Gear

 

The invention relates to the field of engineering and is intended for lowering and increasing the frequency of rotation of the working bodies of machines and mechanisms. Gear contains several identical stages, including gear and wheel. Each subsequent gear and each succeeding wheel offset from the previous one and the same step. The number of stages in gear and the contact ratio gears are connected by dependency=withn, where- given the overlap ratio gears;cis the coverage factor level; n is the number of stages in gear. The angular spacing between the teeth of the gears and wheels of each step performed in the range from 40 to 90°. The gears can be made convex profile of the teeth, and the wheel is straight, the angle of the pressure profile of the teeth is not more than 8°. Possible execution in gears convex profiles of the teeth and on wheels - concave. The technical result is an increase in the bending strength of the teeth, the transmission efficiency and the reduction of contact stresses. 2 C.p. f-crystals, 6 ill.

Known transfer (see II Artobolevsky I. I. Theory of mechanisms and machines. - M.: Nauka, 1975. - S. 463, Fig. 20.44), which consists of gears and wheels, assembled from multiple identical gears and multiple identical wheels. With each subsequent gear and each succeeding wheel offset from the previous one and the same step. Known transfer recruited from several standard involute gears.

A disadvantage of the known transmission is that when working on increasing the frequency of rotation of the driven shaft this transmission has the following disadvantages. In the transfer of involute profiles of the teeth of power from one profile of the tooth to another tooth profile is sent under the standard angle of 20° , resulting in only one component of this force imparts a motion to the follower wheel, the other causes additional harmful friction in the gears.

In fine-grained involute gears the main criterion for the load capacity of the transmission is the bending strength of the teeth, which in many cases does not meet the requirements set, and the second criterion load capacity predeceased, containing composite wheel formed by interconnected disks, the teeth are offset relative to each other in the plane of rotation, and the thickness of the teeth of each disk is directly proportional to the number of disks comprising each wheel gear, number of teeth of each disk is inversely proportional to the number of discs of each wheel, and the step displacement of the teeth adjacent disks is defined as the product of a constant numbermodule gearing (A. S. No. 911069, MKI F 16 N 11/02).

A disadvantage of the known transmission is that the transmission of forces from one tooth to another occurs under the standard angle of 20 and this causes additional harmful friction and poor contact stress.

The invention solves the problem of increasing the quality of transmission rates: increase the bending strength of the teeth, increasing efficiency and reducing contact stresses for the manual transmission how to decrease and increase the speed of the driven shaft.

The technical result is to increase the bending strength of the teeth, to increase the transmission efficiency and the reduction of contact stresses, while the angle gear involute profile teeth nd many of the same steps, includes gear and wheel, where each successive gear and each succeeding wheel offset from the previous one and the same step, according to the invention the ratio of the number of steps in gear and overlap ratio gear set in accordance with addictions

=withn

where- given the overlap ratio gears;

withis the coverage factor level;

n is the number of stages in gear,

angular step between the teeth of gears and wheels of each step performed in the range from 40 to 90° .

The gears are made convex profiles of the teeth and on the wheels straight, where the pressure angle of the profile of the teeth is not more than 8° .

The gears are made convex profiles of the teeth and on wheels-concave.

It is established that the sequential decrease in the angle of engagement<20° is also consistent reduction of the practical length of the line gear, which ogranichivaetsya, when the angle gearing=10° number of teeth z1=25; when the angle gearing=8° number of teeth z1=31; when the angle gearing=6° number of teeth z1=42. To use the program with a large number of teeth on the gear is not rational, because it has a low Flexural strength of teeth.

The proposed transfer includes the steps with a small number of teeth on the gears.

Performing the angular spacing between the teeth of the gears and wheels of each stage in the range from 40 to 90° allows you to increase the bending strength of gears. To reduce power more harmful friction resistance reduced the lengths of the sliding contact of the profile of the teeth by reducing the height of involute gear teeth and wheels.

Using (instead of the involute profile of the tooth profile of the tooth in A. S. No. 506714, in which the line of engagement is snail Pascal, allows you to increase transmission efficiency, because the change of the parameter snails Pascal allows you to use the pressure angle of the profile of the teeth is less than 8° that snoqiteh (modification profiles M. L. Novikova) can reduce contact stress.

In Fig.1 shows a gear, General view; Fig.2 - section a-a in Fig.2; Fig.3 is a conventional scanner gears: a - for the two gears, b - for the three gears; Fig.4 - shift three gears on the value ofFig.5 - gear transmission with a convex working surfaces on the teeth 3 and with concave or straight teeth 4, General view; Fig.6 - cross section a-a in Fig.5.

Gear contains, for example, two stages, the first stage consists of gears and wheels, the second stage of the gear b and the wheel d (Fig.1 and 2), forming a toothed gear 1 and gear 2 gear. Gears a, b and wheels c, d have the teeth 3 and 4 and are rigidly connected with each other by using, for example, keyed 5 or spline connection. With each successive gear b and each succeeding wheel d is shifted relative to the previous gear and a wheel c on the same step

=D/(zn),

where D is the initial diameter of the circle gear (wheels);

z - number of teeth of the gear (wheels);

n is the number of steps.

Straight teeth 3 speed gear 1 and straight teeth 4 speed wheel 2 fixed to the helical lines of the left and Prada three schemes: 1. convexity and convexity; 2. bulge and plane; 3. convexity and concavity.

The second scheme has a smaller surface tension than the first, and the third circuit than the second.

In gears contact voltage determined by the formula

where- the radius of curvature of the mating surfaces of teeth:1and2the radii of curvature of the working surfaces of gear teeth and a wheel c; " + " sign for the third circuit; the sign "-" for the first scheme.

Given the radius of curvature for the second schema:

From the formula (1) shows that more than the given radius of curvature, the smaller the surface tension of the working surfaces of the teeth of gears and wheels.

For solving the problem of reducing the contact stresses of the adjacent working surfaces of the teeth on the gears a and b is made convex working surface, and the wheels c and d - flat or concave so that for each point of contact vzaimozavisimikh surfaces observed the main theorem gearingwhere/img>- relative velocity vector.

During operation, the teeth 3 of the gears a and b transmit the rotation of the teeth 4 of the wheels c and d. While the teeth 3 and 4, opposite located in steps a and c, b and d, alternately come into engagement with each other. The transmission of rotational motion is performed sequentially from the first stage to the second stage and so on, and the engagement of the teeth subsequent stage overlaps the engagement of the teeth of the previous stage, and the engagement of the teeth of the last stage overlaps the engagement of the teeth of the first degree.

The transmission can be attributed to the helical gear, because straight teeth are proposed transfer are located on the helical lines of the left and right directions on the cylindrical surfaces of gears and wheels.

This transfer has no axial forces, which consumes part of the power connected to the drive shaft in a helical gear.

Claims

1. Gear, containing several identical stages, including gear and wheel, where each successive gear and each succeeding wheel offset from the previous one and the same step, characterized in that the ratio of the number of stages in gear the rc="https://img.russianpatents.com/chr/949.gif" border="0">=withn

where- given the overlap ratio gears;

cis the coverage factor level;

n is the number of stages in gear,

angular step between the teeth of gears and wheels of each step performed in the range from 40 to 90°.

2. Transfer under item 1, characterized in that the gears are made convex profiles of the teeth and on the wheels straight, where the pressure angle of the profile of the teeth is not more than 8°.

3. Transfer under item 1, characterized in that the gears are made convex profiles of the teeth and on wheels - concave.



 

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