CN114439896A

CN114439896A - Novel automobile stepless speed regulation transmission system

Info

Publication number: CN114439896A
Application number: CN202011231196.7A
Authority: CN
Inventors: 冯福荣
Original assignee: Individual
Current assignee: Individual
Priority date: 2020-11-06
Filing date: 2020-11-06
Publication date: 2022-05-06
Anticipated expiration: 2040-11-06
Also published as: CN114439896B

Abstract

The invention belongs to the technical field of speed change of automobile gearboxes, and discloses a novel automobile stepless speed regulation gearbox system which comprises an input shaft, a gearbox and an output shaft, wherein the input shaft is movably connected with a swinging column through the structure of a crank connecting rod, the bottom of the swinging column is rotatably connected with the inner side wall of the gearbox, and the eccentric shaft can drive the swinging column to swing in a reciprocating manner; the swing column is movably sleeved with a phase rotor and a phase rotor output shaft, and the output phase of the phase rotor output shaft can be changed by adjusting the displacement of the phase rotor; the output shaft of the phase mover is connected with an output shaft through a rack and pinion mechanism, so that the cycloid type reciprocating motion is converted into rotary motion; the invention utilizes the principle of a crankshaft connecting rod, a swing column is arranged between an input shaft and an output shaft of a transmission system, transmission is carried out by means of the reciprocating cycloid motion of the swing column, and the output phase distance of the output shaft of a phase mover is adjusted by a stepless motor, so as to realize different transmission ratios.

Description

Novel automobile stepless speed regulation transmission system

Technical Field

The invention relates to the technical field of automobile gearbox speed change, in particular to a novel automobile stepless speed regulation transmission system.

Background

Currently, a conventional continuously variable transmission includes a hydro-mechanical continuously variable transmission and a metal belt type continuously variable transmission. The stepless speed variator and the common automatic speed variator are mainly different in that the complex and heavy gear combination variable speed transmission is omitted, only two groups of belt wheels are used for variable speed transmission, and the contact radius of a driving wheel and a driven wheel transmission belt is changed for speed change, so that the transmission ratio can be continuously changed.

Specifically, the stepless speed changer is mainly driven by two rollers with variable diameters and a steel belt, and the speed is changed by the rollers, so that the defects of intermittent gear shifting, slow accelerator reaction, high oil consumption and the like of a common automatic speed change mechanism are overcome. However, the steel belt for transmitting energy has low strength and short service life compared with the gear, and the steel belt transmits the power through friction, so the steel belt transmits the torque and the energy of the engine, and the power transmission is not as accurate and reliable as the gear. When the continuously variable transmission is used for speed change, the rollers slide in the vertical direction for transmitting power to the steel belt, which undoubtedly destroys the static friction between the steel belt and the rollers and easily causes the slipping phenomenon, so the existing continuously variable transmission has the appearance of slow response when accelerating under speed change.

Therefore, the continuously variable transmission has the advantages of comfort, high efficiency, energy conservation and the like, but still has the defects of difficulty in bearing larger load, slow gear shifting and the like, so that the currently marketed continuously variable transmissions are mostly limited to low-power and low-torque automobiles with the displacement of about 1 liter, and the belt transmission is obviously limited to popularization and application.

Disclosure of Invention

The invention aims to solve the problems in the prior art, and provides an automobile stepless speed regulation transmission system adopting a novel transmission mode to solve the problems of small torque and slow speed regulation of a stepless speed regulation transmission in the prior art.

The above purpose of the invention is realized by the following technical scheme:

a novel automobile stepless speed regulation transmission system comprises an input shaft, a transmission case and an output shaft, wherein the input shaft extends into the transmission case and is sleeved with a flywheel at the shaft end, the end face of the flywheel is provided with equidirectional eccentric shafts in the area outside a wheel core, the eccentric shafts are movably connected with a swing shaft through a first connecting rod, the end part of the swing shaft is fixedly connected with a swing column perpendicular to the swing shaft, the bottom of the swing column is rotatably connected with the side wall of the transmission case, and the eccentric shafts can drive the swing shaft and the swing column to swing back and forth around a rotating connection point through the first connecting rod in the process of rotating around the input shaft;

