, the small ball annular gear ring and the second bead meshing gear is respectively 10, 60, 30 and 30, and 6 can be realized: 1, fixed deceleration.

Example 6: as shown in fig. 3-8, the speed change device using the ball-and-tooth meshing mechanism comprises a box body 6, a rotating disk 5 is arranged in the

box body

6, 3 ball-and-ring gear rings 14 which are formed by a plurality of balls with the same size at equal intervals are arranged on the rotating disk 5, and a first ball-and-tooth wheel 4 which can be meshed with the ball-and-ring gear rings 14 and drives the rotating disk 5 to rotate and is connected with a driving shaft 3 and a second ball-and-tooth wheel 11 which can be meshed with the ball-and-ring gear rings 14 and is driven by the rotating disk 5 and connected with a driven shaft 12 are arranged on the rotating disk 5. The driving shaft 3 is provided with a driving shaft sliding key 16, and the first ball-and-pinion type wheel 4 is matched with the driving shaft sliding key 16 through a sliding key groove arranged on a central hole of the driving shaft and can slide on the driving shaft so as to be meshed with any ball-and-ring type gear ring 14 of the rotating disc 5. The driving shaft 3 and the driven shaft 12 are provided with one supporting bearing on the wall of the box body 6, and the other supporting bearing is arranged outside the box body 6. The arc length L1 between the center points of two adjacent ball teeth on the concentric ball annular gear ring 14 is equal to the arc length L2 between two teeth of the ball engaging wheel, and the height of the ball 8 on the rotating disc 5 is 60% of the original height (diameter). The ball 8 is oval, the major diameter is 20, the minor diameter is 18mm, the height of the rotating disc 5 is 12 mm, and the ball 8 is welded on the rotating disc 5. The number of teeth of the ball annular gear ring is respectively set to 100, 60 and 20 from the 1 st to the 3 rd circles, the number of teeth of the first ball meshing gear (driving gear) and the second ball meshing gear (driven gear) is 15, and the maximum transmission ratio is 5: 1.

example 7: referring to fig. 3-8, the speed change device using the ball-and-teeth meshing mechanism comprises a box body 6, a rotating disk 5 is arranged in the

box body

6, 5 ball-and-ring gear rings 14 which are formed by a plurality of balls with the same size at equal intervals are arranged on the rotating disk 5, a first ball-and-tooth wheel 4 which can be meshed with the ball-and-ring gear rings 14 and drives the rotating disk 5 to rotate and is connected with a driving shaft 3 and a second ball-and-tooth wheel 11 which can be meshed with the ball-and-ring gear rings 14 and is driven by the rotating disk 5 and connected with a driven shaft 12 are arranged on the rotating disk 5. The driving shaft 3 is provided with a driving shaft sliding key 16, and the first ball-and-pinion type wheel 4 is matched with the driving shaft sliding key 16 through a sliding key groove arranged on a central hole of the driving shaft and can slide on the driving shaft so as to be meshed with any ball-and-ring type gear ring 14 of the rotating disc 5. The driving shaft 3 and the driven shaft 12 are provided with one supporting bearing on the wall of the box body 6 and the other supporting bearing is arranged outside the box body 6 (not shown). The driven shaft 12 is provided with a driven shaft sliding key 13, and the second ball gear 11 is matched with the driven shaft sliding key 13 through a sliding key groove arranged on a central hole of the second ball gear and can slide on the driven shaft 12 so as to be meshed with any ball annular gear ring 14 of the rotating disc 5. The sliding of the first ball-toothed wheel 4 and the second ball-toothed wheel 11 may be urged using a hydraulic mechanism or a pneumatic mechanism. The diameter of the ball 8 is 26mm, the height of the rotating disc 5 is 15 mm, and the ball 8 and the rotating disc 5 are integrally cast. The number of teeth of the ball annular gear ring is 150, 120, 80, 50 and 20 in the 1 st to 5 th circles, the number of teeth of the first ball meshing gear (driving gear) is 10, the number of teeth of the second ball meshing gear (driven gear) is 30, and the transmission ratio range is 3: 1-22.5: 1. as the functions of the driving shaft and the driven shaft can be interchanged, the speed increasing and the speed reducing of up to 21.5 times can be realized.

