Eccentric-cycloidal engagement of complex tooth profiles

FIELD: machine building.

SUBSTANCE: profiles of gears (1,2) are composed of similar turned one relative to another crowns. Crowns of gear (1) have one tooth and correspond to eccentric setoff circumferences (3). Crowns of gear (2) have crowns (8, 8', 8") of cycloidal profile. Each crown of one tooth gear (1) is formed with external sleeve (4) of bearing (5) set on eccentric set off section (6) of common shaft (7).

EFFECT: reduced skidding of engaged profiles.

5 cl, 6 dwg

 

The invention relates to a toothed gearing and can be used as a mesh, composite wheels, and gearing composite wheels and composite slats. Gearing can be used in cylindrical and bevel gears external and internal gears, and rack and pinion gears with high load capacity.

Widely used in gears involute toothing wheels with all its advantages has a low bearing capacity, which is determined by the size of the teeth, and also has restrictions on the size ratio to the same degree. In practice gear ratio single-stage gearbox rarely exceeds 7. To increase the load capacity of involute gearing is necessary to increase the module of the teeth, which leads to unnecessary increase in the size of the transfer.

Known Cam-cycloidal gearing (EC n.) a compound of the wheels (see Stanowski CENTURIES, Kazakevicius S.M. and other New type of gear wheels with curved teeth. The Handbook. Engineering journal, No. 9, 2008. P.34-39, figure 8). These wheels gearing composed of several rotated relative to each other the same rims. A smaller wheel in mesh has only one tooth, the profile of which in the end section of each of the crown of the description of the circumference, eccentric offset from the wheel axis. The adjacent rims of the wheels - eccentric - rotated relative to each other by an angle depending on the number of crowns is defined as α/n, where α is the angle, which for uniform transmission of motion must be greater than 180°, n is the number of crowns wheels. A larger wheel is made up of crowns cycloidal profile, rotated relative to each other by an angle equal to the angular step of the crown, divided by the number of crowns. Each of the crowns of larger wheels mated with a corresponding smaller crown odnoperogo wheels. Such engagement provides a gear ratio equal to the number of periods of a cycloidal curve, i.e. the number of teeth of the larger sprocket. The mesh lets in one step to provide a gear ratio of 40-50. In addition, with equal-sized wheels, the gearing has a high load capacity compared to involute, and under the same load capacity is much smaller. The main drawback of this engagement is that the slippage between the Cam and cycloidal profiles, albeit small, but still exists, which reduces the maximum possible efficiency gearing.

It is also known the use of this same system Cam-cycloidal gearing into the pinion, which is olaso, and the rail is composed of individual shifted in phase toothed crowns (Stanowski CENTURIES, Kazakevicius S.M. and other Eccentric-cycloidal gearing gears and mechanisms based on it. Proceedings of the scientific-technical conference with international participation "Theory and practice gear box Assembly", Izhevsk, 3-5 December 2008, P.148-152). Gear rack with eccentrico-cycloidal gearing composite profiles comprises a gear wheel and the rack installed with the possibility of translational movement relative to each other. The wheel and the rail is composed of individual teeth, crowns, shifted relative to each other in phase. Each crown wheel has a tooth profile in the mechanical section of the wheel in a circle eccentric offset from the axis of rotation of the wheel. Every crown Reiki is made with the teeth of a cycloidal profile, same rims of the wheels and rails are conjugate to each other.

In pinion interlocking engagement exhibits the same properties high load capacity and also not completely devoid of slippage effect of teeth.

Thus, the object of the invention is to provide a gear of the compound gear profiles with an increased efficiency.

The technical result achieved by the invention is to eliminate proschalsya the I between the mating profiles.

