CN102720818B - Mechanical, intelligent, adaptive, two-speed and multi-cam automatic transmission - Google Patents

Abstract

The invention discloses a mechanical intelligent self-adaptive two-speed multi-cam automatic transmission, which comprises a transmission shaft, a slow gear transmission mechanism, an axially outer taper sleeve of a ring body and an inner tapered sleeve in the axial direction of the ring body, and the axial direction of the ring body is The outer tapered sleeve is overlaid on the transmission shaft and is driven by a spiral cam pair. The slow gear transmission mechanism adopts the transmission structure of multi-face cams. The structure can ensure the sensitivity during the shifting process, eliminate the frustration and jamming feeling of shifting, improve driving comfort, further save energy and reduce consumption, and greatly improve the power, economy, driving safety and comfort of the vehicle .

Description

Mechanical intelligent adaptive two-speed multi-cam automatic transmission

technical field

The invention relates to a motor vehicle transmission, in particular to a mechanically intelligent self-adaptive two-speed multi-cam automatic transmission.

Background technique

In the prior art, automobiles, motorcycles, and electric bicycles basically directly control the throttle or current control speed through a speed control handle or an accelerator pedal, or use a manual mechanical automatic transmission mechanism to realize speed change. The operation of the handle or accelerator pedal depends entirely on the driver's operation, which often causes a mismatch between the operation and the driving conditions, resulting in unstable operation of the motor or engine, and stalling.

When the motor vehicle is operated by the rider without knowing the driving resistance, the speed change device is operated and controlled only based on experience, which inevitably has the following problems: 1. When starting, going uphill and with a large load, due to the increase in driving resistance, the motor or The engine speed drops to work in the low efficiency area. 2. Since there is no mechanical transmission to adjust the torque and speed, it can only be popularized and used in plain areas, and cannot be used in mountainous, hilly and heavy-load conditions, which reduces the scope of use; 3. The installation space at the drive wheel is small, and the engine or motor is installed It is difficult to accommodate automatic transmissions and other new technologies in the future; 4. It does not have the function of self-adaptation, and cannot automatically detect, correct and eliminate the driver's operation errors; Resistance is hard to match. 6. The continuation distance is short, the climbing ability is poor, and the adaptability range is small.

In order to solve the above problems, the inventors of the present application have invented a series of cam adaptive automatic transmission devices, which use driving resistance to drive the cam to achieve the purpose of automatic gear shifting and adaptive matching of vehicle speed output torque according to driving resistance, which has a good application effect ; Although the aforementioned cam adaptive automatic transmission has the above-mentioned advantages, the stability and high efficiency are greatly improved compared with the prior art, but the structure of some parts is relatively complicated, and the transmission volume is relatively large. At the same time, due to the use of multiple cams (the same Circumferential) structure, the stability is still not ideal; and there will be jamming in the process of clutching through the cam, which will affect the smoothness of the automatic shifting process; although the service life is improved compared with the existing technology, according to the structural analysis, There is still room for improvement in service life.

Therefore, there is a need for an improvement to the above-mentioned cam adaptive automatic transmission device, which can not only adapt to the change of driving resistance without cutting off the driving force, but also automatically shift gears and change gears, and solve the problem that small torque-rotational speed changes cannot meet road use under complex conditions. It has good stability, further improves work efficiency, has better energy-saving and consumption-reducing effects, and reduces volume; at the same time, the shifting process is smooth and free of jamming, responsive, saves driving energy, reduces energy consumption, and further improves Service life, suitable for motor vehicle use.

Contents of the invention

In view of this, the object of the present invention is to provide a mechanical intelligent self-adaptive two-speed multi-cam automatic transmission, which can not only automatically perform gear shifting without cutting off the driving force according to the change of driving resistance, but also solve the problem of torque-rotational speed variation. Small size cannot meet the problem of road use under complex conditions, good stability, further improving work efficiency, better energy saving effect, and reduced volume; at the same time, the shifting process is smooth and free of jamming, responsive, saving driving energy , reduce energy consumption, and further increase service life, suitable for use in motor vehicles.

The mechanical intelligent self-adaptive two-speed multi-cam automatic transmission of the present invention includes a transmission shaft for outputting power, and also includes a slow gear transmission mechanism and a mechanical intelligent self-adaptive transmission assembly arranged on the transmission shaft;

The mechanical intelligent self-adaptive speed change assembly includes the axial outer taper sleeve of the torus, the axial inner taper sleeve of the torus and the variable speed elastic element;

The axial inner tapered sleeve of the annular body is used for power input, the axial inner tapered sleeve of the annular body is provided with an axial inner tapered surface and is overlaid on the axial outer tapered sleeve of the annular body, and the axial outer tapered sleeve of the annular body is set There is an axially outer tapered surface matched with the axially inner tapered surface of the axially inner tapered sleeve of the annular body; the axially outer tapered sleeve of the annular body is overlaid on the transmission shaft and matched with it through the main transmission cam pair;

The speed-changing elastic element exerts a pretightening force on the axial outer tapered sleeve of the annular body so that the outer tapered surface and the inner tapered surface of the axial inner tapered sleeve of the annular body fit the transmission; when the power output of the transmission shaft, the main transmission cam The auxiliary pair exerts an axial component force opposite to the preload of the variable speed elastic element on the axial outer tapered sleeve of the annular body;

The slow gear transmission mechanism includes an intermediate reduction transmission mechanism with an overrunning clutch, and the axial inner taper sleeve of the annular body is in transmission cooperation with the power input end of the intermediate reduction transmission mechanism; The axial ends of the middle cam sleeve are respectively equipped with corresponding cam engagement pairs, the axial outer taper sleeve of the ring body and the intermediate reduction transmission mechanism, and the slow gear power is transmitted from the power output end of the intermediate reduction transmission mechanism to the circular ring. The ring body is axially externally tapered.