Example 8: referring to fig. 3-5, 9-12, a speed change gear using a ball-tooth meshing mechanism is provided with a case 6, a rotating disk 5 is arranged in the

case

6, 6 ball ring-shaped gear rings 14 composed of a plurality of balls 8 with the same size are arranged on the rotating disk 5 at equal intervals, a driving shaft 3 capable of driving the rotating disk 5 to rotate is arranged on the rotating disk 5 along the radius direction of the rotating disk, a driven shaft 12 driven by the rotating disk 5 is arranged on the rotating disk 5 along the other radius direction of the rotating disk, and the included angle between the driven shaft 12 and the driving shaft 3 is 180 ℃. The arc length L1 between the two adjacent ball tooth central points on the concentric ball annular gear ring 14 is equal to the arc length L2 between two teeth of the ball gear wheel, the height of the ball 8 on the rotating disk 5 is 50% of the original height (diameter), and a first ball gear wheel 4 and a second ball gear wheel 11 which can slide on the driving shaft 3 and the driven shaft 12 and can be meshed with the ball annular gear ring 14 on the rotating disk 5 are respectively arranged on the driving shaft 3 and the driven shaft 12. The central hole 31 of the rotating disc 5 is internally provided with a rotating disc bearing 29, the rotating disc bearing 29 is internally provided with a support column 9, the top of the support column 9 is provided with a central bearing seat 10, and the central bearing seat 10 is internally provided with a first driving shaft bearing 28 and a first driven shaft bearing 26 which operate independently. A first bearing housing 33 and a second bearing housing 30 are provided on the side wall of the case 6, a second drive shaft bearing 19 is provided in the first bearing housing 33, and a second driven shaft bearing 27 is provided in the second bearing housing 30. The driving shaft 3 and the driven shaft 12 are respectively provided with a driving shaft sliding key 16 and a driven shaft sliding key 13, the first ball-meshed gear 4 is matched with the driving shaft sliding key 16 through a sliding key groove arranged on a central hole of the first ball-meshed gear, and the second ball-meshed gear 11 is matched with the driven shaft sliding key 13 through a sliding key groove arranged on a central hole of the second ball-meshed gear. The first ball-point gear 4 is sleeved with a first shifting fork 17 which can enable the first ball-point gear to slide, and the second ball-point gear 11 is provided with a second shifting fork 15 which can enable the second ball-point gear to slide. The box body 6 is provided with a box cover 1, and the box cover is provided with a moving groove 18 corresponding to the moving direction of the shifting fork. The diameter of the ball 8 is 28mm, the height of the rotating disc 5 is 15 mm, and the ball 8 and the rotating disc 5 are integrally cast. The number of teeth of the ball annular gear ring is respectively 160, 130, 100, 50 and 20 from the 1 st circle to the 6 th circle, the number of teeth of the first ball gear (driving gear) is 10, the number of teeth of the second ball gear (driven gear) is 30, and the transmission ratio range is 3: 1-24: 1. because the functions of the driving shaft and the driven shaft can be interchanged, 24 times of speed increasing and speed reducing can be realized.

