EA007997B1 - Stepless transmission (variants) - Google Patents

Abstract

The invention relates to transport mechanical engineering and can be used in the form of a mechanism for the speed variation of power delivery in the transport means. The inventive stepless transmission comprises drive, intermediate and output shafts which are axially arranged with respect to each other, a two double-link planetary differential whose links are disposed at an angle of 180 DEG to each other and whose sun gear is embodied in the form of a drum provided with two rows of internal toothed paths which are constantly meshed with the first and second pinion sets. The first pinion set is connected to the drive shaft by means of a carrier, the second set is connected to the driven shaft, wherein said two shafts are interconnected by means of gears with the intermediate shaft. Said invention also relates to the stepless transmission variants, wherein brake means can be mounted in the drum area on the drive and driven shaft-carriers and/or the dampers and/or breaking devices can be mounted on the drive and driven shafts-carriers in the area of the pinion sets. The inventive two-link planetary differentials can be combined in a successive or in a parallel manner.

Description

Technical field

The invention relates to the field of transport engineering and can be used as a mechanism for changing the speed of power supply, namely in a continuously variable gearbox of vehicles.

A stepless gearbox is known, containing a drive shaft for power supply to the gearbox, an output shaft for power output from the gearbox, a composite planetary mechanism, including two sun gears, two sets of satellites, a carrier, a torque converter, parts of which are connected to certain components of the planetary mechanism ( Pat. Of the Russian Federation No. 2166681 in class P 16 H 37/06, 47/08 from 11/20/97).

The disadvantages of the known solutions are its complexity, low reliability and efficiency, due to structural elements included in the gearbox, and stepless speed changes only during operation during reverse, which limits the use of the known solution.

The closest technical solution to the claimed one is the transmission and rotation mechanism of the vehicle, containing driving, intermediate and output shafts kinematically connected to hydraulic machines, one of which is connected to the sun gears of two planetary differentials, the epicyclic gears of which are connected to the intermediate shaft, and the carrier - with output shafts, and both planetary differentials through the gearbox with the drive shaft. The invention can be used as an infinitely variable transmission and rotation mechanism in transmissions, mainly tracked vehicles (Pat. RF No. 2236356 in class P 16 H 47/00 from 08/26/02).

The disadvantages of the decision adopted for the prototype are its complexity, low reliability due to structural elements, and limited use, mainly for tracked vehicles.

Disclosure of invention

The challenge faced by the inventor was to create a tool with a simplified design, having increased reliability and widespread use for any vehicles.

The task in the known stepless gearbox containing the drive, intermediate and output shafts, two planetary differentials, sun gears, carrier, is achieved by the fact that the drive, intermediate and output shafts are aligned, and the sun gears are made in the form of a drum mounted on an axis with shafts with two rows of internal gear tracks that are in constant engagement with the first and second sets of satellites, of which the first is connected to the drive shaft, the second is connected to the output shaft, interconnected sets of satellites associated with countershaft gears, forming a two-tier planetary differential units which are arranged relative to each other by 180 °.

According to another option, the task in a continuously variable transmission containing drive, intermediate and output shafts, two planetary differentials, sun gears, a carrier, is achieved by the fact that the drive, intermediate and output shafts are aligned, and the sun gears are designed as mounted on an axis with shafts a drum with two rows of internal gear tracks, which are in constant engagement with the first and second sets of satellites, of which the first is connected to the drive shaft, the second is connected to the output shaft, and two sets of satellites are connected by an intermediate shaft with gears, forming a two-link planetary differential, the links of which are 180 ° relative to each other, brake devices are installed in the drum area, as well as on the drive and output shafts, while the brake device is turned on in The drum has a two-link planetary differential that can be converted to a planetary gear, and when the braking devices installed on the drive and output drive shafts are turned on, the two-link differential etarny differential has the ability to transform into a direct transfer.