Further, the axially inner tapered surface of the axially inner tapered sleeve of the toroidal body or\and the axially outer tapered surface of the axially outer tapered sleeve of the toroidal body are provided with lubricating oil grooves, and the lubricating oil grooves are provided with holes for oil inlet and outlet port;

Further, the axially outer tapered surface of the axial outer taper sleeve of the annular body is provided with a lubricating oil groove, and the lubricating oil groove is left-handed and right-handed spirally coiled on the axial outer tapered surface alternately, and its port is controlled by the lubricating oil groove left-handed and right-handed. The right-handed helix is naturally formed at both ends of the axial outer cone;

Further, the inner ring of the overrunning clutch is rotatably fitted on the transmission shaft, and the intermediate speed reduction transmission mechanism also includes a reduction gear set for transmitting the power from the annular body axially to the inner tapered sleeve to the overrunning clutch. The inner ring of the overrunning clutch is in the The power output rotation direction of the transmission shaft and the outer ring overrun, the inner tapered sleeve in the axial direction of the annular body is driven and matched with the outer ring of the overrunning clutch through the reduction gear set, and the inner ring of the overrunning clutch and the axial direction of the annular body Between the outer tapered sleeves, the slow gear power is transmitted from the inner ring of the overrunning clutch to the outer tapered sleeve in the axial direction of the annular body through the intermediate cam sleeve; the cam engagement pairs at both ends of the intermediate cam sleeve are end cam engagement pairs, and the The profile angles are all less than or equal to 45° and the profile angles of the end cams at both ends of the middle cam sleeve are different;

Further, the overrunning clutch is a shrapnel type overrunning clutch, including a roller and a cage, and an engagement groove for engaging or separating from the roller is formed between the outer ring and the inner ring of the overrunning clutch; the cage includes a support plate, The support column and the reed, the support column corresponds to the roller one by one, the support piece is fixedly arranged on the support column in the circumferential direction and forms a slot between the support piece and the outer surface of the support column, and the reed is provided There is a fitting part embedded in the slot, and the reed extends out of the slot to apply a pre-tightening force to the roller along the engaging direction of the engaging groove. deformation allowance;

Further, the fitting part is provided with a pressure-receiving part, and the support sheet is provided with a pressing part that applies pressure to the pressure-receiving part to insert the fitting part into the slot and restricts the fitting part from coming out of the slot;

Further, the pressure-receiving part is integrally formed on the fitting part and is an elastic sheet structure extending outward, the pressure-receiving part is bent toward the pressing part to form a pressure-bearing section, and the pressing part is bent toward the pressure-bearing part to form a superimposed on the bearing The compression section that presses the outer surface of the section and applies pressure to the pressure section;

Further, the reduction gear set includes a slow gear intermediate shaft, a first slow gear and a second slow gear arranged on the slow gear intermediate shaft and drivingly matched with it, and the inner taper sleeve of the annular body axially passes through the slow gear drive It is engaged with the first slow gear for transmission, and the second slow gear is engaged with the outer ring of the overrunning clutch for transmission;

Further, the variable-speed elastic element is a variable-speed disc spring that is sheathed on the transmission shaft. The variable-speed disc spring and the overrunning clutch are arranged on both axial sides of the axially outer taper sleeve of the annular body, and the variable-speed disc spring is sequentially fitted with the outer sleeve by sliding. The speed change sleeve and the speed change plane bearing on the transmission shaft withstand one axial end of the axial outer tapered sleeve of the annular body, and the other axial end of the axial outer tapered sleeve of the annular body and the middle cam sleeve pass through the corresponding end cam Auxiliary transmission cooperation; the ring body is equipped with an inner helical cam on the inner circle of the outer tapered sleeve, and the transmission shaft is equipped with an outer helical cam that matches the inner helical cam to form a helical cam pair;

Further, the variable speed butterfly spring is arranged on the right side of the axial outer tapered sleeve of the annular body, and the overrunning clutch is located on the left side of the axial outer tapered sleeve of the annular body; the inner helical cam of the axial outer tapered sleeve of the annular body and the The expansion direction of the external helical cam of the transmission shaft is the same as the power output rotation direction of the transmission shaft from left to right; the two ends of the middle cam sleeve, the inner ring of the overrunning clutch and the axial outer taper sleeve of the torus are respectively provided with end cams and passed through The end face cams mesh with each other to form an end face cam meshing pair; both ends of the middle cam sleeve, the inner ring of the overrunning clutch and the torus axially extend from the end face cam meshing line of the outer tapered sleeve to the opposite direction of the power output rotation of the transmission shaft.

The beneficial effects of the present invention are: the mechanical intelligent self-adaptive two-speed multi-cam automatic transmission of the present invention has all the advantages of the existing cam self-adaptive automatic transmission, such as being able to detect the driving torque-speed and the driving resistance-vehicle speed according to the driving resistance Signal, so that the output power of the motor or engine and the driving condition of the vehicle are always in the best matching state, realizing the balance control of the driving torque and the comprehensive driving resistance of the vehicle, and automatically shifting gears according to the change of driving resistance without cutting off the driving force ;It can be used in mountainous areas, hills and heavy load conditions, so that the motor or engine load changes smoothly, the motor vehicle runs smoothly, and improves safety;

At the same time, the present invention adopts the slow-shift transmission structure of multi-face cams, which can ensure the sensitivity during the shifting process, eliminate the frustration and jamming feeling of shifting, improve driving comfort, further save energy and reduce consumption, and greatly improve the efficiency of the vehicle. Power, economy, driving safety and comfort.