the swing column is movably sleeved with a phase rotor, a phase rotor output shaft parallel to the swing shaft is arranged on the outer side of the phase rotor, the other side of the phase rotor is connected with a stepless driving device, and the phase rotor can move back and forth along the swing column under the driving action of the stepless driving device, so that the output phase of the phase rotor output shaft is changed;

the output shaft of the phase rotor is connected with a rack through a second connecting rod, and the rack is connected with the output shaft through a rack and pinion mechanism, so that the cycloidal reciprocating motion of the output shaft of the phase rotor is converted into the rotary motion of the output shaft.

The invention utilizes the principle of a crankshaft connecting rod, a swing column is arranged between an input shaft and an output shaft of a transmission system, transmission is carried out through the reciprocating cycloid motion of the swing column, and the swing output radius of the swing column is adjusted, namely the output phase distance of a phase mover output shaft is adjusted in a stepless mode, so that different transmission ratios are realized.

Specifically, the phase mover movably sleeved on the swing column can perform rail-type stepless motion along the swing column under the urging of the stepless driving device, so that the distance between the phase mover and a swing fulcrum of the swing column is changed, because the phase mover is mounted on the outer side of the phase mover, the distance is an effective swing output radius, the larger the distance is, the larger the swing distance which can be reached by the phase mover output shaft is, and the larger the rotating speed converted to the output shaft indirectly connected with the phase mover output shaft is; when the phase rotor approaches to the swing fulcrum of the swing column, even when the output shaft of the phase rotor is coaxial with the swing fulcrum, the output shaft of the phase rotor can only rotate to output the phase, and the output rotating speed of the output shaft is zero at the moment.

As a further optimization scheme of the invention, the stepless driving device comprises a bidirectional motor, a motor gear and a phase mover rack; the phase rotor rack is arranged on the outer side of the phase rotor and is parallel to the swinging column, the bidirectional motor is arranged on the outer side of the rotating connection point, a motor gear is sleeved on a driving shaft of the bidirectional motor, and under the action of the motor driving shaft, the motor gear can drive the phase rotor rack and the phase rotor to move back and forth along the swinging column, so that the distance from the output shaft of the phase rotor to the swinging fulcrum of the swinging column is changed, namely the swinging distance which can be reached by the output shaft of the phase rotor is changed.

The output rotating speed of the output shaft is obtained by controlling the bidirectional motor, and the working mode of the motor is stepless rotating motion, and the phase rotor is movably sleeved on the long and straight swinging column, so that the displacement of the phase rotor can be regulated and controlled according to the stepless rotation of the bidirectional motor, namely the output phase of the output shaft of the phase rotor is regulated and controlled in a stepless mode, and further the stepless speed change of the output shaft is realized.

It should be noted that the bidirectional motor is a brake type motor, a brake is arranged in the bidirectional motor, the brake type motor is suitable for various spindle transmissions and auxiliary transmissions of quick stop, accurate positioning, reciprocating operation and sliding prevention, and the problem that the output shaft of the phase mover slips due to overlarge load can be effectively prevented.

As a further optimization scheme of the invention, the bottom of the swing column is fixedly connected with a swing support, and outward convex cylinders are symmetrically arranged on two sides of the swing support and are respectively in rotating connection with the inner side wall of the gearbox; a phase control rod penetrates through one of the convex cylinders through a bearing, one end of the phase control rod extends to the outside of the swing bracket and is sleeved with an outer phase control gear, and the outer phase control gear is in meshed connection with the motor gear; the other end of the phase control rod extends to the inside of the swing support and is sleeved with an inner phase control gear, and the inner phase control gear is connected with the phase mover rack in a meshed mode.

The motor gear, the outer phase control gear, the phase control lever, the inner phase control gear and the phase rotor rack are sequentially connected together to form a phase control mechanism, the mechanism can be used for converting the rotary motion of the bidirectional motor into the reciprocating linear motion of the phase rotor, the rack and gear combination is used as a mechanical reversing structure which is widely applied, the transmission is stable, and the mechanism is particularly suitable for environments with heavy load, high precision, high rigidity, high speed and long stroke.

