RU2389922C2 - Method of torque transfer and variator tooth gear - Google Patents

Abstract

FIELD: machine building.

SUBSTANCE: in disclosed tooth gear torque from driving shaft (3) to driven shaft (4) is transmitted with at least one tooth gear. Gear wheels (1, 2) of the said gear can slide along their proper shafts without relative rotation and have spiral teeth with random cross section. Depending on load applied to the driven shaft at any moment of torque transfer the meshing point travels along generatrices so, that increase of diametre and incline angle of teeth of one gear respond to decrease of diametre and incline angle of teeth of another gear.

EFFECT: expanded arsenal of technique.

10 cl, 4 dwg

Description

Field of Invention

The present invention relates to mechanical engineering and can be used as a gear transmission with the property of redistribution of forces on the teeth of the wheels, as well as as a differential.

State of the art

Various gear arrangements are currently known.

The hypoid, chain, planetary and other gears are known from the prior art (see P.G. Guzenkov. Machine details: Textbook for high schools. - 4th ed., Rev. M .: Higher school., 1986. - 359 p. .).

The hypoid gear transmission includes two bevel wheels with oblique or curved teeth located on intersecting axles, the axis of one of the wheels being offset from the axis of the other gear.

The disadvantage of hypoid transmission is the increased risk of seizure, as well as the inability to change the transmission operating mode.

The chain transmission includes two gears (sprockets) located at a certain distance from each other, interconnected by a chain enclosing them.

The disadvantages of this transmission are chain stretching during operation, the occurrence of significant dynamic loads at high speeds and noise.

A planetary gear transmission includes satellites interconnected and moving relative to two central wheels by means of a carrier.

The disadvantages of this transmission are increased accuracy and manufacturing complexity.

The closest in design is the worm gear transmission known from the prior art (see P.G. Guzenkov, Machine Details: Textbook for high schools. - 4th ed., Rev. M .: Higher school, 1986. - 359 p. ), consisting of a gear ("worm") and a worm wheel, which have curved teeth and are mounted on intersecting shafts.

The disadvantage of this transmission is that it does not have the ability to change the operating mode, and is also unable to redistribute the load between the input and output shaft.

Thus, the present invention is the development of such a method of transmitting rotation and implementing this method of gear transmission, which would be free from these disadvantages, and in addition, would provide a technical result in the form of an expansion of the arsenal of technical means.

SUMMARY OF THE INVENTION

In the first object of the present invention, the problem is solved with the achievement of the specified technical result by providing a method of transmitting rotation, which consists in the following: transmit rotation from the drive shaft to the driven shaft by means of at least one gearing; positioning said gears in such a way that they are in gear mating at any moment of transmission of rotation; when transmitting rotation, the point of engagement of the wheels is moved along their generators, depending on the load applied to the driven shaft, while changing the angle of inclination of the teeth and the diameters of the wheels, so that at the mating point of the wheels, increasing the diameter and angle of inclination of the teeth of one wheel corresponds to a decrease in the diameter and angle of inclination teeth of another wheel.

In a variant of the first object of the invention, the problem is solved by the fact that when transmitting rotation, one of the wheels, in addition to rotation around its own geometric axis, has the ability to rotate around the geometric axis of the second wheel.

In the second object of the present invention, the problem is solved with the achievement of the specified technical result by providing a CVT gear comprising: at least one gear mesh; gears of said gearing, mounted with the possibility of free sliding on own shafts without relative rotation, made in the form of bodies of revolution, on the surfaces of which curved teeth are cut with an arbitrary transverse profile so that when the wheels move along the shafts at any moment of transmission of rotation, gear coupling is provided in the place of mating wheels, and the increase in the diameter and angle of inclination of the teeth of one wheel corresponds to a decrease in the diameter and angle of inclination of the teeth of another wheel.

In a variant of the second object of the invention, the problem is solved by the fact that one of the wheels is spring-loaded in the direction opposite to the mentioned movement, while increasing the load on the output shaft.