Description of drawings

The present invention will be further described below in conjunction with the accompanying drawings and embodiments.

Fig. 1 is the axial sectional structure schematic diagram of the present invention;

Fig. 2 is a schematic diagram of the structure of the axial outer taper sleeve of the torus;

Fig. 3 is a structural schematic diagram of the inner ring of the overrunning clutch;

Fig. 4 Schematic diagram of the structure of the oil passage on the tapered surface of the axial outer tapered sleeve of the annular body;

Fig. 5 is a structural schematic diagram of the middle cam sleeve;

Fig. 6 is a schematic diagram of cam expansion at both ends of the middle cam sleeve;

Fig. 7 is a structural schematic diagram of an overrunning clutch;

Fig. 8 is a schematic diagram of the cooperation of the support column, the support piece and the reed;

Fig. 9 is a schematic diagram of the reed structure;

Fig. 10 is a structural schematic diagram of an axial partial sectional view of an overrunning clutch.

Detailed ways

Fig. 1 is a schematic diagram of the axial section structure of the present invention, Fig. 2 is a schematic diagram of the structure of the axial outer tapered sleeve of the annular body, Fig. 3 is a schematic structural diagram of the inner ring of the overrunning clutch, Fig. 4 is on the tapered surface of the axial outer tapered sleeve of the annular body Schematic diagram of the structure of the oil passage; Figure 5 is a schematic diagram of the structure of the middle cam sleeve; Figure 6 is a schematic diagram of the expansion of the cams at both ends of the middle cam sleeve; Figure 7 is a schematic diagram of the structure of the overrunning clutch; It is a schematic diagram of the reed structure, and Fig. 10 is a schematic diagram of an axial partial cross-sectional structure of an overrunning clutch, as shown in the figure: the mechanical intelligent self-adaptive two-speed multi-cam automatic transmission of the present invention includes a transmission shaft 1 for outputting power, and also includes The slow gear transmission mechanism and the mechanical intelligent self-adaptive transmission assembly arranged on the transmission shaft; as shown in the figure, the two ends of the transmission shaft 1 are respectively equipped with radial rolling bearings 4 and radial rolling bearings 13, which are used to rotate and support the installation of the transmission The box body; the drive shaft 1 outputs the power and cooperates with the driven parts (such as wheels or machine tool spindles, etc.), as shown in the figure, the drive shaft 1 is equipped with a middle piece 3 for power output, and the middle piece 3 Cooperate with drive shaft 1 through spline transmission;

The mechanical intelligent self-adaptive speed change assembly includes the axially outer tapered sleeve 14 of the torus, the axially inner tapered sleeve 17 of the toroidal body and the variable speed elastic element 25;

The axial inner tapered sleeve 17 of the annular body is used for inputting power, such as driving and cooperating with power output components of power devices such as motors. As shown in the figure, the outer edge of the axially inner tapered sleeve 17 of the annular body is provided with The flange of the ring body can be equipped with gears, sprockets, etc.; the axial inner tapered sleeve 17 of the annular body is provided with an axial inner tapered surface and is overlaid on the axially outer tapered sleeve 14 of the annular body, and the axial outer tapered sleeve 14 of the annular body There is an axial outer tapered surface matched with the axial inner tapered surface of the axial inner tapered sleeve of the annular body, and the matching transmission is carried out through the tapered sleeve structure. At least one of the inner tapered surface and the outer tapered surface must have a certain roughness. Those skilled in the art can know according to this record, and will not go into details here; the axial outer tapered sleeve 14 of the annular body is sleeved on the transmission shaft 1 and the inner circle is provided with an internal helical cam 14a, and the transmission shaft 1 is provided with a The outer helical cam 1a matched with the inner helical cam together forms a helical cam pair; the helical cam pair is a thread structure that cooperates with each other. and two component forces in the circumferential direction, wherein the component force in the circumferential direction drives the transmission shaft 1 to rotate and output power, the axial component force is offset by the installation structure of the transmission shaft 1, and its reaction force acts on the axial outer tapered sleeve 14 of the ring body and Applied to the variable speed elastic element 25; of course, the spiral cam pair is the preferred structure of this embodiment, and other existing cam pairs can also be used to drive, such as end face cams, etc., but the spiral cam pair can make the structure more compact and make , Installation and maintenance are more convenient, and the spiral structure has stable transmission, uniform force, unparalleled stability and smoothness, further improves work efficiency, has better energy saving and consumption reduction effects, and greatly controls vehicle emissions. It is more suitable for light vehicles such as light two-wheeled vehicles;

The speed-changing elastic element 25 applies a pretightening force to the axial outer tapered sleeve 14 of the annular body so that the outer tapered surface and the inner tapered surface of the axial inner tapered sleeve 17 of the annular body are attached to the transmission; when the power output of the transmission shaft 1 , the helical cam pair exerts an axial component force opposite to the pretightening force of the variable speed elastic element 25 on the axial outer tapered sleeve 14 of the toroidal body; The direction is related. According to the above-mentioned records, those skilled in the art can know the axial component force in which direction the helical cam can be applied under the premise of knowing the power output direction of the transmission shaft, and will not repeat them here;

