阅读说明：本技术 一种膜片弹簧式无级变速器 (Diaphragm spring type continuously variable transmission ) 是由 赵良红 于 2020-08-18 设计创作，主要内容包括：一种膜片弹簧式无级变速器,包括通过传动带连接的主动传动部分和从动传动部分,两传动部分均具有传动轴、固定在传动轴上的定盘、可相对定盘移动的动盘,传动带设置在由定盘、动盘的端面形成的V形槽上,还包括主动压板、从动压板,主动传动部分和从动传动部分的定盘、动盘均设置在主动压板和从动压板之间,变速控制杆连接主动、从动压板,在主动压板与相邻的动盘之间、从动压板与相邻的动盘之间设置膜片弹簧,变速控制机构驱动变速控制杆同步带动主动压板与从动压板沿传动轴轴线移动,从而调整主动传动部分的动盘与定盘之间的距离。本发明利用变速控制机构及变速控制杆,实现传动比的改变,完全克服了采用液压控制的传统无级变速器的各种缺点。(The utility model provides a diaphragm spring formula buncher, include the initiative transmission part and the driven transmission part who connects through the drive belt, two transmission parts all have the transmission shaft, fix the epaxial price fixing, the driving disk that the price fixing removed relatively, the drive belt sets up by the price fixing, on the V-arrangement groove that the terminal surface of driving disk formed, still include the initiative clamp plate, driven clamp plate, the price fixing of initiative transmission part and driven transmission part, the driving disk all sets up between initiative clamp plate and driven clamp plate, the variable speed control pole is connected initiatively, driven clamp plate, between initiative clamp plate and adjacent driving disk, set up diaphragm spring between driven clamp plate and the adjacent driving disk, variable speed control mechanism drive variable speed control pole is synchronous to move initiative clamp plate and driven clamp plate along the transmission shaft axis, thereby adjust the distance between the driving disk and the price fixing of initiative transmission part. The invention utilizes the speed change control mechanism and the speed change control rod to realize the change of the transmission ratio and completely overcomes various defects of the traditional stepless speed changer adopting hydraulic control.)

1. The utility model provides a diaphragm spring formula buncher, includes the initiative transmission part and the driven transmission part that connect through the drive belt, and two transmission parts all have the transmission shaft, fix the epaxial price fixing, the driving disk that the price fixing removed relatively, and the drive belt setting is on the V-arrangement groove that is formed by the terminal surface of price fixing, driving disk, its characterized in that: still include the initiative clamp plate, driven clamp plate, the price fixing of initiative transmission part and driven transmission part, the driving disk all sets up between initiative clamp plate and driven clamp plate, the initiative is connected to the variable speed control pole, driven clamp plate, between initiative clamp plate and adjacent driving disk, set up diaphragm spring between driven clamp plate and the adjacent driving disk, variable speed control mechanism drive variable speed control pole synchronous motion initiative clamp plate and driven clamp plate move along the transmission shaft axis, thereby adjust the distance between initiative and the driving disk of driven transmission part and the price fixing.

2. The diaphragm spring type continuously variable transmission of claim 1, wherein: a thrust bearing is arranged between the diaphragm spring and the movable disc.

3. The diaphragm spring type continuously variable transmission according to claim 2, wherein: the diaphragm spring comprises a round base part and a tooth-shaped film part, the round base part is provided with a shaft hole, the round base part penetrates through the transmission shaft and abuts against the end face of the thrust bearing, and the free end of the tooth-shaped film part abuts against the driving pressing plate or the driven pressing plate.

4. The diaphragm spring type continuously variable transmission according to claim 3, wherein: the tooth-shaped film part is bent towards the driving pressing plate or the driven pressing plate, and the free end of the tooth-shaped film part is provided with an arc-shaped flange.

5. The diaphragm spring type continuously variable transmission of claim 1, wherein: a pair of reverse threads are processed on the variable speed control rod and are respectively in threaded connection with the driving pressing plate and the driven pressing plate.

6. The diaphragm spring type continuously variable transmission according to claim 5, wherein: the end part of the speed change control rod is provided with a speed change control rod gear, the tensioning mechanism is connected with the tensioning driving gear, and the tensioning driving gear is meshed with the speed change control rod gear.