In the third embodiment, the task in the known stepless gearbox containing drive, intermediate and output shafts, two planetary differentials, sun gears, carrier, is solved by the fact that the drive, intermediate and output shafts are aligned, and the sun gears are made in the form of mounted on the axis with drum shafts with two rows of internal gear tracks, which are in constant engagement with the first and second sets of satellites, of which the first is connected to the drive shaft, the second is connected to the output the carrier shaft, and the sets of satellites are interconnected by an intermediate shaft with gears, forming a two-link planetary differential, the links of which are 180 ° relative to each other, while in the region of the first and second sets of satellites dampers are installed, preferably magnetic, and / or on the drive and output shafts drove installed braking devices and / or dampers.

In addition, the problem is solved by the fact that the ratio of the diameters of the gears of the intermediate shaft and the sets of satellites are selected based on the operating transmission modes, and one of the links of the two-link planetary differential can be asymmetric and the other link symmetrical, or both links can be asymmetric, while any known type of planetary gear can be used as links of a two-link planetary differential.

The task is also achieved by the fact that two-link planetary differentials have the ability

- 1 007997 sequential or parallel aggregation.

The introduction of the alignment of the drive, intermediate and output shafts, the implementation of sun gears in the form of a drum mounted on an axis with shafts with two rows of gear tracks, which are in constant engagement with two sets of planetary differential gears, interconnected by an intermediate shaft with the formation of a single two-link differential with links, 180 ° relative to each other, and the implementation of the drive and output shafts with the carrier function provides the claimed solution with a significant simplification of the design In comparison with the well-known solution, high reliability and widespread use in vehicles of any kind.

Additionally, the application of the invention allows to reduce the size, reduce metal consumption, increase the variability of the mechanism, significantly reduce fuel consumption.

Thus, the inventive stepless gearbox (its variants) solves the problem and meets the criteria of "novelty" and "inventive step".

The best embodiment of the invention

The invention is illustrated by drawings, where in FIG. 1 shows a general diagram of a first embodiment; in FIG. 2 is a kinematic diagram of FIG. one; in FIG. 3 is a general diagram of a second embodiment; in FIG. 4 is a general diagram of a third embodiment; in FIG. 5 is a kinematic diagram of a two-link planetary differential with asymmetric and symmetric links; in FIG. 6 is a kinematic diagram of a two-link planetary differential with two asymmetric links; in FIG. 7 is a kinematic diagram of a two-link planetary mechanism with two different types of links; in FIG. 8 is a diagram with sequentially aggregated two-link planetary differentials; in FIG. 9 is a diagram with parallel aggregated two-link planetary differentials.

The stepless gearbox (Fig. 1) consists of a shaft 2 mounted coaxially in the housing 1 of the drive 2, intermediate 3 and output 4. The intermediate shaft 3 has gears 5 and 6, which are kinematically connected respectively to the first 7 and second 8 sets of satellites, interacting respectively with the leading 2 and output 4 shafts and drum 9, having on the inner side two rows of gear tracks 10, 11 and mounted on one axis with shafts. The shafts 2 and 4 are made with the possibility of implementing the functions of the carrier. This mechanism is a two-link system of planetary differentials set 180 ° relative to each other.

A kinematic diagram illustrating the operation of the device of FIG. 1 is shown in FIG. 2, in accordance with which the device operates as follows.

When power is supplied to the gearbox, the drive shaft 2 drives its rotation through the first set of satellites 7 and the gear track 10, which are constantly engaged, the drum 9 and the intermediate shaft 3. The gear track 11 is in constant gear with the second set of satellites 8 , while the output shaft carrier 4 starts to rotate and delivers power from the gearbox. When the load on the shaft 4, there is a decrease in the speed of the drum 9 and, as a consequence, an increase in the speed of the intermediate shaft 3. This is due to different diameters of the gears 5 and 6, since the gear 6 on the output shaft-carrier 4 side has a smaller diameter than the gear 5 on the side drive shaft 2. The ratio of the diameters of the gears 5 and 6, as well as the gear sets of the satellites depend on the operating conditions.