The slow gear transmission mechanism includes an intermediate reduction transmission mechanism with an overrunning clutch, and the axial inner taper sleeve 17 of the annular body is in transmission cooperation with the power input end of the intermediate reduction transmission mechanism; Sleeve 6, the axial ends of the middle cam sleeve 6 are respectively equipped with corresponding cam engagement pairs and the axial outer tapered sleeve 14 of the ring body and the intermediate reduction transmission mechanism, and the slow gear power is output from the intermediate reduction transmission mechanism. The end is transmitted to the axial outer tapered sleeve 14 of the annular body; the cam engagement pair can be an end face cam engagement pair or a spiral cam engagement pair, both of which can realize the purpose of the invention; the overrunning clutch of the intermediate reduction transmission mechanism can be arranged on the transmission of the mechanism Any position of the chain can achieve the purpose. The intermediate reduction transmission mechanism can be a first-stage gear reduction transmission or other reduction transmission structure. The intermediate reduction transmission mechanism can ensure that the axial inner tapered sleeve 17 of the annular body is transmitted to the outer ring of the overrunning clutch The rotational speed of 15 is lower than the rotational speed of the axial inner tapered sleeve 17 of the annular body; at the same time, the intermediate cam sleeve 6 also applies an axial force to the axial outer tapered sleeve 14 of the annular body while performing slow gear transmission to make the variable speed elastic element 25 Compression keeps the separation of the axial outer tapered sleeve 14 of the annular body and the axial inner tapered sleeve 17 of the annular body, so as to ensure that the slow gear transmission is not interfered.

In this embodiment, the axially inner tapered surface of the axial inner tapered sleeve 17 of the annular body or the axially outer tapered surface of the axially outer tapered sleeve 14 of the annular body is provided with a lubricating oil groove, and the lubricating oil groove is provided for Oil and oil outlet ports; the lubricating oil tank does not need additional oil supply, and can be lubricated directly by using the lubricating oil in the transmission case; the port is generally set on the axial inner tapered surface of the axial inner tapered sleeve of the annular body or\and The axial end portion of the axially outer tapered surface of the annular body axially outer taper sleeve is beneficial to form circulating lubrication.

In this embodiment, a lubricating oil groove 9 is provided on the axially outer tapered surface of the axially outer taper sleeve 14 of the annular body. The ports are naturally formed by lubricating oil grooves 9 left-handed and right-handed helical coils at both ends of the axial outer tapered surface; The ports are naturally truncated at both ends of the axial outer tapered surface. Due to the formation of a spiral coil structure and the ports are located at both ends of the axial direction, when the axial outer tapered sleeve 14 of the annular body rotates at high speed, one port uses centrifugal force in the lubricating oil groove. Vacuum is generated in 9, and the other port uses rotation to meet the lubricating oil and introduces the lubricating oil into the lubricating oil groove 9 to flow out from the port through the vacuum, forming a circulation of lubricating oil, thereby forming a flushing effect, which is beneficial to take away impurities and heat; that is, the The circulation not only keeps the space between the axial inner tapered sleeve 17 of the annular body and the axial outer tapered sleeve 14 of the annular body clean, but also facilitates the two to disengage quickly and maintain good relative movement when they are separated during slow gear transmission, reducing friction. The generation of heat is conducive to maintaining the good operation of the whole mechanism.

In this embodiment, the inner ring 31 of the overrunning clutch is rotated and fitted over the transmission shaft 1, as shown in the figure, the surface where the transmission shaft 1 and the inner ring 31 cooperate is provided with a lubricating oil groove 7 to ensure the flexibility of rotation; the intermediate reduction transmission mechanism It also includes a reduction gear set for transmitting power from the annular body axially to the inner tapered sleeve 17 to the overrunning clutch, the inner ring 31 of the overrunning clutch overruns between the power output rotation direction of the transmission shaft 1 and the outer ring 15, To ensure the high gear, the slow gear transmission mechanism is overrun; the axial inner taper sleeve 17 of the annular body is in transmission cooperation with the outer ring 15 of the overrunning clutch through the reduction gear set, and the inner ring 31 of the overrunning clutch and the ring The slow gear power is transmitted from the inner ring 31 of the overrunning clutch to the outer tapered sleeve 14 in the axial direction of the body through the intermediate cam sleeve 6 between the axial outer tapered sleeves 14; pair, and the profile cam angles of the end face cams of the cam engagement pair at the two ends of the middle cam sleeve 6 are all less than or equal to 45° and the shape line angles of the end cams at both ends of the middle cam sleeve 6 are different in size, as shown in the figure, the middle cam sleeve 6. The end cams at both ends are respectively the end cam 6a and the end cam 6b, which are respectively engaged with the end cam 31a of the inner ring 31 of the overrunning clutch and the end cam 14b of the axially outer taper sleeve 14 of the annular body to form an engagement pair of end cams; It is beneficial to reduce the radial size and is suitable for small vehicles; the cam-shaped line rise angle of the end face is less than 45°, which is conducive to forming a sufficiently large axial component force and circumferential driving force, and can avoid jamming; the end faces of the middle cam sleeve 6 The lift angles of the cams are different, that is to say, one has a larger lift angle and the other has a smaller lift angle. As shown in the figure, the lift angle α of the end cam 6a meshing with the end cam of the inner ring 31 of the overrunning clutch is smaller than that of the circle The lift angle β of the end face cam 6a engaged with the end face cam of the axial outer tapered sleeve 14 of the ring body, the lift angle β ensures the circumferential driving force, and the lift angle α ensures the circumferential misalignment and realizes the axial outer cone of the ring body. Sensitive axial drive of sleeve 14.