Example 9: as shown in fig. 6-12, the speed change device using the ball gear meshing mechanism is provided with a box body 6, a rotating disk 5 is arranged in the box body 6, 7 (not shown) ball annular gear rings 14 which are formed by a plurality of balls 8 with the same size at equal intervals are arranged on the rotating disk 5, a driving shaft 3 which can drive the rotating disk 5 to rotate is arranged on the rotating disk 5 along the radius direction of the rotating disk, a driven shaft 12 which is driven by the rotating disk 5 is arranged on the rotating disk 5 along the other radius direction of the rotating disk, and the included angle between the driven shaft 12 and the driving shaft 3 is 90 ℃. The driving shaft 3 and the driven shaft 12 are respectively provided with a first ball-engaging wheel 4 and a second ball-engaging wheel 11 which can slide on the shafts and can engage with a ball-ring-shaped gear ring 14 on the rotating disk 5. The central hole 31 of the rotating disk 5 is internally provided with a rotating disk bearing 29, the rotating disk bearing 29 is internally provided with a support column 9, the top of the support column 9 is provided with a central bearing seat 10, and the central bearing seat 10 is internally provided with a first driving shaft bearing 28 and a first driven shaft bearing 26. A first bearing housing 33 and a second bearing housing 30 are provided on the side wall of the case 6, a second drive shaft bearing 19 is provided in the first bearing housing 33, and a second driven shaft bearing 27 is provided in the second bearing housing 30. The driving shaft 3 and the driven shaft 12 are respectively provided with a driving shaft sliding key 16 and a driven shaft sliding key 13, the first ball-meshed gear 4 is matched with the driving shaft sliding key 16 through a sliding key groove arranged on a central hole of the first ball-meshed gear, and the second ball-meshed gear 11 is matched with the driven shaft sliding key 13 through a sliding key groove arranged on a central hole of the second ball-meshed gear. The first ball-point gear 4 is sleeved with a first shifting fork 17 which can enable the first ball-point gear to slide, and the second ball-point gear 11 is provided with a second shifting fork 15 which can enable the second ball-point gear to slide. The box body 6 is provided with a box cover 1, and the box cover 1 is provided with a moving groove 18 corresponding to the moving direction of the shifting fork. The cover 1 is fixed to the case 6 by bolts 2 and coupling screw holes 34. The outer side of the bottom of the box body 6 is provided with a fixing part 7 for fixing the box body 6. A large thrust bearing 25 is arranged between the rotating disc 5 and the inner bottom of the box body 6, a small thrust bearing 24 is arranged in the middle of the large thrust bearing 25, a large lantern ring 21 clamped in the upper part of the large thrust bearing 25 and a small lantern ring 33 clamped in the upper part of the small thrust bearing 24 are arranged at the bottom of the rotating disc 5, a large fixing ring 20 clamped outside the lower part of the large thrust bearing 25 and a small fixing ring 23 clamped outside the lower part of the small thrust bearing 24 are arranged on the inner bottom surface of the box body 6, and the bottom surface of the rotating disc 5 is supported by the top surface of the thrust bearing. The ball 8 is an ellipsoid, the long diameter is 30mm, the short diameter is 26mm, the ball is transversely arranged on the rotating disc 5, the short diameter is 15 mm in height on the rotating disc 5, and the ball 8 and the rotating disc 5 are integrally cast and processed. The number of teeth of the ball annular gear ring is set to 190, 160, 130, 100, 50 and 20 in the 1 st to 7 th circles respectively, the number of teeth of the first ball meshing gear (driving gear) is 20, the number of teeth of the second ball meshing gear (driven gear) is 20, and the transmission ratio range is 1: 1-9.5: 1.

example 10: referring to fig. 6-12, a speed change device using a ball-tooth meshing mechanism is provided with a case 6, a rotating disk 5 is arranged in the

