Vertical rotor support

FIELD: mechanics.

SUBSTANCE: support surface of rotor trunnion is made in the form of toroidal surface and installed on spherical support surface in cavity of support toe. The latter is installed on a damping element arranged in cavity of housing with lubricating liquid. Radius of toroidal surface of trunnion is 0.4÷0.95 of the radius value of spherical support surface of the toe, and distance between axial line of toroidal surface and trunnion axis is 0.05÷0.6 of the radius value of spherical support surface of the toe. Geometrical parametres of the support meet the ratio: , but not less than 1, where: r - radius of the toe sphere, m; ρ - radius of torodial surface, m; δ- distance between axial line of torodial surface and trunnion axis, m; P - axial load, H; F - radial load, H; β - slope angle of figure end from rotation axis under influence of radial load, rad.

EFFECT: increasing carrying capacity of support and decreasing costs for manufacturing and repairing thereof.

9 cl, 3 dwg

 

The invention relates to supports fast machines and appliances such as energy storage devices, gyroscopes, separators, centrifuges, and particularly to supports of vertical shafts such devices.

Known for vertically loaded bearing rapidly rotating shaft in UK patent No. 1212481, 1969.03.05, F16C 17/08, taken as a prototype. Vertically loaded journal bearing shaft with a rounded radius end is supported in a corresponding recess in the bearing glides. In the bearing glides made the cut, combined with a channel for directing lubricant. The radius of curvature of the sphere axle bearing is either 2/3 of the radius of the spherical recess of the thrust bearing and the field is rounded at the periphery of the shaft to a smaller radius, or less than the radius of the sphere of the thrust bearing. On the journal and on covering the trunnion sleeve made grooves for pumping the grease.

Known bearing has a high voltage in the reference surfaces for the vertical and radial load at a pressure lower sphere pin on the big sphere deepening thrust bearing, which can cause rupture of a lubricating film and the wear of the bearings.

Known vertical rotor in the form of the invention the FSUE PA "electrochemical plant" ("vertical shaft", authors: Kaliteevsky A.K., deaf N, Alekseev A.F., Likhachov A.V.), including submerged in the lubricating liquid is ity bearing surface, performed on the round end of the axle, mounted on a support surface, made in deepening thrust bearing support and bearing surface of the trunnion is made in the form of a toroidal surface and the bearing surface of the thrust bearing made in the form of a spherical surface. The radius of the toroidal surface of the trunnion is 0.4÷0,95 on the radius of the spherical bearing surface of the thrust bearing, and the distance between the axial line of the toroidal surface and the axis of the trunnion is 0.05÷0.6 of the radius of the spherical bearing surface of the thrust bearing.

Known technical solution allows you to create simple to manufacture support a rapidly rotating rotor with increased load capacity while reducing the cost of manufacture and repair support. However, with some ratios, axial and radial load support favorable conditions for interaction and lubrication of the contacting bearing surfaces of the torus and the sphere can be broken, which leads to premature wear of the bearings and its their order.

The problem to which the present invention is directed, is to create an easy to manufacture support a rapidly rotating rotor for a given ratio of axial and radial load.

Technical result achieved in the implementation of the invention is to increase the carrier is sposobnosti support for known loads.

The technical result is achieved in that in the support of the vertical rotor comprising immersed in a lubricating fluid toroidal bearing surface, made at the end of the axle, mounted on a spherical bearing surface, made in the recess of the heel support, radius of the toroidal surface of the trunnion is 0.4÷0,95 on the radius of the spherical bearing surface of the thrust bearing, and the distance between the axial line of the toroidal surface and the axis of the trunnion is 0.05÷0.6 of the radius of the spherical bearing surface of the thrust bearing, the geometric parameters of the bearing satisfy the relation:

but not less than 1,

where r is the sphere radius of the thrust bearing, m;

ρ is the radius of the toroidal surface, m;

δ is the distance between the axial line of the toroidal surface and the axis of the trunnion, m;

P is the axial load, N;

F - radial load, N;

β - angle end of the pin from the axis of rotation under the action of radial load, pleased.

In addition, the depth of the spherical bearing surface of the thrust bearing is 0.7÷1,3 on the radius of the spherical bearing surface of the thrust bearing.