In this embodiment, the overrunning clutch is a shrapnel type overrunning clutch, including a roller 33 and a cage, and an engagement groove for engaging or separating from the roller is formed between the outer ring 15 and the inner ring 31 of the overrunning clutch; The cage includes a support piece 36, a support column 35 and a reed 34. The support column 35 corresponds to the rollers 33 one by one. A slot 37 is formed between the outer surfaces of the columns 35, and the reed 34 is provided with a fitting portion 34a embedded in the slot 37, and the reed 34 extends out of the slot 37 to apply a pre-tightening force to the roller 33 along the engaging direction of the engaging groove. , the slot 37 is provided with a deformation allowance for elastic deformation of the reed 34 due to the pre-tightening force applied to the roller 33; the overrunning clutch of this structure avoids directly processing the limit seat on the outer ring 15, simplifies the processing process, and improves Work efficiency, reduce processing costs, ensure processing and assembly accuracy, and is different from the structure of centralized fixed points in the prior art, does not use spot welding fixed structure, the consequences of metallographic structure changes will not occur, and eliminates the consequences of overrunning clutches The stress concentration caused by the elastic deformation of the engaging and disengaging reeds makes the reed 34 have a better degree of freedom of movement, so the operating life of the reed 34 and the entire overrunning clutch can be improved, and the reed can reach more than 5 million times with The elastic deformation of the pre-tightening force greatly reduces the cost of use and maintenance; the related parts of the present invention are easy to replace after damage, and the outer ring 15 does not need to be scrapped as a whole, which reduces maintenance and use costs; The axial length of the overrunning clutch and the roller 33 is infinitely extended to increase the meshing length, that is to say, the axial length of the overrunning clutch can be increased according to the load-bearing requirements, thereby increasing the carrying capacity of the overrunning clutch and reducing the load-bearing capacity of the overrunning clutch The radial dimension of the overrunning clutch is lower, prolonging the service life of the overrunning clutch; at the same time, because the reeds are distributed along the axial direction, the preload can be applied to the rollers at multiple points according to the needs, ensuring that the premise of longer axial dimension The limit balance of the lower pair of rollers makes it not deviate from the parallel axis of the inner ring, so as to ensure the stable operation of the overrunning clutch and avoid mechanical failure;

As shown in the figure, the support piece 36 is wrapped around the support column 35 in the circumferential direction and the pre-tightening force is set. The cross section of the support column 35 is a non-circular shape that can limit the relative rotation of the support piece 36 in the circumferential direction. A slot 37 is formed between one side of the support piece 36 and one side surface of the support column 35; the cross section of the support column 35 adopts a special-shaped structure, and the support piece 36 is wrapped around the support column 35 to limit its rotation in the circumferential direction, and the structure is simple , easy to implement and disassemble, use the non-circular structure to limit the circumferential movement of the support piece 36, form a relatively stable slot 37 structure, provide conditions for the installation of the reed 34, do not need additional mechanical fixing structures, and avoid due to Structures such as spot welding form the mechanical force on the reed to ensure its service life; as shown in the figure, the cross section of the support column 35 is a special-shaped structure composed of arcs and straight lines, and the support piece 36 is wrapped around the outer periphery of the special-shaped structure, so that it There is no relative rotation condition.

In this embodiment, the fitting portion 34a is provided with a pressure-receiving portion 34b, and the supporting piece 36 is provided with a pressure-receiving portion 34a to apply pressure to insert the fitting portion 34a into the slot 37 and restrict the fitting portion 34a from inserting into the socket 37. The pressing portion 36a protruding from the groove prevents the embedding portion 34a from protruding while ensuring that the reed 34 has a better degree of freedom to swing, prolonging its service life.

In this embodiment, the pressure receiving portion 34b is integrally formed on the fitting portion 34a and is an elastic sheet structure extending outward. The pressure receiving portion 34b is bent toward the pressing portion 36a to form a pressure receiving section 34c. The pressing part 34b is bent to form a pressing part 36b which is superimposed on the outer surface of the pressure-bearing section 34c and exerts pressure on the pressure-bearing section 34c; the pressure makes the fitting part fit into the slot 37 to form a stable fitting structure; as shown in the figure As shown, the bending adopts a smooth transition structure to avoid stress concentration. When installing, the external force is directly submerged and the pressure-bearing section is superimposed on the pressing section, and the pressure-bearing section itself is used to form the embedded force. The structure is simple and the installation is convenient. Large deformation and stress concentration will occur.

As shown in the figure, the cage also includes a support ring I32 and a support ring II24. The support ring I32 and the support ring II24 are arranged at the two ends of the outer ring 15 in the axial direction and are fixedly fitted with the outer ring 15 in the circumferential direction. The two ends of the support column 4 are respectively supported by the support ring I32 and the support ring II24, and the support column 35 is fixedly matched with the support ring I32 or/and the support ring II24 in its own circumferential direction; after assembly, the support ring I32 and the support ring II24 can be screwed , riveting and fixed on the outer ring 15, and can also be fixed on the outer ring 15 by other components; as shown in the figure, the support column 35 is parallel to the roller 33; the meshing direction of the meshing groove is that the meshing groove gradually becomes shallower direction, that is, the direction in which the meshing space formed by the meshing groove and the outer circle of the inner ring 31 gradually narrows; the elasticity of the reed 34 is sufficient to prevent the rollers from reversely meshing when the overrunning clutch is overrunning; as shown in the figure, the supporting column One end of the 35 axial direction forms a flat shaft, and the flat shaft is correspondingly inserted into the flat hole of the support ring I32 to form a fixed fit structure in the circumferential direction. Therefore, there is a better positioning effect, which is beneficial to assembly and maintains a better running state; the other axial end of the support column 35 passes through the round hole on the support ring II 24, and the support column passes through the end of the round hole on the support ring II to form a Conical head, the structure of the conical head has better adaptability, which is conducive to penetration and assembly, and improves work efficiency.