case

6, 10 ball ring-shaped gear rings 14 which are formed by a plurality of balls 8 with the same size at equal intervals are arranged on the rotating disk 5, a driving shaft 3 which can drive the rotating disk 5 to rotate is arranged on the rotating disk 5 along the radius direction of the rotating disk, a driven shaft 12 which is driven by the rotating disk 5 is arranged on the rotating disk 5 along the other radius direction of the rotating disk, and the included angle between the driven shaft 12 and the driving shaft 3 is 145 ℃ or other required angles. The driving shaft 3 and the driven shaft 12 are respectively provided with a first ball-engaging wheel 4 and a second ball-engaging wheel 11 which can slide on the shafts and can engage with a ball-ring-shaped gear ring 14 on the rotating disk 5. The width of the ball gear is larger than the diameter of the ball 8 and smaller than the width of the interval between the two adjacent ball ring gears. The central hole 31 of the rotating disk 5 is internally provided with a rotating disk bearing 29, the rotating disk bearing 29 is internally provided with a support column 9, the top of the support column 9 is provided with a central bearing seat 10, and the central bearing seat 10 is internally provided with a first driving shaft bearing 28 and a first driven shaft bearing 26. A first bearing housing 33 and a second bearing housing 30 are provided on the side wall of the case 6, a second drive shaft bearing 19 is provided in the first bearing housing 33, and a second driven shaft bearing 27 is provided in the second bearing housing 30. The driving shaft 3 and the driven shaft 12 are respectively provided with a driving shaft sliding key 16 and a driven shaft sliding key 13, the first ball-meshed gear 4 is matched with the driving shaft sliding key 16 through a sliding key groove arranged on a central hole of the first ball-meshed gear, and the second ball-meshed gear 11 is matched with the driven shaft sliding key 13 through a sliding key groove arranged on a central hole of the second ball-meshed gear. The first ball-point gear 4 is sleeved with a first shifting fork 17 which can enable the first ball-point gear to slide, and the second ball-point gear 11 is provided with a second shifting fork 15 which can enable the second ball-point gear to slide. The box body 6 is provided with a box cover 1, the box cover is provided with a moving groove 18 corresponding to the moving direction of the shifting fork, the moving groove 18 is V-shaped, and the included angle is the same as that of the driving shaft and the driven shaft. The cover 1 is fixed to the case 6 by bolts 2 and coupling screw holes 34. The outer side of the bottom of the box body 6 is provided with a fixing part 7 for fixing the box body 6. A large thrust bearing 25 is arranged between the rotating disc 5 and the inner bottom of the box body 6, a small thrust bearing 24 is arranged in the middle of the large thrust bearing 25, a large lantern ring 21 clamped in the upper part of the large thrust bearing 25 and a small lantern ring 33 clamped in the upper part of the small thrust bearing 24 are arranged at the bottom of the rotating disc 5, a large fixing ring 20 clamped outside the lower part of the large thrust bearing 25 and a small fixing ring 23 clamped outside the lower part of the small thrust bearing 24 are arranged on the inner bottom surface of the box body 6, and the bottom surface of the rotating disc 5 is supported by the top surface of the thrust bearing. The diameter of the ball 8 is 28mm, the height of the rotating disc 5 is 16 mm, and the ball 8 and the rotating disc 5 are integrally cast. The numbers of teeth of the ball ring gear from 1 st to 10 th are 230, 210, 190, 160, 130, 100, 50, and 20, respectively, the number of teeth of the first ball gear (drive gear) from 15 to the number of teeth of the second ball gear (driven gear) from 30, and the transmission ratio range 2: 1-23: 1.

examples 4-10 overcome the limitations of the prior art, the structure is extremely simple, and the number of parts is reduced by about 90%; the structure is compact, and the volume is only about one tenth of that of the prior art; the driving shaft and the driven shaft are simultaneously meshed with concentric ball annular gear rings on the rotating disc, wherein the concentric ball annular gear rings are different in diameter, so that the number of speed change gears is obviously increased; because the included angle between the driven shaft and the driving shaft can be changed in a large range, the power can be output from 90 degrees, 180 degrees or other angle directions. The speed-changing range is large, so that the power output with large torque and low rotating speed can be realized, the power output with small torque and high rotating speed can also be realized, the application range is wide, and the speed-changing device can be used for the speed change of various machines, and is particularly suitable for the speed change of pure electric vehicles.