In the structural parameters of the transmission part, the inner phase control gear is designed to be a gear with a smaller modulus relative to the outer phase control gear, so that the tooth pitch of the inner phase control gear is as small as possible, and the inner phase control gear is meshed with the phase rotor rack more tightly, and the diameter of the inner phase control gear is smaller than that of the outer phase control gear, so that the positioning of the output shaft of the phase rotor is stabilized to a certain extent, and the output shaft of the phase rotor is not easy to loosen and slide due to overlarge load.

As a further optimization scheme of the present invention, two sides of the swing bracket are connected through a bottom plate, and a clearance groove is provided in a region of the bottom plate close to the phase mover rack, so as to avoid obstructing a traveling path of the phase mover rack.

As a further optimization scheme of the invention, a position of the swing column close to the swing shaft is provided with a limiting block so as to limit the highest displacement point of the phase mover.

As a further optimized solution of the present invention, the bottom plate of the rocking support is lower than the convex cylinder to ensure that the displacement range of the phase mover can cover the position of the convex cylinder, and when the output shaft of the phase mover is coaxial with the convex cylinder, that is, coaxial with the rocking fulcrum of the rocking support, the phase output is zero.

As a further optimized scheme of the invention, the working length of the phase mover rack is greater than the distance from the limiting block to the inner phase control gear.

As a further optimization scheme of the invention, circular grooves arranged along the same axis are arranged on two inner walls of the gearbox, and the two convex cylinders are inserted into the corresponding circular grooves through bearings so as to realize rotary connection.

As a further optimized scheme of the invention, the output shaft of the phase mover is movably connected with a driven shaft through a second connecting rod, the end part of the driven shaft is fixed on the side wall of a bilateral linear rack, the upper surface and the lower surface of the bilateral linear rack are respectively connected with a first gear shaft and a second gear shaft in a meshing manner, and the bilateral linear rack makes reciprocating linear motion under the traction of the output shaft of the phase mover, so that the first gear shaft and the second gear shaft are driven to rotate; the first gear shaft and the second gear shaft are respectively and coaxially connected with a third gear shaft and a fourth gear shaft through one-way bearings, the third gear shaft and the fourth gear shaft are both meshed with an output gear, and a hub of the output gear is inserted with the output shaft.

As a further optimized scheme of the present invention, the rotation directions of the first gear shaft and the second gear shaft are opposite to each other, and the work directions of the two one-way bearings are the same, so as to ensure that the output shaft can continuously rotate at a specified direction during the movement of the bilateral linear rack.

Compared with the prior art, the invention has the beneficial effects that:

firstly, the invention uses the principle of a crank connecting rod to take the motion of a swing rod as a transmission mode from an input shaft to an output shaft, a rotation-reciprocating swing-rotation motion mode is formed, and the modules are connected through the connecting rod, so that the whole structure is in flexible connection of a rigid body, the slip phenomenon of belt transmission is avoided, and strong torque can be provided.

In addition, in the operation of adjusting the transmission ratio, the structure changes the swing output radius of the swing rod by starting the stepless driving device instead of increasing fuel, and saves labor and fuel in the acceleration process while realizing a larger transmission ratio range.

Further, the invention uses a rack and pinion combination as a phase control mechanism, and the mechanism is used for smoothly converting the rotary motion of the bidirectional motor into the reciprocating linear motion of the phase mover, thereby smoothly and powerfully regulating and controlling the output phase of the output shaft of the phase mover.

In the transmission connection between the output shaft of the phase rotor and the output shaft, in order to adapt to the change of the swing radius of the output shaft of the phase rotor, the invention adopts a rack and gear combination for transmission, the stroke of a rack can be linearly adjusted along with the change of the swing distance of the output shaft of the phase rotor, and compared with a crankshaft connecting rod mechanism, the invention can skillfully solve the problem of the dead locking of a connecting rod;

finally, two working faces of the rack are respectively provided with two symmetrical one-way bearings and a gear shaft, so that no matter which direction the phase rotor output shaft swings to, the output shaft can obtain effective output rotating speed, and the transmission efficiency of stepless speed regulation is further improved.