Both the support ring I32 and the support ring II24 are made into a sliding bearing structure; as shown in the figure, sinking grooves are formed at both ends of the outer ring 15 in the axial direction (sinking groove 15a and sinking groove 15b as shown in the figure), so The radial grooves (radial groove 15a and radial groove 15b) at both axial ends of the outer ring 15 are respectively arranged in the inner circle of the corresponding sinker groove wall, and the support ring I32 and the support ring II24 are respectively embedded in the sinker Groove, support ring I32 and support ring II24 are respectively provided with radial protrusions (radial protrusions 32a and radial protrusions 24a) for correspondingly embedded in radial grooves (radial grooves 15a and radial grooves 15b) , the radial projections (radial projections 32a and radial projections 24a) of the support ring I32 and the support ring II24 are opposite to the corresponding radial grooves (radial groove 15a and radial groove 15b), along the shaft Just push it in; it forms a support between the outer ring 15 and the inner ring 31 and helps to keep the cage compact in structure and stable in assembly, and will not fall off due to external force interference; at the same time, it is conducive to the stable operation between the outer ring and the inner ring .

In this embodiment, the intermediate deceleration transmission mechanism includes a slow gear intermediate shaft 18, a first slow gear 20 and a second slow gear 19 arranged on the slow gear intermediate shaft 18 and cooperating with its transmission. As shown in the figure, the slow gear The intermediate shaft 18 is provided with a radial rolling bearing 22 and a radial rolling bearing 16, which can be rotated and matched with the transmission case during use; Engagement transmission, as shown in the figure, the axial inner taper sleeve 17 of the annular body is connected to the slow gear driving gear 10 through the end face spline or other transmission methods in the prior art, and the second slow gear 19 is connected to the outer ring of the overrunning clutch. 15 meshing transmission; the structure is simple and compact, and the power transmission of slow gear is realized.

In this embodiment, the variable-speed elastic element 25 is a variable-speed disc spring that is sheathed on the transmission shaft 1, and the variable-speed disc spring and the inner ring 31 of the overrunning clutch are arranged on the two axial sides of the axial outer taper sleeve 14 of the annular body. On the other side, the speed change butterfly spring is fitted with the speed change sleeve 21 of the drive shaft 1 by sliding to withstand one axial end of the axial outer tapered sleeve 14 of the annular body, and the other axial end of the axial outer tapered sleeve 14 of the annular body It cooperates with the middle cam sleeve 6 through the corresponding end cam pair; the structure is simple, the arrangement space is small, and the parts are arranged rationally by using the power transmission route, so that the present invention is more suitable for use in a small space.

In this embodiment, the variable speed butterfly spring is arranged on the right side of the axial outer tapered sleeve 14 of the annular body, and the overrunning clutch is located on the left side of the axial outer tapered sleeve 14 of the annular body; The expansion direction of the inner helical cam of 14 and the outer helical cam of the transmission shaft 1 is the same as the power output rotation direction of the transmission shaft from left to right; the two ends of the intermediate cam sleeve 6 and the inner ring 31 of the overrunning clutch and the axial Outer cone sleeves 14 are provided with end cams respectively, and the end cams mesh with each other to form an end cam meshing pair. As shown in the figure, the slow gear driving gear 10 is rotated and fitted over the middle cam sleeve 6, and the annular body is axially inner. Radial rolling bearing 23 is provided to support and ensure stability during installation; the end face cam 31a of the inner ring 31 of the overrunning clutch, the end face cam 14b of the axial outer taper sleeve 14 of the annular body, the end face cam 14b and the end face cam 31a and the middle The cam sleeves 6 cooperate to form an end face cam pair for transmission; as shown in the figure, the outer circle of the inner ring 31 of the overrunning clutch is located on the right side of the overrunning clutch and is provided with an annular boss, and the annular boss is connected with the slow gear driving gear 10 in turn. A plane bearing 8 and a limit ring 11 are provided to limit the axial position. The left end of the inner ring 31 of the overrunning clutch is provided with a plane bearing 11, and the positioning is realized through mechanical installation to achieve a relatively stable axial limit; the middle The two ends of the cam sleeve 6 and the inner ring 31 of the overrunning clutch and the end face cam engagement line of the annular body axially outside the taper sleeve 14 develop from left to right and are opposite to the power output rotation direction of the transmission shaft.

The above embodiments are only the best structures of the present invention, and are not intended to limit the protection scope of the present invention; the schemes adjusted in the connection mode will not affect the realization of the purpose of the present invention.