For example, for a gearbox with a gear ratio of 1: 1-1: 4, the ratio of the diameters of the gears 6 and 5 will be 1: 8.

If the load is removed from the output drive shaft 4, the revolutions increase and the load is evenly transmitted through the first set of satellites 7 and the gear track 10 to the drum 9 and the intermediate shaft 3, bringing the entire shaft system into rotation at the same speed, that is, transmission condition 1 is observed: one.

In the second embodiment (Fig. 3), the continuously variable gearbox consists of coaxial shafts installed in the housing 1 of the drive 2, intermediate 3 and output 4. The intermediate shaft 3 has gears 5 and 6, which are kinematically connected, respectively, with the first 7 and second 8 sets of satellites, interacting respectively with the leading 1 and output 4 shafts and drum 9, having on the inner side two rows of gear tracks 10, 11 and mounted on one axis with shafts. The shafts 2 and 4 are made with the possibility of implementing the functions of the carrier. This mechanism is a two-link system of planetary differentials set 180 ° relative to each other. A brake device 12 is installed between the housing 1 and the drum 9, and the brake devices 13, which can be used for manual adjustment, are installed on the drive 2 and the output 4 drive shafts.

The operation of the device of FIG. 3 is carried out as follows.

The transmission of rotation through the shafts 2, 3 and 4 takes place as described above for FIG. 1. But when the brake 12 is activated, the speed transmitted to the output drive shaft 4 decreases due to the stop of the drum 9. With full braking, the two-link planetary differential turns into a planetary gear and the highest transmission condition is fulfilled. In the above example, this is a gear ratio of 1: 4. When weakening the action of the brake device 12, the drum 9 begins to rotate together with the drive shaft-carrier 2 and the speed of the shaft 4 increases. With incomplete braking

- 2 007997 ratios can be satisfied, for example 1: 1,5, 1: 2, 1: 2,4, 1: 3,2, 1: 3,7 and others. Thus, the use of the brake device 12 helps to reduce speed and, accordingly, increase power.

In the case of the activation of the braking devices 13, the speed transmitted to the output shaft 4 increases. With complete braking, the two-link planetary differential turns into a direct transmission. Thus, the braking devices 13 contribute to reducing the difference in rotation of the shafts 2, 3, 4 and the drum 9, providing the necessary gear ratio during gradual braking.

In the third embodiment (Fig. 4), the continuously variable gearbox consists of coaxial shafts installed in the housing 1 of the drive 2, intermediate 3 and output 4. The intermediate shaft 3 has gears 5 and 6, which are kinematically connected, respectively, with the first 7 and second 8 sets of satellites, interacting respectively with the leading 1 and output 4 shafts and drum 9, having on the inner side two rows of gear tracks 10, 11 and mounted on one axis with shafts. The shafts 2 and 4 are made with the possibility of implementing the functions of the carrier. This mechanism is a two-link system of planetary differentials set 180 ° relative to each other. In the area of the first 7 and second 8 set of satellites, dampers 14, preferably of a magnetic type, are installed, and brake devices 13 and / or dampers 14 are installed on the drive 3 and output 4 drive shafts.

The operation of the device of FIG. 4 is as follows.

The transmission of rotation through the shafts 2, 3, 4 occurs as well as during operation of the device of FIG. 1. To equalize the speeds of the intermediate shaft 3 and the drum 9, dampers are used, for example, when starting off. In this case, the intermediate shaft 3 has a high speed with respect to the drum 9 and the first 7 and second 8 sets of satellites, interacting with dampers 14, reduce the speed difference between the intermediate shaft 3 and the drum 9.

The identical principle of operation of the dampers 14 installed on the leading 3 and 4 output shafts.

The braking devices 13 on the drive 3 and output 4 shafts also work as described above for the device of FIG. 3.

In FIG. 5 shows a stepless gearbox in which link 15 of the two-link planetary differential is symmetrical and link 16 is asymmetric.