Drawings

In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to the provided drawings without creative efforts.

FIG. 1 is a schematic representation of the internal connections of the transmission system of the present invention;

FIG. 2 is a schematic diagram of the system A of FIG. 1 (for converting a rotational input mode to a rocking mode);

FIG. 3 is a schematic diagram of the system B of FIG. 1 (for converting the wobble mode to the infinitely variable phase output driving mode);

FIG. 4 is an assembly view of the rocking post, rocking support and cam of the present invention;

FIG. 5 is a schematic structural view of a sway brace assembly of the present invention;

FIG. 6 is a schematic view of the rocking support member of the invention;

FIG. 7 is a schematic diagram of a phase mover assembly of the present invention;

FIG. 8 is a schematic diagram of the configuration of the system C of FIG. 1 (for converting a continuously variable phase output drive mode to a rotary output drive mode);

FIG. 9 is a schematic diagram of the motion of the bilateral linear rack of the present invention;

in the figure, a1 — input shaft; a2-flywheel; a3-eccentric shaft; b1-rocking support; b2-rocking column; b3-rocking axis; b4 — first boss; b5 — second cam; b6 — first bearing; b7 — second bearing; b8-phase mover; b9-phase mover output shaft; b10-phase mover rack; b11-inner phase manipulating gear; b12-phase lever; b13-outer phase steering gear; b14-joystick bearing; b15-motor gear; b16-bidirectional motor; c1-driven shaft; c2-bilateral linear rack; c3-guide shaft; c4 — first gear shaft; c5-second gear shaft; c6 — first one-way bearing; c7-second one-way bearing; c8-third gear shaft; c9-fourth gear shaft; c10 — output gear; c11-fulcrum bearing; c12-output shaft; c13 — first gear; c14 — second gear; c15-third gear; c16-fourth gear; c17-bearing housing; d1-a first link; d2-second link.

Detailed Description

The following further describes embodiments of the present invention with reference to the drawings. It should be noted that the description of the embodiments is provided to help understanding of the present invention, but the present invention is not limited thereto. In addition, the technical features involved in the embodiments of the present invention described below may be combined with each other as long as they do not conflict with each other.

First, fig. 1 shows a three-module system of the transmission system of the present invention and the connection relationship thereof, wherein the a system is used for converting the rotational input mode of the input shaft a1 into the rocking mode, and specifically comprises an input shaft a1, a flywheel a2 and an eccentric shaft A3;

the B system is used for converting the swing mode of the A system into a stepless regulation phase output driving mode, and specifically comprises a swing bracket B1, a swing column B2, a swing shaft B3, a first convex barrel B4, a second convex barrel B5, a first bearing B6, a second bearing B7, a phase rotor B8, a phase rotor output shaft B9, a phase rotor rack B10, an inner phase control gear B11, a phase control lever B12, an outer phase control gear B13, a control lever bearing B14, a motor gear B15 and a bidirectional motor B16;

the C system is used for converting a stepless phase regulation output driving mode of the B system into a rotary output driving mode of an output shaft C12, and specifically comprises a driven shaft C1, a bilateral linear rack C2, a guide pillar shaft C3, a first gear shaft C4, a second gear shaft C5, a first one-way bearing C6, a second one-way bearing C7, a third gear shaft C8, a fourth gear shaft C9, an output gear C10, a support bearing C11 and an output shaft C12;

the system A and the system B are connected by a first connecting rod D1, and the system B and the system C are connected by a second connecting rod D2.