The fast gear power transmission route of the present embodiment:

Power→annulus axial inner tapered sleeve 17→annular axial outer tapered sleeve 14→inner helical cam 14a of annulus axial outer tapered sleeve→outer helical cam 1a of transmission shaft 1→transmission shaft 1 output power ;

At this time, the overrunning clutch is overrunning, and the resistance transmission route: transmission shaft 1 → external helical cam 1a of transmission shaft 1 → internal helical cam 14a of the axial outer tapered sleeve of the annular body → axial outer tapered sleeve 14 of the annular body → compression shifting Belleville spring; the transmission shaft applies axial force to the inner helical cam 14a of the axial outer tapered sleeve of the annular body and the axial outer tapered sleeve 14 of the annular body through the outer helical cam 1a of the transmission shaft 1 and compresses the variable speed disc spring, when driving When the resistance increases to a certain level, the axial force of the variable-speed butterfly spring separates the axial inner tapered sleeve 17 of the annular body from the axial outer tapered sleeve 14 of the annular body, and the power is transmitted through the following route, that is, the slow gear power transmission route :

Power → ring body axial inner taper sleeve 17 → slow driving gear 10 → first slow gear 20 → slow intermediate shaft 18 → second slow gear 19 → outer ring 15 of overrunning clutch → inner ring 31 of overrunning clutch →Middle cam sleeve 6→Annulus axial outer tapered sleeve 14→Inner helical cam 14a of annulus axial outer tapered sleeve→External helical cam 1a of transmission shaft 1→Transmission shaft 1 output power.

The slow gear power transmission route also passes through the following route at the same time: the middle cam sleeve 6 → the axial outer cone sleeve 14 of the annular body → compresses the variable speed disc spring to prevent the compression of the variable speed disc spring from reciprocating compression during the slow gear transmission, thereby preventing the annular body from The axial inner taper sleeve 17 is fitted to the axial outer taper sleeve 14 of the annular body.

It can be seen from the above-mentioned transmission route that when the present invention is in operation, the inner tapered surface of the axial inner tapered sleeve 17 of the annular body and the outer tapered surface of the axially outer tapered sleeve 14 of the annular body closely fit under the action of the speed change disc spring , to form an automatic transmission mechanism that maintains a certain pressure, and the pressure required for clutch engagement can be adjusted by increasing the axial thickness of the transmission sleeve 21 to achieve the purpose of transmission. At this time, the power drives the axial inner tapered sleeve 17, The annular body axially outer taper sleeve 14 and the transmission shaft 1 make the output power of the transmission shaft 1 rotate counterclockwise; at this time, the slow gear overrunning clutch is in the overrunning state.

When the motor vehicle is started, the resistance is greater than the driving force, and the resistance forces the transmission shaft 1 to rotate clockwise at a certain angle. Under the action of the outer helical cam 1a of the transmission shaft 1, the annular body axially compresses the speed-changing disc spring with the outer tapered sleeve 14; the annular body The axial outer taper sleeve 14 and the annular body axial inner taper sleeve 17 are separated and synchronized, the slow gear overrunning clutch is engaged, and the power drives the annular body axial inner taper sleeve 17, the first slow gear 20, and the slow gear intermediate shaft 18 , the second slow gear 19, the outer ring 15 of the overrunning clutch, the inner ring 31, the middle cam sleeve 6, the axial outer tapered sleeve 14 of the annular body and the transmission shaft 1, so that the output power of the transmission shaft 1 rotates at the slow gear speed; Therefore, low-speed gear starting is automatically realized, the starting time is shortened, and the starting force is reduced. At the same time, the variable speed butterfly spring absorbs the energy of the motion resistance torque, and stores potential energy for restoring the fast gear transmission power.

After the start is successful, the driving resistance decreases. When the component force is reduced to less than the pressure generated by the variable speed disc spring, the pressure of the variable speed disc spring is quickly released due to the compression of the movement resistance, and the outer tapered sleeve 14 in the axial direction of the annular body is completed. The tapered surface and the inner tapered surface of the axial inner taper sleeve 17 of the toroidal body recover the tight fit state, and the slow gear overrunning clutch is in the overrunning state.

During the driving process, the principle of automatic gear shifting with the change of motion resistance is the same as above, and the gear shifting is realized without cutting the driving force, so that the whole locomotive runs smoothly, is safe and low-consumption, and the transmission route is simplified to improve the transmission efficiency.

Finally, it is noted that the above embodiments are only used to illustrate the technical solutions of the present invention without limitation. Although the present invention has been described in detail with reference to the preferred embodiments, those of ordinary skill in the art should understand that the technical solutions of the present invention can be carried out Modifications or equivalent replacements without departing from the spirit and scope of the technical solution of the present invention shall be covered by the claims of the present invention.

Claims (10)

1. mechanical intelligent self adaption cam automatic transmission more than two grades, comprises the transmission shaft outputed power, it is characterized in that: the mechanical intelligent adaptive rate assembly also comprising slow gear driving mechanism and be arranged on transmission shaft;

Mechanical intelligent adaptive rate assembly comprises the axial external conical sleeve of cirque body, the axial inner conical drogue of cirque body and speed change elastic element;

The axial inner conical drogue of described cirque body is used for input power, and the axial inner conical drogue of cirque body is provided with axial inner conical surface and is coated at the axial external conical sleeve of cirque body, the axial male cone (strobilus masculinus) that the axial inner conical surface that the axial external conical sleeve of cirque body is provided with inner conical drogue axial with cirque body matches; The axial external conical sleeve of described cirque body is coated at transmission shaft and is coordinated by the auxiliary driving of main transmission cam with it;

Speed change elastic element applies to make the inner conical surface of its male cone (strobilus masculinus) and the axial inner conical drogue of cirque body to fit the pretightening force of transmission to the axial external conical sleeve of cirque body; During described transmission shaft Power output, main transmission cam is secondary applies the axial thrust load contrary with speed change elastic element pretightening force to the axial external conical sleeve of cirque body;

Described slow gear driving mechanism comprises the intermediate reduction gear driving mechanism with free wheel device, and the axial inner conical drogue of cirque body coordinates with the power intake transmission of intermediate reduction gear driving mechanism; Be rotatably assorted and be coated at transmission shaft and be at least provided with an intermediate cam cover, described intermediate cam is overlapped axial two ends and is respectively equipped with and correspondingly coordinates with the axial external conical sleeve of cirque body and intermediate reduction gear driving mechanism by cam-engaged is secondary and is passed to cirque body axis external conical sleeve by keeping off the clutch end of power by intermediate reduction gear driving mechanism slowly.