7. The diaphragm spring type continuously variable transmission according to claim 6, wherein: the guide rod is further included, guide holes are formed in the driving pressing plate and the driven pressing plate, and the guide holes of the driving pressing plate and the driven pressing plate are sleeved on the guide rod.

8. The diaphragm spring type continuously variable transmission according to any one of claims 1 to 7, characterized in that: the transmission shaft comprises an input shaft and an output shaft.

Technical Field

The invention relates to the technical field of transmissions, in particular to a diaphragm spring type continuously variable transmission.

Background

The stepless speed variator is a speed variator applied to automobile transmission system, and has the characteristics of simple structure, small volume, light weight, higher transmission efficiency and low manufacturing cost, and has wide application in automobiles.

The stepless speed changer utilizes the friction force between the V-shaped groove and the transmission belt to realize power transmission, and the currently applied stepless speed changer adopts a hydraulic mode to generate pressing force between the V-shaped groove and the transmission belt, and simultaneously changes the transmission ratio by adjusting hydraulic oil.

The defects of the traditional continuously variable transmission are obvious: (1) the V-shaped groove and the transmission belt are easy to slip, and the V-shaped groove and the transmission belt are easy to slip due to the fact that the requirement on oil pressure control accuracy of the continuously variable transmission is high, faults occur easily, pressing force is insufficient, and the V-shaped groove and the transmission belt slip, which is a common fault of the continuously variable transmission and is the most fatal problem. (2) The transmission torque is small and is limited by the maximum oil pressure of the continuously variable transmission system, and the transmission torque is generally small. (3) The speed change is delayed, because the oil pressure building time of the stepless speed changer is slow, the pressing force generated between the V-shaped groove and the transmission belt can not be increased in time, the torque output of an engine can be limited in the acceleration process of the automobile, the situation that the torque of the engine is accelerated too fast to avoid the slippage of the stepless speed changer is avoided, and as a result, the acceleration performance of the automobile is poor, the automobile is not suitable for violent driving, and the driving pleasure is insufficient. (4) The hydraulic control system is complex, difficult to manufacture and high in cost.

Disclosure of Invention

The invention provides a diaphragm spring type stepless speed changer which realizes transmission ratio adjustment through a brand new structure of a diaphragm spring, utilizes elastic force generated by elastic deformation of the diaphragm spring to provide pressing force between a V-shaped groove and a transmission belt of the stepless speed changer, utilizes a speed change control mechanism and a speed change control rod to realize change of the transmission ratio, does not slip when transmitting power, has high reliability, large transmission torque and quick speed change response, is suitable for a large-torque engine, has a compact structure and overcomes the defects of the traditional stepless speed changer.

The technical scheme of the invention is as follows: the utility model provides a diaphragm spring formula buncher, includes the initiative transmission part and the driven transmission part that connect through the drive belt, and two transmission parts all have the transmission shaft, fix the epaxial price fixing, the driving disk that the price fixing removed relatively, and the drive belt setting is on the V-arrangement groove that is formed by the terminal surface of price fixing, driving disk, its characterized in that: still include the initiative clamp plate, driven clamp plate, the price fixing of initiative transmission part and driven transmission part, the driving disk all sets up between initiative clamp plate and driven clamp plate, the initiative is connected to the variable speed control pole, driven clamp plate, between initiative clamp plate and adjacent driving disk, set up diaphragm spring between driven clamp plate and the adjacent driving disk, variable speed control mechanism drive variable speed control pole synchronous motion initiative clamp plate and driven clamp plate move along the transmission shaft axis, thereby adjust the distance between initiative and the driving disk of driven transmission part and the price fixing.

A thrust bearing is arranged between the diaphragm spring and the movable disc.

The diaphragm spring comprises a round base part and a tooth-shaped film part, the round base part is provided with a shaft hole, the round base part penetrates through the transmission shaft and abuts against the end face of the thrust bearing, and the free end of the tooth-shaped film part abuts against the driving pressing plate or the driven pressing plate.

The tooth-shaped film part is bent towards the driving pressing plate or the driven pressing plate, and the free end of the tooth-shaped film part is provided with an arc-shaped flange.