The embodiment provides a novel automobile stepless speed regulation transmission system, which comprises an input shaft A1, a gearbox (not shown in the figure) and an output shaft C12, wherein the input shaft A1 and the output shaft C12 are respectively arranged on two opposite side walls of the gearbox in a penetrating manner through bearings. As shown in fig. 2, the input shaft a1 extends into the transmission case and is fixedly connected with a flywheel a2 at the shaft end, the end face of the flywheel a2 is provided with an eccentric shaft A3 in the same direction in the region outside the wheel core, the eccentric shaft A3 is movably connected with a swing shaft B3 through a first connecting rod D1, the end part of the swing shaft B3 is fixedly connected with a swing column B2 perpendicular to the end part, and a crank-link mechanism is basically formed. As shown in fig. 3-6, the bottom of the swing post B2 is fixedly connected to a swing bracket B1, a first outward-facing cam B4 and a second outward-facing cam B5 are symmetrically disposed on both sides of the swing bracket B1, the two cams are respectively connected to the inner side wall of the transmission case in a rotating manner, the eccentric shaft A3 can drive the eccentric shaft A3 and the swing post B2 to swing back and forth around the axes of the two cams B4 and B5 through the first connecting rod D1 during the rotation around the input shaft a1, that is, the first cam B4 and the second cam B5 can be regarded as a swing fulcrum of the swing post B2.

It should be added that circular grooves (not shown in the figures) arranged along the same axis are formed in two inner side walls of the transmission case, a first bearing B6 is sleeved on the outer circumference of the first convex cylinder B4, a second bearing B7 is sleeved on the outer circumference of the second convex cylinder B5, and the two convex cylinders are respectively inserted into the corresponding circular grooves through a first bearing B6 and a second bearing B7 to realize the rotational connection with the side walls of the transmission case.

The swing column B2 is movably sleeved with a phase mover B8, a phase mover output shaft B9 parallel to the swing shaft B3 is arranged on the outer side of the phase mover B8, the other side of the phase mover B8 is indirectly connected with a bidirectional motor B16, and under the driving action of the bidirectional motor B16, the phase mover B8 can move back and forth along the swing column B2, so that the output phase of the phase mover output shaft B9 is changed.

Specifically, a phase manipulating mechanism is arranged between the bidirectional motor B16 and the phase mover B8, and the phase manipulating mechanism comprises a motor gear B15, an outer phase manipulating gear B13, a phase manipulating rod B12, an inner phase manipulating gear B11 and a phase mover rack B10. As shown in fig. 7, the phase mover rack B10 is disposed outside the phase mover B8 and is parallel to the swing column B2, the bidirectional motor B16 is disposed outside the swing bracket B1, the motor gear B15 is sleeved on a drive shaft of the bidirectional motor B16, the motor gear B15 is engaged with the outer phase manipulating gear B13, the phase manipulating lever B12 is inserted into a hub of the outer phase manipulating gear B13, the phase manipulating lever B12 is movably inserted into an inner ring of the first boss B4 through a lever bearing B14, and extends into the swing bracket B1 and is sleeved with an inner phase manipulating gear B11, and the outer phase manipulating gear B13, the phase manipulating lever B12 and the inner phase manipulating gear B11 form a whole in appearance; the inner phase manipulation gear B11 is in meshing connection with the phase mover rack B10. As can be seen from the above, the rotational motion of the bidirectional motor B16 can be smoothly and powerfully converted into the reciprocating linear motion of the phase mover B8 by the phase manipulating mechanism.

In order to limit the phase range of the phase mover output shaft B9, in this embodiment, the phase mover B8 is disposed on the swing post B2 in a ring shape, and an oblong limiting groove (as shown in fig. 4) is disposed on the top surface facing the swing shaft B3, when the phase mover B8 moves to a certain position in a direction away from the swing fulcrum of the swing bracket B1, the bottom of the limiting groove of the phase mover B8 contacts the swing shaft B3, so as to limit the highest displacement point of the phase mover B8, and at this time, the swing shaft B3 is coaxial with the phase mover output shaft B9, so as to achieve the maximum transmission ratio.

Of course, in some other embodiments, the swing post B2 may also be provided with a limiting block for limiting the maximum displacement limit of the phase mover B8, which is not specifically limited herein.

As shown in fig. 6, in this embodiment, two sidewalls of the swing bracket B1, on which the first convex cylinder B4 and the second convex cylinder B5 are mounted, are connected by a bottom plate, and the bottom plate is lower than the two convex cylinders, so as to ensure that the displacement range of the phase mover B8 can cover the position of the convex cylinder B4. When the phase mover output shaft B9 is driven by the linear reciprocating motion of the phase mover rack B10 to be coaxial with the axes of the first and second convex cylinders B4 and B5, that is, the swing fulcrum of the swing bracket B1, it can only rotate and no longer swing, and at this time, the phase output is zero.