To solve the problem in Cam-cycloidal engagement compound gear profiles, as in the prototype, each profile is composed of individual shifted in phase relative to each other crowns. The crowns of one of the profiles have one tooth in the form of an eccentric offset from the center of rotation of the profile of a circle, so that the profile represents a system of eccentrics, rotated relative to each other. Crowns have another profile of a cycloidal shape. Unlike the prototype Cam crowns odnoperogo profile formed by the outer race of the bearings, mounted on the eccentric and offset phase plots common shaft. Thus, with each crown cycloidal profile mates outer ring of the corresponding bearing.

This link can be used as an engagement composite cylindrical wheels internal and external gearing, and an integral conical wheels.

In addition, if the profile of the crown of a cycloidal shape to perform in the form of a toothed rack, composed of individual shifted in phase crowns, then this solution forms a rack and pinion gearing.

All the above varieties gearing gear profiles are equally made the profile with a single tooth crowns which formed the outer rings of the bearings, p is suzannah on rotated relative to each other eccentrics of one shaft.

In order to be able simply to assemble such a profile suitable eccentric sections of the common shaft to perform with progressively decreasing along the axis from the mid-shaft diameters. In this case, the inner diameter of the bearings must also consistently decreased, while the outer diameter of the bearings should remain unchanged.

The invention is illustrated in graphic materials, in which figure 1 shows a General view siteplease profiles for option a cylindrical wheels external gearing. Figure 2 shows a cross-section odnoperogo composite profile made according to the invention. Figure 3 shows a cross-section odnoperogo composite profile, in which bearings of different sizes, and figure 4 shows the position and dimensions of the inner and outer diameters of bearings for different crowns odnoperogo profile figure 3. Figure 5 shows a General view of the gearing for option internal gears cylindrical wheels. 6 illustrates the use of the invention in a rack and pinion gear.

Refer to figures 1 and 2, where siteplease profiles presents a cylindrical composite wheels 1 and 2 external gearing. Profiles of smaller 1 and 2 more wheels are made up of individual crowns. In figure 1 for clarity shows only a fragment of sacal the tion, ie shows only three of the five crowns each composite profile. The rims of the wheels 1 have one tooth in the form of a circle 3, the eccentric offset distanceeaxis OO1 rotation of the wheel 1. Each odnopolyj the crown 3 is formed of the outer race 4 of the bearing 5. The bearing 5 of each crown is planted on the eccentric section 6 common shaft 7. Eccentric sections 6, 6', 6”, ... rotated relative to each other at an angle, which in this case is equal to the angular step of the wheel divided by the number of crowns. This corner for five crowns is 360/5=72°. As a result, the rims 3 of the wheel 1, which represents the outer surface of the outer ring 4 of the bearing 5, is also rotated relative to each other at the same angle.

More wheel 2 is composed of 8 crowns cycloidal profile. For the outer wheel toothing profile defined equidistantly epicycloid. Neighboring crowns 8 and 8'; 8' and 8”, etc. are rotated relative to each other by an angle equal to the angular step of the crown 8, divided by the number of crowns. I.e. the angle of rotation of the crowns is defined as 360/z/n, where z is the number of teeth of the crown 8, and n is the number of crowns. For profiles in figure 1, this angle is 8°. Engages the respective rims of the wheels 1 and 2, and the tooth wheel 1 forms the outer ring 4 of the bearing 5. I.e. with a cycloidal teeth crowns 8 integrated exterior cartridge bearings 4 and 5 of the drawings to show an example of rolling bearings, with higher efficiency, but, in principle, it could be the bearings, made of antifriction material.