A pair of reverse threads are processed on the variable speed control rod and are respectively in threaded connection with the driving pressing plate and the driven pressing plate.

The end part of the speed change control rod is provided with a speed change control rod gear, the tensioning mechanism is connected with the tensioning driving gear, and the tensioning driving gear is meshed with the speed change control rod gear.

The guide rod is further included, guide holes are formed in the driving pressing plate and the driven pressing plate, and the guide holes of the driving pressing plate and the driven pressing plate are sleeved on the guide rod.

The transmission shaft comprises an input shaft and an output shaft.

Compared with the prior art, the invention has the following advantages:

the diaphragm spring type continuously variable transmission utilizes the elastic force generated by elastic deformation of the diaphragm spring to provide pressing force between a V-shaped groove and a transmission belt of the continuously variable transmission, utilizes a speed change control mechanism and a speed change control rod to realize the change of transmission ratio, completely overcomes various defects of the traditional continuously variable transmission adopting hydraulic control, and has the advantages of: (1) because the pressing force between the V-shaped groove and the transmission belt never disappears, the phenomenon of slipping between the V-shaped groove and the transmission belt cannot occur. (2) The transmission torque is large, and the pressing force between the V-shaped groove and the transmission belt is easy to increase, so that larger torque can be transmitted without limiting the torque output of an engine. (3) The speed change response is fast, a mechanism capable of changing speed fast is adopted, and meanwhile, the pressing force between the V-shaped groove and the transmission belt never disappears, so that the fast speed change can be realized, the acceleration performance of the automobile can be fully exerted, and the driving experience is extremely strong. (4) The hydraulic control system is not used, the manufacturing difficulty and cost of the transmission are reduced, and the fuel efficiency of the automobile is improved.

Drawings

Fig. 1 is a general structural view of an embodiment of a diaphragm spring type continuously variable transmission of the present invention (a partially developed sectional view taken along axis a-a of a shift lever shown in fig. 2).

FIG. 2 is a front end view of an input shaft of an embodiment of the diaphragm spring type continuously variable transmission of the present invention.

FIG. 3 is a rear end view of an input shaft of an embodiment of the diaphragm spring type continuously variable transmission of the present invention.

Fig. 4 is a structural diagram of the diaphragm spring type continuously variable transmission of the invention.

Fig. 5 is a diagram showing the engagement between the shift control lever gear 24 and the tension drive gear 40 of the diaphragm spring type cvt of the present invention.

FIG. 6 is a structural view of the installation relationship between the diaphragm spring type stepless transmission tensioning mechanism and the speed change control rod, the driving pressure plate and the driven pressure plate.

FIG. 7 is a free state diagram of the diaphragm spring type continuously variable transmission of the present invention.

Fig. 8 is a diaphragm spring force diagram of the diaphragm spring type continuously variable transmission of the present invention.

FIG. 9 is a schematic diagram of the diaphragm spring type CVT with the transmission ratio decreasing from the top to the bottom.

FIG. 10 is a schematic diagram of the operation of the diaphragm spring type continuously variable transmission tensioning mechanism for adjusting the pressing force.

Fig. 11 is a structural modification example diagram of the diaphragm spring type continuously variable transmission diaphragm spring of the present invention.

Detailed Description

The invention provides pressing force between the V-shaped groove of the continuously variable transmission and the transmission belt by using elastic force generated by elastic deformation of the diaphragm spring. The deformation of the diaphragm spring is adjusted by changing the distance between the driving pressing plate and the driven pressing plate, so that the pressing force between the V-shaped groove and the transmission belt is adjusted. Meanwhile, the change of the transmission ratio of the transmission is realized through the axial movement of the driving pressure plate and the driven pressure plate.