While the invention has been described with respect to specific embodiments thereof, it will be understood by those skilled in the art that various changes in form and details may be made therein without departing from the spirit and scope of the invention. Those skilled in the art can make various changes, modifications and alterations without departing from the spirit of the invention, which are equivalent to the embodiments of the invention; meanwhile, any equivalent changes, modifications and alterations of the above embodiments according to the spirit and techniques of the present invention are also within the scope of the present invention.

Claims

1. Pearl tooth engagement mechanism, including driving gear and driven gear, its characterized in that: the driven gear consists of a rotating disc and a concentric ball annular gear ring which is arranged on the rotating disc and consists of a plurality of balls with the same size at equal intervals, the driving gear is a ball meshing gear, and a concave arc-shaped structure corresponding to the balls is formed between two teeth of the ball meshing gear so as to enable the ball meshing gear to be meshed with the ball annular gear ring.

2. The bead tooth engagement mechanism of claim 1, wherein: the arc length L1 between the central points of two adjacent ball teeth on the concentric ball annular gear ring is equal to the arc length L2 between two teeth of the ball tooth wheel.

3. The bead tooth engagement mechanism of claim 1, wherein: the diameter phi of the concentric ball annular gear ring = arc length between two teeth of the ball engaging wheel x ball tooth number of the concentric ball annular gear ring ÷ pi.

4. A transmission incorporating the ball and tooth engagement mechanism as claimed in any one of claims 1 to 3, comprising a housing, wherein: the box is internally provided with a rotating disc, the rotating disc is provided with 1 to a plurality of ball annular gear rings which are formed by a plurality of balls with the same size at equal intervals, a first ball meshing gear which can be meshed with the ball annular gear rings and drives the rotating disc to rotate and is connected with a driving shaft is arranged on the rotating disc 5, and the power transmission output of the rotating disc adopts a central shaft for output.

5. A transmission incorporating the ball and tooth engagement mechanism as claimed in any one of claims 1 to 3, comprising a housing, wherein: the ball gear box is characterized in that a rotating disc is arranged in the box body, 1 to a plurality of ball annular gear rings which are formed by a plurality of balls with the same size at equal intervals are arranged on the rotating disc, and a first ball meshing gear which can be meshed with the ball annular gear rings and drives the rotating disc to rotate and is connected with a driving shaft and a second ball meshing gear which can be meshed with the ball annular gear rings and is driven by the rotating disc and connected with a driven shaft are arranged on the rotating disc.

6. The transmission adopting the ball-and-teeth engagement mechanism according to claim 4 or 5, wherein: the driving shaft is provided with a driving shaft sliding key, and the first ball-shaped gear is matched with the driving shaft sliding key through a sliding key groove formed in a center hole of the first ball-shaped gear and can slide on the driving shaft, so that the first ball-shaped gear can be meshed with any ball-shaped annular gear ring of the rotating disc.

7. The transmission adopting a ball-and-tooth engagement mechanism according to claim 5, wherein: and the second ball-shaped gear is matched with the driven shaft sliding key through a sliding key groove formed in a central hole of the second ball-shaped gear and can slide on the driven shaft, so that the second ball-shaped gear can be meshed with any ball-shaped annular gear ring of the rotating disc.

8. The transmission adopting a ball-and-tooth engagement mechanism according to claim 4, wherein: the included angle between the driven shaft and the driving shaft is 180 ℃, or 90 ℃ or other angles.

9. The transmission using a ball-and-teeth engagement mechanism according to any one of claims 4 to 6, wherein: the first ball gear is sleeved with a first shifting fork capable of enabling the first ball gear to slide, and the second ball gear is provided with a second shifting fork capable of enabling the second ball gear to slide.

10. The transmission adopting the ball-and-teeth engagement mechanism according to claim 4 or 5, wherein: a rotating disc bearing is arranged in the central hole of the rotating disc, a support column is arranged in the rotating disc bearing, a central bearing seat is arranged at the top of the support column, and a first driving shaft bearing and a first driven shaft bearing which are mutually independent are arranged in the central bearing seat.