Technologically, the task of planting the bearings 5 are rotated relative to each other eccentrics 6 can be solved as follows. For the eccentric sections of the common shaft 7 perform different diameters decreasing from mid-shaft to its ends, as shown in figure 3 and 4. The Cam 9 in the middle of the shaft 7 has a maximum size. Accordingly, the bearing 10, which is planted on this Cam also has the largest inner diameter. Adjacent to the left and right eccentrics 11 and 12 have diameters smaller than the eccentric shaft 9, by an amount which takes into account their rotation relative to the Cam disk 9. This means that the circumference of the eccentrics 11 and 12 fit into the circumference of the eccentric 9, therefore, the bearing 10 is freely fitted on the eccentric shaft 9 with any of the parties, bypassing the eccentrics 11 and 12. Similarly eccentrics 13 and 14 at the edges of the common shaft 7 have a diameter smaller than that of the eccentrics 11 and 12, and corresponding to the circumference of the Cam disc also fit into the circumference of the eccentrics 11 and 12. The bearings 15 and 16 pass freely through the eccentrics 13 and 14 and put on eccentrics 11 and 12. The diameter of the shaft 7 is also less than the diameter of the eccentrics 13 and 14, and then the Assembly is still the same way. On wenye the diameters of all of the bearings 10, 15, 16, 17 and 18 are the same, i.e. we obtain an integral toothed profile of the same rims that are rotated relative to each other.

Figure 5 smaller odnopoloe wheel made exactly as shown in figure 2, a larger wheel 19 is composed of 20 crowns internal gears. Adjacent the rims 20, 20', 20”, ... are the teeth of a cycloidal profile (for internal gearing is equidistant hypocycloid) and rotated relative to each other by an angle equal to the angular step of the crown, divided by the number of crowns. For gearing figure 5, this angle is 360°/9/5=8°. Here with internal cycloidal teeth crowns 20 mated well as the outer casing 4 bearings 5, mounted on eccentrics 6, forming crowns composite wheel 1.

Figure 6 in mesh composite profile includes all the same odnopoloe smaller wheel 1 and the crowns of compound 21 rack 22. Crowns 21 also have a cycloidal profile, for which Reiki is a equidistants cycloid. With cycloidal crowns 21 mated external cartridge bearings 4 and 5.

Consider the work of the proposed engagement by the example of cylindrical wheels external gearing, shown in figure 1. When turning wheel 1 clockwise, as shown in the drawing, the crown 3 of the wheel 1 is in the phase of the power contact with the crown 8 of the wheel 2. I.e. when turning the Cam screw 3 the external ferrule 4 bearing 5 will put pressure on the tooth crown 8, causing it to rotate about the axis in a counterclockwise direction. Exactly the same power contact through the bearing bracket will be crowns 3' and 8'. But the crowns 3” and 8” in this position will start coming out of the power contact, i.e. to take off. Upon further rotation of the wheel 1 position non-working crowns continuously changes, but all the time you'll have at least one crown in working position (position power). Thus, rotation of the wheel 1 one turn will cause rotation of the wheel 2 by an angle corresponding to its angular step. The rotation of the wheel 1 is converted to the opposite rotation of the wheel 2 with a gear ratio equal to the number of teeth of the larger sprocket. When the rotation of the respective profiles slippage relative to each other will be compensated by the rotation of the bearing bracket. I.e. friction losses in engagement actually will be determined by the losses in the bearings, which are very small.

All other options are gearing figure 5 and 6 operate in the same way, except that the rack profile 22 figure 6 will not be rotated by an angular step of rotation of the wheel 1, and linearly move to the appropriate step.

Thus, the invention describes a new type of eccentric-cycloidal gear meshed which I has the least possible loss to the slippage of the profiles relative to each other.

1. Eccentric-cycloidal gearing compound gear profiles, each of which is composed of individual shifted in phase relative to each other crowns, and crowns one profile have one tooth in the form of an eccentric offset from the center of rotation of the profile of a circle, and the crowns have another profile of a cycloidal shape of the teeth, characterized in that each Cam crown odnoperogo profile formed by an outer bearing bracket, mounted on the eccentric offset area of the common shaft.

2. Eccentric-cycloidal gearing profile according to claim 1, characterized in that the profiles are made in the form of a cylindrical composite wheels external gearing.

3. Eccentric-cycloidal gearing profile according to claim 1, characterized in that the profiles are made in the form of a cylindrical composite wheels with internal engagement.