Additionally, the end surface of the trunnion is made flat.

In addition, the end surface of the trunnion is made spherical with a radius of the sphere, a large radius spherical reference surface is rnost thrust bearing.

Additionally on the toroidal surface of the trunnion is made grooves inclined to the axis of rotation in the direction of discharge of lubricant between the toroidal and spherical support surfaces.

In addition, the spherical bearing surface of the thrust bearing paired with a cylindrical or conical surface.

Additionally, the thrust bearing is made a channel for the passage of lubricating fluid located on the axis of rotation of the rotor.

In addition, the thrust bearing is made of one or more channels for the passage of lubricating fluid located at an angle to the axis of rotation of the rotor.

Additionally, the thrust bearing supports mounted on the damping element.

In addition, the thrust bearing made of synthetic sapphire or ruby.

The invention is illustrated by drawings.

Figure 1 shows a vertical section of the General form of a support with the damping element.

Figure 2 is given a vertical section of the journal and thrust bearing with the notation geometry bearings.

Figure 3 shows a vertical section of a variant of the geometry of the trunnion and heel.

Vertical rotor 1 with pin 2 mounted for rotation around a vertical axis 3, the thrust bearing 4 mounted on the damping element 5. The damping element 5 in the form of a cylinder mounted on the hinge 6 and the centering springs 7 in the housing cavity 8 is filled with the lubricating liquids is calling 9. At the end of the trunnion 2 is made of a toroidal bearing surface 10, immersed in a lubricating fluid 9 and supported on the spherical bearing surface 11 made in deepening thrust bearing 4. For the passage of lubricant to the bearing surfaces 10 and 11 in the thrust bearing 4 is made the channel 12 located on the axis of rotation 3, and channel 13 located at an angle to the axis of rotation 3. Toroidal bearing surface 10 is formed by rotation around the axis 3 of the arc of a circle of radius ρ with center offset from the axis 3 by the value of δ, and is based on the spherical bearing surface 11 of the thrust bearing 4 with the sphere radius r. Moreover, the radius ρ toroidal surface 10 of the trunnion 2 is 0.4÷0,95 on the value of the radius r of the spherical bearing surface 11 of the thrust bearing 4, so that is the ratio: ρ=(0,4÷0,95)r. The distance δ between the axial line of the toroidal surface 10 and the axle 3 axle 2 is 0.05÷0.6 of the radius r of the spherical bearing surface 11 of the thrust bearing 4, so that is the relationship: δ=(0,05÷0,6)r. To the trunnion 2 standards applied vertical load P and radial load F. Radial load causes the inclination of the trunnion end from the axis of rotation by the angle β.

The end surface 14 of the axle 2 in the variant of a support, shown in figure 2, is planar. The end surface 15 of the axle 2 in the variant of a support, shown in figure 3, are spherical with radio the ohms of the sphere R. Moreover, the radius R of the sphere 15 the radius r of the spherical bearing surface 11 of the thrust bearing 4, so that is the ratio: R>r.

On the toroidal surface 10 of the axle 2 has grooves 16, is inclined to the axis 3 of rotation of the rotor 1 in the direction of discharge of lubricant between 9 toroidal 10 11 and spherical bearing surfaces.

The depth h of the spherical bearing surface 11 of the thrust bearing 4 is 0.7÷1,3 on the value of the radius r of the spherical bearing surface 11, so is the ratio: h=(0,7÷1,3)r.

At a depth of h>r of the spherical bearing surface 11 is associated with the cylindrical surface 17 or conical surface 18 with a slight taper (shown in figure 3 by the dotted line).

The support works as follows.