Additionally, the area of the base plate adjacent to the phase mover rack B10 should be provided with a clearance groove to avoid interfering with the travel path of the phase mover rack B10.

The working principle of the phase mover output shaft B9 is briefly described here:

since the working length of the first link D1 is fixed, the swing distance converted from the eccentric shaft A3 by the first link D1 is fixed, that is, the swing angle of the swing column B2 is fixed, and the first boss B4 and the second boss B5 close to the bottom of the swing column B2 can only rotate around the circular groove and cannot swing, so that the swing column B2 forms a V-shaped swing mode around the axes (which can be understood as a swing fulcrum) of the first boss B4 and the second boss B5. The swing column B2 is movably connected with a phase mover output shaft B9 through a phase mover B8, and the distance from the phase mover output shaft B9 to a swing fulcrum is the effective swing output radius of the swing column B2. In this configuration, by adjusting the position of the phaser output shaft B9, the pitch of the phaser output shaft B9 can be changed, which in turn changes the distance traveled by the two-sided linear rack C2, thereby affecting the output speed of the output shaft C12.

For example, when the phase mover output shaft B9 is coaxial with the rocking shaft B3, the maximum achievable rocking distance is achieved, and the maximum output rotational speed transmitted to the output shaft C12 is achieved; when the output shaft B9 of the phase mover and the swing fulcrum of the swing bracket B1 are coaxial, the output shaft B9 can only rotate to output no phase, and the output rotating speed of the output shaft C12 is zero.

The output shaft C12 is also indirectly connected to the phaser output shaft B9 as a complete transmission system to convert the modulated reciprocating cycloidal motion into a rotary motion at a corresponding speed.

Specifically, the phase mover output shaft B9 is movably connected to a driven shaft C1 through a second connecting rod D2, as shown in fig. 8, an end of the driven shaft C1 is fixed to a side wall of a double-sided linear rack C2, and the double-sided linear rack C2 is sleeved on the guide pillar shaft C3 along the traveling direction; as shown in fig. 9, the phaser output shaft B9, the second link D2, the driven shaft C1 and the guide post shaft C3 form a crank slider mechanism, and the bilateral linear rack C2 is capable of reciprocating linearly along the guide post shaft C3 under the traction of the cycloidal motion of the phaser output shaft B9.

The crank-slider mechanism is introduced into the system C, the slider is skillfully deformed into the straight-edge rack, the swinging motion is converted back to the rotating motion in one step without reversely adopting a crankshaft-connecting rod mechanism similar to the system A, the position of the phase mover output shaft B9 serving as a crank in the invention is considered to be variable, two connecting rods connected in sequence are required if a conventional crankshaft-connecting rod mechanism is adopted, and the structure of the crankshaft-connecting rod-driven piece is easy to cause the two connecting rods to be blocked due to overlarge longitudinal stress under the condition of crankshaft displacement; the crank slider mechanism and the straight-edge rack combination of the system C can solve the problem skillfully, even if the phase mover output shaft B9 displaces in the swinging process, the stroke of the bilateral linear rack C2 is only correspondingly increased or decreased, the bilateral linear rack C2 slides stably all the time and is meshed and connected with the first gear shaft C4 and the first gear shaft C5 all the time, and the stability of rotating speed output is guaranteed.

The upper surface and the lower surface of the bilateral linear rack C2 are respectively connected with a first gear C13 and a second gear C14 in a meshing manner, a first gear shaft C4 penetrates through the hub of the first gear C13, and a second gear shaft C5 penetrates through the hub of the second gear C14, so that the bilateral linear rack C2 can make the linear reciprocating motion through the first gear C13 and the second gear C14 to drive the first gear shaft C4 and the second gear shaft C5 to rotate towards opposite directions at the same time.