2. mechanical intelligent self adaption according to claim 1 cam automatic transmission more than two grades, it is characterized in that: the axial inner conical surface of the axial inner conical drogue of cirque body or and the axial male cone (strobilus masculinus) of the axial external conical sleeve of cirque body be provided with oil groove, this oil groove is provided with for oil-feed and fuel-displaced port.

3. mechanical intelligent self adaption according to claim 2 cam automatic transmission more than two grades, it is characterized in that: the axial male cone (strobilus masculinus) of the axial external conical sleeve of described cirque body is provided with oil groove, described oil groove is left-handed and right hand helix shape interleaved discs is around in axial male cone (strobilus masculinus) and its port is coiled in axial male cone (strobilus masculinus) two ends self-assembling formation by oil groove is left-handed with right hand helix.

4. mechanical intelligent self adaption according to claim 3 cam automatic transmission more than two grades, it is characterized in that: the inner ring of free wheel device is rotatably assorted and is coated at transmission shaft, intermediate reduction gear driving mechanism also comprises the train of reduction gears for power to be passed to free wheel device by the axial inner conical drogue of cirque body, the inner ring of described free wheel device surmounts between the Power output sense of rotation and outer ring of transmission shaft, the axial inner conical drogue of described cirque body is coordinated with the outer ring transmission of free wheel device by train of reduction gears, the axial external conical sleeve of cirque body is passed to by intermediate cam cover by keeping off the inner ring of power by free wheel device slowly between the inner ring of described free wheel device and the axial external conical sleeve of cirque body, the cam-engaged pair at intermediate cam cover two ends is end cam engagement pair, and the shape line lift angle of its end cam is all less than or equal to 45 ° and the shape line lift angle of intermediate cam cover two ends end cam varies in size.

5. mechanical intelligent self adaption according to claim 4 cam automatic transmission more than two grades, it is characterized in that: described free wheel device is elastic sheet type overrunning clutch, comprise roller and retainer, between the outer ring of free wheel device and inner ring, form the engaging groove being used for engaging with roller or being separated; Described retainer comprises support plate, supporting post and reed, described supporting post and roller one_to_one corresponding, described support plate is arranged at supporting post in circumferencial direction secure fit and forms slot between support plate and supporting post outer surface, described reed is provided with the embedding part embedding slot, reed extends slot and applies pretightening force along the engagement direction of engaging groove to roller, described slot be provided with reed due to roller is applied pretightening force produce the distortion allowance of resiliently deformable.

6. mechanical intelligent self adaption according to claim 5 cam automatic transmission more than two grades, it is characterized in that: described embedding part is provided with pressure-bearing portion, described support plate is provided with and applies to make embedding part embed the pressure of slot and limit the nip portion that embedding part deviates from from slot to pressure-bearing portion.

7. mechanical intelligent self adaption according to claim 6 cam automatic transmission more than two grades, it is characterized in that: described pressure-bearing portion is formed in one in embedding part and outward extending elastic piece structure, pressure-bearing portion forms pressure-bearing section to nip portion bending, and nip portion is formed to the bending of pressure-bearing portion and is superimposed on pressure-bearing section outer surface and executes stressed pressing section to pressure-bearing section.

8. mechanical intelligent self adaption according to claim 7 cam automatic transmission more than two grades, it is characterized in that: described train of reduction gears comprise keep off jack shaft slowly, be arranged at that slow gear jack shaft coordinates with its transmission first keep off gear and second and keep off gear slowly slowly, the axial inner conical drogue of described cirque body keeps off meshed transmission gear slowly by slow gear driving gear and first, the outer ring engagement driving of the second slow gear gear and free wheel device.

9. mechanical intelligent self adaption according to claim 8 cam automatic transmission more than two grades, it is characterized in that: described speed change elastic element is the speed change butterfly spring being coated at transmission shaft, described speed change butterfly spring and free wheel device are respectively in the axial both sides of the axial external conical sleeve of cirque body, speed change butterfly spring is coated at the speed change axle sleeve of transmission shaft successively by being slidably matched and speed change plane bearing withstands axial external conical sleeve one axial end portion of cirque body, and axial another axial end portion of external conical sleeve of cirque body is coordinated by corresponding end cam auxiliary driving with intermediate cam cover; The axial external conical sleeve inner circle of cirque body is provided with internal spiral cam, and transmission shaft is provided with the external spiral cam matched with internal spiral cam and jointly forms spiral prominence wheel set.

10. mechanical intelligent self adaption according to claim 9 cam automatic transmission more than two grades, is characterized in that: described speed change butterfly spring is arranged on the right side of the axial external conical sleeve of cirque body, and free wheel device is positioned on the left of the axial external conical sleeve of cirque body; The axial internal spiral cam of external conical sleeve of described cirque body is identical with transmission shaft Power output sense of rotation from left to right with the expansion direction of the external spiral cam of transmission shaft; The inner ring of described intermediate cam cover two ends and free wheel device and the axial external conical sleeve of cirque body are arranged end cam respectively and are intermeshed by end cam and form end cam engagement pair; The end cam line of contact expansion direction of the inner ring of intermediate cam cover two ends and free wheel device and the axial external conical sleeve of cirque body is contrary with transmission shaft Power output sense of rotation from left to right.