4. Eccentric-cycloidal gearing profile according to claim 1, characterized in that the profile of the crown of a cycloidal shape made in the form of a toothed rack, composed of individual shifted in phase rack crowns.

5. Eccentric-cycloidal gearing profiles according to any one of claims 1 to 4, characterized in that the eccentric sections of the common shaft odnoperogo profile sootvetstvenno internal diameters of bearings are of progressively decreasing from the middle of the common shaft to the edges dimensions, and outer diameters of all bearings are the same.



 

Same patents:

FIELD: machine building.

SUBSTANCE: gear transmission contains driven wheel, teeth (2) of which are implemented with plane work surfaces (3) and, drive wheel, teeth (5) of which are implemented with convex work surfaces (6), joined to plane work surfaces (3) by line of engagement, corresponding part "Pascal's limacon".

EFFECT: reliability growth ensured by accurate gearing of teeth.

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FIELD: technological processes, casting.

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Motion converter // 2308603

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10 cl, 6 dwg

FIELD: mechanical engineering.

SUBSTANCE: according to invention, body 10 forms prismatic chamber 12 whose cross section is oval of odd order formed from arcs 34, 36, 38 with first smaller radius of curvature and arcs 40, 42, 44 with second, larger radius of curvature changing continuously and differentially one into the other. Thus, corresponding cylindrical parts of inner surface of chamber are formed. Chamber 12 accommodates rotating piston 60 whose cross section forms oval of the order smaller by 1 than order of chamber 12. Opposite parts of side surface are formed on rotating piston 60, one of which rotates in part of inner surface of radius of curvature equal to said part and the other adjoins opposite part of inner surface to slide along surface. rotating piston 60 divides chamber 12 in any position into two working spaces 78, 80. Instantaneous axes of rotation 112, 114 of rotating piston 60 are determined on middle plane of piston being fixed for a short time. Working agent to set rotating piston 60 into motion is periodically introduced into working spaces. Rotating piston 60 rotates in each phase of its motion in one of opposite parts of its side surface 70 in corresponding part of inner side surface 62 of chamber around corresponding instantaneous axis of rotation 112 and slides by opposite part of its surface 72 along corresponding opposite part of inner side surface 54 of chamber 12 to stop, i.e. until it comes into extreme position. Then, to execute following phase of movement, instantaneous axis of rotation jumps from previous position into second possible position 114 relative to piston and is fixed in this position for a short rime. Driven or driving shaft 102 is in engagement with rotating piston 60. To prevent kinematic ambiguity of instantaneous axis of rotation in extreme position, instantaneous axis of rotation is mechanically fixed in each extreme position for a time (Fig.1).

EFFECT: improved efficiency of machine in operation.

20 cl, 79 dwg

Gearing device // 2289046

FIELD: mechanical engineering.

SUBSTANCE: gearing device comprises two gear racks and gear wheel. The recess is provided between the racks (26) and (28) to prevent gear wheel (10) against the contact with both of the racks simultaneously. The adapting gear member between two racks is defined by the convex gear arc. When gear wheel (10) engages adapting member (30), it disengages rack (26) immediately before the moment when it engages rack (28).

EFFECT: improved structure.

13 cl

FIELD: mechanical engineering.

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EFFECT: enhanced efficiency.

7 cl, 6 dwg

FIELD: mechanical engineering.

SUBSTANCE: converter comprises the rack, gearing, output shaft, two overloading clutches, and thrusts. The rack connected with the pivot is in coincidence with the overrunning clutches which are in a staggered contact with conical gears. The movement of the conical pivots are limited by means of the pinion secured to the output shaft. The racks provided with the gearing and overrunning clutches are interposed between the two conical gearings.

EFFECT: simplified structure.

1 dwg

FIELD: railway transport.

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EFFECT: uniform wear of braking surfaces, wheels locking in all braking conditions.

8 dwg

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