The technical scheme of the invention is further explained by combining the drawings and the specific embodiments in the specification:

the diaphragm spring type continuously variable transmission is composed of a driving transmission portion 100 (see the dashed line frame portion in fig. 1), a driven transmission portion 200 (see the dashed line frame portion in fig. 1), a guide rod 20, a shift control mechanism 16, a shift control lever 17, a tension mechanism 25, a shift control lever gear 24, a tension driving gear 40, a transmission belt 23, and the like, and is a partial sectional view developed with the shift control lever 17 as an axis as shown in fig. 1, an input shaft front end view as shown in fig. 2, an input shaft rear end view as shown in fig. 3,

the driving transmission part 100 is composed of an input shaft 13, a driving movable disc 11, a driving fixed disc 22, a driving diaphragm spring 12, a thrust bearing 14 and a driving pressure plate 15.

The driving fixed disc 22 of the driving transmission part 100 is fixed on the input shaft 13, the driving movable disc 11 is mounted on the input shaft 13 through a spline and can move axially, a driving V-shaped groove is formed between the driving fixed disc 22 and the driving movable disc 11 after the driving fixed disc 22 and the driving movable disc 11 are assembled, and the thrust bearing 14 is arranged between the driving diaphragm spring 12 and the driving movable disc 11, as shown in fig. 4, which is a diaphragm spring structure diagram. The outer circumferential end of the active diaphragm spring 12 is in contact with the active pressure plate 15. Four corners of the active pressure plate 15 are sleeved on the four guide rods 20.

The structure of the driven power transmission part 200 is the same as that of the driving power transmission part 100.

The driven transmission part 200 is composed of an output shaft 18, a driven movable disk 29, a driven fixed disk 19, a driven diaphragm spring 28, a thrust bearing 27 and a driven pressure plate 26.

The driven fixed disc 19 of the driven transmission part 200 is fixed on the output shaft 18, the driven movable disc 29 is mounted on the output shaft 18 through a spline and can move axially, a driven V-shaped groove is formed between the driven fixed disc 19 and the driven movable disc 29 after the driven fixed disc 19 and the driven movable disc 29 are assembled, and the thrust bearing 27 is arranged between the driven diaphragm spring 28 and the driven movable disc 29. The outer circular end of the driven diaphragm spring 28 contacts the driven pressure plate 26. Four corners of the driven pressure plate 26 are sleeved on the four guide rods 20.

The belt 23 is installed between the driving V-groove and the driven V-groove.

The shift control mechanism 16 is matched with a shift control lever 17, and the shift control mechanism 16 can control the shift control lever 17 to move left and right to change the transmission ratio.

The diaphragm spring can be selected from different structural forms according to the magnitude of the transmitted torque, and as shown in fig. 11, different structural forms are exemplified.

The tensioning mechanism 25 is connected with a tensioning driving gear 40, the tensioning driving gear 40 is meshed with variable speed control rod gears 24 on two sides, the variable speed control rod gears 24 are arranged at one ends of two variable speed control rods 17, two sets of reverse threads are processed on two sides and are respectively matched with the driving pressing plate 15 and the driven pressing plate 26, the distance between the driving pressing plate 15 and the driven pressing plate 26 can be controlled by the rotation of the two variable speed control rods 17, the deformation of the diaphragm spring is adjusted, and the adjustment of pressing force between the V-shaped groove and the transmission belt is realized. Fig. 5 shows the engagement between the shift control lever gear 24 and the tension drive gear 40, and fig. 6 shows the installation relationship between the tension mechanism and the shift control lever 17, the drive pressure plate 15, and the driven pressure plate 26.

Analyzing the working process:

1. power transmission process

The diaphragm spring type continuously variable transmission uses a diaphragm spring to provide pressing force between a V-shaped groove and a transmission belt, and as shown in FIG. 7, the outer circle end of the diaphragm spring is warped when the diaphragm spring is in a free state. As the outer circular end of the diaphragm spring is subjected to pressure, it becomes progressively flatter, as shown in figure 8.

Before power transmission is realized, the tensioning mechanism 25 drives the tensioning driving gear 40 and the speed change control rod gear 24 to rotate to drive the speed change control rod 17 to rotate, so that the driving pressure plate 15 and the driven pressure plate 26 are close to each other to push the driving diaphragm spring 12 and the driven diaphragm spring 28 to generate elastic deformation, and the driving movable disk 11 and the driven movable disk 29 are extruded, so that the V-shaped grooves of the driving transmission part 100 and the driven transmission part 200 respectively generate pressing force with the transmission belt 23, and when the input shaft 13 rotates, power is transmitted to the output shaft 18 by using the friction force between the V-shaped grooves and the transmission belt 23, so that the power transmission is realized.