The first gear shaft C4 is coaxially connected with a third gear shaft C8 through a first one-way bearing C6, specifically, the end of the first gear shaft C4 is sleeved with a first one-way bearing C6, the end of the third gear shaft C8 is fixedly sleeved with a bearing sleeve C17, namely, the bearing sleeve C8 of the third gear shaft C17 is of an integrated structure, and the two shafts form a long straight transmission rod through the assembly of the bearing and the bearing sleeve; similarly, the second gear shaft C5 is also coaxially connected with a fourth gear shaft C9 through a second one-way bearing C7 and another bearing sleeve C17; the third gear C15 on the third gear shaft C8 and the fourth gear C16 on the fourth gear shaft C9 are meshed with the output gear C10, and the hub of the output gear C10 is inserted with the output shaft C12.

As can be seen from the above, in the process of linear sliding, the bilateral linear rack C2 can drive the first gear shaft C4 and the second gear shaft C5, which are symmetrically arranged up and down, to rotate in opposite directions at a constant speed, and when the rotation direction of the shaft body (the first gear shaft C4 or the second gear shaft C5) is the same as the work direction of the corresponding one-way bearing (the first one-way bearing C6 or the second one-way bearing C7), the rotation of the shaft body can be transmitted to the rear gear shaft (the third gear shaft C8 or the fourth gear shaft C9), and then transmitted to the output shaft C12.

It is supplementary to explain, the unidirectional bearing of this embodiment has adopted the unidirectional bearing of ratchet type, have forward rotation to do work and reverse to do empty characteristic, when the unidirectional bearing inner ring of ratchet type rotates around the appointed direction, inner ring and outer lane are blocked, the ratchet of the inner ring can drive the outer lane to rotate synchronously, thus transmit the driving force to the gear shaft behind; when the inner ring rotates around other directions, namely rotates reversely, the inner ring and the outer ring both rotate in a reactive mode, the ratchet wheel of the inner ring cannot drive the outer ring to rotate, and therefore driving force cannot be transmitted out; the one-way bearing can only transmit the rotation speed in one direction. In this embodiment, the first one-way bearing C6 and the second one-way bearing C7 are set to have the same normal rotation direction.

In summary, because the rotation directions of the first gear shaft C4 and the second gear shaft C5 are always opposite, and the acting directions of the first one-way bearing C6 and the second one-way bearing C7 are the same, and in addition, the one-way bearing has the characteristic that positive rotation, acting and negative rotation are empty, such a structure enables the output shaft C12 to obtain an output rotation speed no matter which direction the phase mover output shaft B9 swings to, and the efficiency of stepless speed change is improved to a certain extent.

It should be understood that, as shown in fig. 8, in order to ensure the normal operation of each transmission shaft of the C-system, the first gear shaft C4, the second gear shaft C5, the third gear shaft C8, the fourth gear shaft C9 and the output shaft C12 in this embodiment are all sleeved with a support bearing C11 on the circumference to function as an auxiliary support.

It should be further noted that, in order to ensure the stability of the linear motion of the phase mover B8, that is, the phase mover output shaft B9, a gear is sleeved on the input end of the input shaft a1 of the present invention, and the input end needs to be in gear engagement with the engine output shaft, and the number of gear teeth of the input shaft a1 should be greater than that of the engine output shaft, so that the connection structure can reduce the input rotation speed of the input shaft a1 to a certain extent, thereby reducing the vibration of the phase mover output shaft B9 relative to the rocking column B2, and as a whole, the function of preventing the oscillation of the transmission is achieved.

The transmission system mainly adopts a connection mode of the gear and the connecting rod, the output power of the transmission system is obviously improved compared with the traditional metal belt type stepless transmission, and the transmission system can be suitable for small and even heavy automobiles; meanwhile, the transmission system is simple in structure, the size of the transmission box is reduced, reliable speed change is achieved, and meanwhile, the production cost can be saved.

In general, the invention has reasonable design, effectively overcomes the defects of slow speed regulation and insufficient torque of the existing continuously variable transmission, and has important popularization and application values in the technical field of automobile speed change systems.

The embodiments of the present invention have been described in detail with reference to the accompanying drawings, but the present invention is not limited to the described embodiments. It will be apparent to those skilled in the art that various changes, modifications, substitutions and alterations can be made in these embodiments without departing from the principles and spirit of the invention, and the scope of protection is still within the scope of the invention.