In another embodiment of the second object of the invention, the problem is solved by the fact that the movement of the said wheels along the shafts is carried out using an external mechanism.

In a third aspect of the present invention, the object is achieved by achieving the indicated technical result by providing a variable speed gear train comprising: at least one gear mesh; gears of said gearing made in the form of bodies of revolution, on the surfaces of which curvilinear teeth with an arbitrary transverse profile are cut, mounted with the possibility of free sliding on its own shafts without relative rotation, while one of the wheels, in addition to rotation around its own axis, has the ability to rotate around the geometrical axis of the second gear of the gear in such a way that when moving the wheels along the shafts at any moment of transmission of rotation, gear mating is provided in a month those mates of the wheels, and an increase in the diameter and angle of inclination of the teeth of one wheel corresponds to a decrease in the diameter and angle of inclination of the teeth of another wheel.

In a variant of the third object of the invention, the problem is solved by the fact that the said wheel is mounted on the frame without relative rotation.

In another embodiment of the third object of the invention, the problem is solved by the fact that the wheel mounted with the possibility of free sliding on the shaft without relative rotation, is spring loaded in the direction opposite to the mentioned movement, with increasing load on the output shaft.

In another embodiment of the third object of the invention, the problem is solved by the fact that the movement of the said wheels along the shafts is carried out using an external mechanism.

In the last embodiment of the third object of the invention, the problem is solved by the fact that three gear wheels participate in the meshing, the geometrical axes of two of which are mounted in the frame, on both sides of the central wheel, opposite each other, so that the wheels, in addition to rotating around their own geometric axes have the ability to rotate around the geometric axis of the central gear wheels.

For all of these facilities, several options may apply. Gears can be made in the form of bodies of revolution, the generators of which can be straight or curved lines.

Brief Description of the Drawings

The present invention is illustrated by drawings, illustrating its possible options for implementation. In all the drawings, the numbers of the reference numerals relating to the same or similar elements are the same.

1 shows an embodiment of a gear train of the present invention when the gears are conical bodies of revolution.

Figure 2 presents an embodiment of the gear train of the present invention, when the gears are conical bodies of revolution with generators in the form of curves.

Figure 3 presents an embodiment of the gear train of the present invention, when one of the wheels, in addition to rotation around its own axis, has the ability to rotate around the geometric axis of the second gear of the gear.

FIG. 4 shows an embodiment of the gear train of the present invention when three gear wheels are engaged, two of which, in addition to rotating around their own axles, are rotatable around the axis of rotation of the central gear wheel.

List of Terms Used

In this description and in the claims, the following terms and expressions are used.

“Gearing” and “gearing” are two gears meshed with one another.

"Teeth ... made with variable angles of inclination, from one base to another of the bodies of rotation of the wheels" - teeth, the angles of elevation of the turns of which, from one base to another of the bodies of rotation of the wheels, are changed.

DETAILED DESCRIPTION OF THE INVENTION

1 shows one gearing. Gears 1 and 2 are mounted on shafts 3 and 4, respectively. Wheels 1 and 2 are conical-shaped screws (worms) with curved teeth 5 made on their lateral (conical) surfaces. The teeth 5, as well as the gaps between the teeth along the entire length of the gears 1 and 2, have the same size, as a result of which the angle of inclination of the teeth From the smaller base to the larger, the wheel cones gradually increase. Shafts 3 and 4 through bearings are installed in the housing 7. Shafts 3 and 4, like the axial holes of the wheel hubs 1 and 2, in their cross sections are square or any other shape that allows the wheels to slide freely along the shafts without relative rotation.

The gear 1 through the thrust bearing is spring-loaded with a spring 6 from the base side of its own cone. The shafts 3, 4 and the wheels 1, 2 of FIG. 1 placed on them are installed in such a way that, at the point of gearing, the large diameter of the cross section and the small angle of the teeth of one wheel corresponds to the small diameter of the cross section and the large angle of the teeth of the other wheel, or vice versa. It should also be noted that the position of the wheels will occur when their diameters and the angles of inclination of the teeth at the interface are the same.