Transmission ratio variation

As seen in FIG. 1, when the shift control lever 17 is at its leftmost position under the control of the shift control mechanism 16, the driving diaphragm spring 12 and the driven diaphragm spring 24 are also at their leftmost positions. At the moment, the distance between the driving movable disc 11 and the driving fixed disc 22 is the largest, the driving belt 23 is closest to the center of the driving V-shaped groove, and the driving rotating radius is the smallest; the distance between the driven rotary disk 29 and the driven fixed disk 19 is the smallest, and the transmission belt 23 is the farthest from the driven V-shaped groove center, namely, the driven rotary radius is the largest, so that the transmission ratio is the largest at the moment.

When the transmission ratio is to be reduced, the shift control mechanism 16 drives the shift control lever 17 to move rightward, which drives the driving pressure plate 15 and the driven pressure plate 26 to move together rightward along the four guide rods 20, as shown in fig. 9. The driving pressing plate 15 pushes the driving diaphragm spring 12 and the driving movable disc 11 to move right, and the extrusion driving belt 23 moves towards the excircle of the driving V-shaped groove, so that the driving rotating radius is increased; when the driven pressing plate 26 moves to the right, the driven diaphragm spring 28 moves to the right under the self elasticity and the push of the driven movable disc 29, the transmission belt 23 moves to the center of the driven V-shaped groove, the driven rotating radius is reduced, and the transmission ratio is reduced from large to small at the moment.

When the shift control lever 17 is moved leftward under the control of the shift control mechanism 16, the gear ratio is changed from small to large.

Pressing force adjustment between the groove and the belt

The distance between the driving pressure plate 15 and the driven pressure plate 26 is changed by controlling the tensioning mechanism 25 to adjust the pressing force of the V-shaped groove and the transmission belt, thereby adjusting the magnitude of the transmission torque.

As shown in fig. 10, when the tension mechanism 25 drives the tension driving gear 40 and the shift control lever gear 24 to rotate, and the shift control lever 17 is driven to rotate, the distance between the driving pressure plate 15 and the driven pressure plate 26 increases, the elastic deformation of the driving diaphragm spring 12 and the driven diaphragm spring 28 decreases, and the pressing force between the V-shaped groove and the transmission belt decreases, so that the transmission torque decreases.

When the transmission torque is to be increased, the tensioning mechanism 25 controls the distance between the driving pressure plate 15 and the driven pressure plate 26 to be reduced, the elastic deformation of the driving diaphragm spring 12 and the driven diaphragm spring 28 is increased, the pressing force between the V-shaped groove and the transmission belt is increased, and the transmission torque is increased.

When the transmission does not need to transmit power, the tensioning mechanism 25 controls the distance between the driving pressure plate 15 and the driven pressure plate 26 to be maximum, so that the deformation amount of the diaphragm spring is reduced as much as possible.

The diaphragm spring type stepless speed changer of the invention utilizes the elastic force generated by the elastic deformation of the diaphragm spring to provide the pressing force between the V-shaped groove of the stepless speed changer and the transmission belt, utilizes the speed change control mechanism and the speed change control rod to realize the change of the transmission ratio, completely overcomes various defects of the traditional stepless speed changer adopting hydraulic control, and has the advantages that the pressing force between the V-shaped groove and the transmission belt is more reliable, so the V-shaped groove and the transmission belt cannot slide, simultaneously can adopt larger pressing force, can transmit larger torque, does not need to limit the torque output of an engine, has fast speed change response, can completely exert the acceleration performance of an automobile, saves a complex oil pressure control system, reduces the manufacturing difficulty and the cost of the speed changer, and improves the fuel efficiency of the automobile.

The embodiments described above are merely exemplary embodiments of the present invention, and are not intended to limit the present invention in any way, and other variations and modifications are possible without departing from the scope of the invention as set forth in the claims. The technical scheme of the invention is partially changed without creative labor, or equivalent replacement of partial technical characteristics of the technical scheme of the invention belongs to the protection scope of the invention.