In the absence of rotation of the rotor 1 to the end of the axle 2 with toroidal surface 10 is immersed in a lubricating fluid 9 and is mounted on a spherical bearing surface 11 of the thrust bearing 4. The contact stresses from axial load vertical rotor 1 is divided between the spherical bearing surface 11 and a toroidal surface 10 on the ring platform. The area of this site far exceeds the area of the contact spot on the surfaces of known supports, resulting in a maximum contact stress in the toroidal support is much less than in the leg not price the tym spherical surfaces. When the rotor 1 with a frequency of 800-1200 Hz and the effect of the axial load P is an increase in the temperature of lubricant on the contact surfaces between the toroidal surface 10 and the spherical bearing surface 11. Lower level distributed over a larger area of contact stresses creates a more uniform temperature distribution in the contact zone of the toroidal support, which reduces the maximum temperatures in the lubricating fluid and increases the efficiency of support. When the action on the support in addition to the axial load F and the radial load F the end of the axle 2 with toroidal surface 10 is rotated by the angle β. The rotation of the toroidal surface 10 relative to the axis 3 in an inclined position creates additional oil wedge between the incident edge toroidal surface 10 and the spherical surface 11 of the thrust bearing 4. If the geometric parameters of a support selected in accordance with a ratio of

,

the oil wedge creates a socket surface 14 or 15 of the trunnion 2 a hydrodynamic cushion that separates the toroidal surface 10 from the spherical surface 11 of the thrust bearing 4, which reduces wear and increases the efficiency of the reference pair.

The execution of the channels 12 and 13 in the thrust bearing 4 bearing provides for rotation of the rotor 1 duct more than the cold of lubricant in the contact zone with high temperature and further cooling support, and the grooves 16 on the toroidal surface 10 increases the rate of oil circulation through the contact zone, which reduces the wear of the bearings and increases its efficiency.

In addition, when performing thrust bearing 4 from sapphire or ruby in combination, for example, with steel toroidal surface 10 pin 2 base pair has a low coefficient of friction and less power friction and temperature in the support.

A pair of spherical bearing surface 11 at its increased depth with the cylindrical surface 17 or conical surface 18 serves to prevent the slipping of the end of the trunnion 2 of the thrust bearing 4 at large radial loads of interaction and unstable modes of the rotor, and the installation of the thrust bearing support on the damping element 5 further reduces the radial load.

Support design allows for producing a bearing surface of the journal and thrust bearing without their mutual lapping in the individual couple, which reduces the cost of manufacturing, and the independent setting items of the pair in the bearing during Assembly or replacement if repair reduces the cost of installation and operation.

1. Vertical rotor, comprising immersed in a lubricating fluid toroidal bearing surface, made at the end of the axle, mounted on a spherical bearing surface, done is nnow in deepening thrust bearing support, the radius of the toroidal surface of the trunnion is 0.4÷0.95 radius of the spherical bearing surface of the thrust bearing, and the distance between the axial line of the toroidal surface and the axis of the trunnion is 0.05÷0.6 radius of the spherical bearing surface of the thrust bearing, characterized in that the geometrical parameters of the supports meet the ratio
but not less than 1,
where r is the sphere radius of the thrust bearing, m;
ρ is the radius of the toroidal surface, m;
δ is the distance between the axial line of the toroidal surface and the axis of the trunnion, m;
P is the axial load, N;
F - radial load, N;
β - angle end of the pin from the axis of rotation under the action of radial load, pleased.

2. Bearing according to claim 1, characterized in that the depth of the spherical bearing surface of the thrust bearing is 0.7÷1.3 radius of the spherical bearing surface of the thrust bearing.

3. Bearing according to any one of claims 1 and 2, characterized in that the end surface of the trunnion is made flat.

4. Bearing according to any one of claims 1 and 2, characterized in that the end surface of the trunnion is made spherical with a radius of the sphere, a large radius spherical bearing surface of the thrust bearing.

5. Bearing according to any one of claims 1 and 2, characterized in that the toroidal surface of the trunnion is made grooves inclined to the axis of rotation in the direction of discharge, see the prevailing fluid between the toroidal surface and the reference surface, made in deepening thrust bearing.

6. Bearing according to claim 2, characterized in that the spherical bearing surface of the thrust bearing paired with a cylindrical or conical surface.

7. Bearing according to any one of claims 1 and 2, characterized in that the thrust bearing is made a channel for the passage of lubricating fluid located on the axis of rotation of the rotor.

8. Bearing according to any one of claims 1 and 2, characterized in that the thrust bearing is made of one or more channels for the passage of lubricating fluid located at an angle to the axis of rotation of the rotor.

9. Bearing according to any one of claims 1 and 2, characterized in that the thrust bearing supports mounted on the damping element.



 

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