The operation of the device of FIG. 5 is also carried out as described above for FIG. one.

In FIG. 6 shows a stepless gearbox in which both links 17 and 18 of the two-link planetary differential are asymmetric.

The operation of the device of FIG. 6 is carried out in a similar manner as in the device of FIG. one.

In FIG. 7 shows a stepless gearbox in which link 19 of the two-link planetary differential is a gear transmission, and link 20 is a gear with an elastic hoop.

The operation of the device of FIG. 7 is similar to the operation of the device of FIG. one.

The examples given do not limit the use of any known type of planetary gears.

In FIG. Figure 8 shows the sequential aggregation of two-link planetary differentials that form a single gearbox, which reduces the size.

In FIG. Figure 9 shows the parallel aggregation of two-link planetary differentials forming a single gearbox.

The devices shown in FIG. 8 and 9, allow you to create various configurations and expand the possibilities of using continuously variable gearboxes for any type of vehicle.

Claims (11)

CLAIM 1. A continuously variable transmission containing the leading, intermediate and output shafts, two planetary differentials, sun gears, carrier, characterized in that the leading, intermediate and output shafts are aligned, and the sun gears, made in the form of a drum mounted on the shaft with the shafts two rows of internal gear tracks, which are in constant engagement with the first and second sets of satellites, the first of which is connected to the master shaft, the second is connected to the output carrier shaft, and between them sets of LTL connected with countershaft gears, forming a two-tier planetary differential units which are arranged relative to each other by 180 °. 2. A continuously variable transmission containing the leading, intermediate and output shafts, two planetary differentials, sun gears, drove, characterized in that the leading, intermediate and output shafts are aligned, and the sun gears, made in the form of a drum mounted on the shaft with the shafts two rows of internal gear tracks, which are in constant engagement with the first and second sets of satellites, the first of which is connected to the master shaft, the second is connected to the output carrier shaft, and between them sets of LTL linked pro - 3 007997 inter-shaft with gears, forming a two-link planetary differential, the links of which are located relative to each other by 180 °, while in the area of the drum, as well as on the drive and output shafts, the brakes are installed. 3. A continuously variable transmission according to claim 2, characterized in that when the braking device is activated in the area of the drum, the two-stage planetary differential can be converted into a planetary gear. 4. Variable transmission according to claim 2, characterized in that when the braking devices are installed on the drive and output shafts, the two-link planetary differential can be converted into a direct gear. 5. A continuously variable transmission containing the leading, intermediate and output shafts, two planetary differentials, sun gears, drove, characterized in that the leading, intermediate and output shafts are aligned, and the sun gears, made in the form of a drum mounted on the shaft with the shafts two rows of internal gear tracks, which are in constant engagement with the first and second sets of satellites, the first of which is connected to the master shaft, the second is connected to the output carrier shaft, and between them sets of Litas are connected by an intermediate shaft with gears, forming a two-link planetary differential, the links of which are 180 ° relative to each other, while dampers are installed in the area of the first and second sets of satellites and / or brakes and / or dampers are installed on the drive and output shafts . 6. A continuously variable transmission according to claim 5, characterized in that magnetic dampers are preferably installed as dampeners. 7. A continuously variable transmission according to claims 1-6, characterized in that the ratios of the diameters of the intermediate shaft gear and sets of satellites are selected based on the operating modes of the gears. 8. A continuously variable transmission according to claims 1-7, characterized in that one of the links of the two-link planetary differential may be asymmetric, and the other link may be symmetrical. 9. A continuously variable transmission according to claims 1-7, characterized in that both links of the two-link planetary differential may be asymmetric. 10. Continuously variable transmission according to claims 1-9, characterized in that any known type of planetary gear can be used as links of the two-link planetary differential. 11. Continuously variable transmission according to claims 1-10, characterized in that the two-link planetary differentials have the possibility of sequential or parallel aggregation.