The transmission of figure 1 works as follows.

The torque from the input shaft 3 through the gear wheel 1 is transmitted to the gear wheel 2. From the gear wheel 2, the torque is transmitted to the output shaft 4.

When the load on the output shaft 4 increases, the forces arising in the gearing of wheels 1 and 2 tend to push the wheels along their rotation axes. These movements are counteracted by the spring 6, so that after some movement of the wheels on their own shafts, a new position is established for the balance of forces that wedge the wheels and the spring force. An increase in the diameter and angle of inclination of the teeth of the bevel wheel 1 at the interface when moving along the shaft 3 corresponds to a decrease in the diameter and angle of inclination of the teeth of the bevel wheel 2 when moving along the shaft 4. Conversely, a decrease in the diameter and angle of inclination of the teeth of the wheel 1 when it is moved corresponds to increase in the diameter and angle of inclination of the teeth of the wheel 2.

When reducing the load on the output shaft 4, the spring 6 pushes the wheels 1 and 2 to a new equilibrium position.

Thus, at any position of wheels 1 and 2, the angle of inclination of the teeth and the diameters of the gears are sufficient to ensure mutual engagement of the wheels and the transfer of load.

It should be noted that the transmission control, that is, the movement of gears on its own shafts, is also possible using some external mechanism.

Figure 2 shows a variant of the gear transmission, when the gears have generatrices in the form of curves, while one of the gears is a conical body of revolution with generators, the concavity of which is directed to the axis of rotation of the wheel, and the other wheel is a conical body of revolution with generators the concavity of which is directed from the axis of rotation of the wheel. In Fig.2 the convexity of one wheel corresponds to the concavity of the other and vice versa. The teeth and the spaces between the teeth of the wheels 1 and 2 in the same way as in figure 1, along the entire length of the wheels made of the same size.

The transmission operation of FIG. 2 is completely similar to the transmission operation of FIG. 1.

Figure 3 shows a design of the gear train when one of the wheels has two axes of rotation.

In figure 3, the gears 1, 2 are mounted on the shafts 3, 4, and the shaft 3 is installed in the housing 7, and the shaft 4 is mounted on the frame 8. The frame 8 is movably mounted on the shaft 3, so that the axis of rotation of the frame 8 coincides with the axis of rotation wheels 1. The gear wheel 1 is spring-loaded with a spring 6 from the side of the base of its own cone. The output is the shaft of the frame 8. The design and relative position of the gears are similar to figure 1 and figure 2.

The transmission of figure 3 works as follows.

Torque from the input shaft 3 through the gear 1 is transmitted to the gear 2. From the gear 2 through the shaft 4, the torque is transmitted to the frame 8 and the output shaft.

With a small load on the output shaft of FIG. 3, the axial forces in the gearing are insignificant, and the wheels 1, 2 are on the shafts in the upper and left positions, respectively. The relative motion of the frame 8 is absent.

With increasing load on the output shaft 4 of FIG. 3, the forces arising in the gearing of wheels 1 and 2 tend to push the wheels along their axes of rotation. The spring 6 counteracts these movements, so that after some movement of the wheels along their own shafts, a new equilibrium position is established, in which the teeth of the wheels experience great axial forces. At the same time, due to a change in the angle of inclination of the teeth at the mating point, the frame 8 comes into rotation, thereby compensating for the lack or complete absence of rotation of the wheel 2 around its own geometric axis. The rotation speed of the frame 8 will be the lower, the higher the rotation speed of the wheel 2, and vice versa.

It should be noted that in the case when the gear 2 placed on the shaft 4 is mounted on the frame 8 without relative rotation, when the load changes on the output shaft, the frame 8 will rotate and there will be no complete rotation of the wheel 2 around its own geometric axis.

Thus, the gear according to figure 3, in addition to the redistribution of axial forces on the teeth of the wheels, can be used as a differential.