Claims

1. The utility model provides a novel car infinitely variable speed transmission system, includes input shaft, gearbox and output shaft, its characterized in that: the input shaft extends into the gearbox, a flywheel is sleeved at the shaft end, eccentric shafts in the same direction are arranged on the end face of the flywheel in the region outside the wheel core, the eccentric shafts are movably connected with a swing shaft through a first connecting rod, the end part of the swing shaft is fixedly connected with a swing column perpendicular to the swing shaft, the bottom of the swing column is rotatably connected with the side wall of the gearbox, and the eccentric shafts can drive the swing shaft and the swing column to swing back and forth around the rotating connection point through the first connecting rod in the process of rotating around the input shaft;

2. The novel automotive infinitely variable speed transmission system of claim 1, characterized in that: the stepless driving device comprises a bidirectional motor, a motor gear and a phase mover rack; the phase rotor rack is arranged on the outer side of the phase rotor and is parallel to the swinging column, the bidirectional motor is arranged on the outer side of the rotating connection point, a motor gear is sleeved on a driving shaft of the bidirectional motor, and the motor gear can drive the phase rotor rack and the phase rotor to move back and forth along the swinging column under the action of the driving shaft.

3. The novel automotive continuously variable transmission system according to claim 2, characterized in that: the bottom of the swing column is fixedly connected with a swing support, and two sides of the swing support are symmetrically provided with outward convex cylinders which are respectively and rotatably connected with the inner side wall of the gearbox; a phase control rod penetrates through one of the convex cylinders through a bearing, one end of the phase control rod extends to the outside of the swing bracket and is sleeved with an outer phase control gear, and the outer phase control gear is in meshed connection with the motor gear; the other end of the phase control rod extends to the inside of the swing support and is sleeved with an inner phase control gear, and the inner phase control gear is connected with the phase mover rack in a meshed mode.

4. The novel automotive continuously variable transmission system according to claim 3, characterized in that: the two sides of the swing support are connected through a bottom plate, and a position avoiding groove is formed in the area, close to the phase rotor rack, of the bottom plate.

5. The novel automotive infinitely variable speed transmission system of claim 1, characterized in that: and a position of the swing column close to the swing shaft is provided with a limiting block so as to limit the highest displacement point of the phase mover.

6. The novel automotive continuously variable transmission system according to claim 4, characterized in that: the bottom plate of the swing support is lower than the convex barrel so as to ensure that the displacement range of the phase mover can cover the position of the convex barrel.

7. The novel automotive continuously variable transmission system according to claim 5, characterized in that: the working length of the phase rotor rack is larger than the distance from the limiting block to the internal phase control gear.

8. The novel automotive infinitely variable speed transmission system of claim 1, characterized in that: circular grooves arranged along the same axis are formed in two opposite inner walls of the gearbox, and the two convex cylinders are inserted into the corresponding circular grooves through bearings so as to realize rotary connection.

9. The novel automotive infinitely variable speed transmission system of claim 1, characterized in that: the output shaft of the phase mover is movably connected with a driven shaft through a second connecting rod, the end part of the driven shaft is fixed on the side wall of a double-sided linear rack, the upper surface and the lower surface of the double-sided linear rack are respectively connected with a first gear shaft and a second gear shaft in a meshing manner, and the double-sided linear rack makes reciprocating linear motion under the traction of the output shaft of the phase mover so as to drive the first gear shaft and the second gear shaft to rotate; the first gear shaft and the second gear shaft are respectively coaxially connected with a third gear shaft and a fourth gear shaft through one-way bearings, the third gear shaft and the fourth gear shaft are both meshed with an output gear, and a hub of the output gear is inserted with the output shaft.

10. The new automotive infinitely variable speed transmission system of claim 9, characterized in that: the rotation directions of the first gear shaft and the second gear shaft are opposite to each other, and the acting directions of the two one-way bearings are the same, so that the output shaft can continuously designate the rotation speed in the direction in the movement process of the bilateral linear rack.