Figure 4 shows two types of gear construction when three gears are engaged.

Structurally, the mechanism of FIG. 4 is similar to the transmission of FIG. 3 with the difference that two gear wheels 2 and 9 are mounted on the frame 8. Wheels 2 and 9 are placed on both sides of the wheel 1, opposite each other, so that the wheels 2 and 9, in addition to rotation around their own geometric axes, they can rotate around the geometric axis of wheel 1. The output is the shaft of the frame 8.

The transmission operation of FIG. 4 is similar to the transmission operation of FIG. 3. However, the transmission of FIG. 4 has several advantages over the transmission of FIG. 3. The presence of the third wheel in the gear allows you to increase the load capacity of the gear, as well as to balance the forces arising from the interaction of 1 and 2 gears.

The gear train of FIG. 4, like the gear of FIG. 3, in addition to the redistribution of axial forces on the teeth of the wheels, can be used as a differential.

Presented examples of embodiments of the present invention illustrate the work of the proposed: a method of transmitting rotation and a variable speed gear.

All of these examples in the detailed description are intended for illustrative purposes only, and not to limit the scope of this invention. In the examples given, various modifications may be made without departing from the spirit of the present invention. Therefore, the scope of this invention is determined by the attached claims taking into account possible equivalent features.

Claims (10)

1. The method of transmitting rotation, which consists in transmitting rotation from the drive shaft to the driven shaft by means of at least one gearing; positioning said gears in such a way that they are in gear mating at any moment of transmission of rotation; when transmitting rotation, the gearing point of the wheels is moved along their generators depending on the load applied to the driven shaft, while changing the angle of the teeth and the diameters of the wheels so that at the mating point of the wheels an increase in the diameter and angle of inclination of the teeth of one wheel corresponds to a decrease in the diameter and angle of inclination of the teeth another wheel. 2. The method according to claim 1, in which when transmitting rotation, one of the wheels in addition to rotation around its own geometric axis has the ability to rotate around the geometric axis of the second wheel. 3. A CVT gear comprising at least one gear; gears of said gearing, mounted with the possibility of free sliding on own shafts without relative rotation, made in the form of bodies of revolution, on the surfaces of which curved teeth are cut with an arbitrary transverse profile so that when the wheels move along the shafts at any moment of transmission of rotation, gear coupling is provided in the place of mating wheels, and the increase in the diameter and angle of inclination of the teeth of one wheel corresponds to a decrease in the diameter and angle of inclination of the teeth of another wheel. 4. The gear transmission according to claim 3, in which one of the wheels is spring loaded in the direction opposite to the mentioned movement with increasing load on the output shaft. 5. The gear according to claim 3, in which the movement of the said wheels along the shafts is carried out using an external mechanism. 6. CVT gear comprising at least one gear; gears of said gearing made in the form of bodies of revolution, on the surfaces of which curved teeth with an arbitrary transverse profile are cut, mounted with the possibility of free sliding on its own shafts without relative rotation, while one of the wheels, in addition to rotation around its own axis, can rotate around a geometric axis the second gear of the gear in such a way that when moving the wheels along the shafts at any moment of transmission of rotation, gear mating is provided in places e pair of wheels, and an increase in the diameter and angle of inclination of the teeth of one wheel corresponds to a decrease in the diameter and angle of inclination of the teeth of another wheel. 7. The gear according to claim 6, in which said wheel is mounted on a frame without relative rotation. 8. The gear according to claim 6, in which the wheel mounted with the possibility of free sliding on the shaft without relative rotation, is spring-loaded in the direction opposite to the mentioned movement with increasing load on the output shaft. 9. The gear according to claim 6, in which the said wheels are moved along the shafts using an external mechanism. 10. The gear according to claim 6, in which three gear wheels are engaged, the geometric axes of two of which are mounted in a frame on both sides of the central wheel opposite each other so that the wheels, in addition to rotating around their own geometric axes, can rotate around the geometric axis of the central gear wheel.

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