JPH0135557Y2 - - Google Patents

Description

[Detailed Description of the Invention] This invention relates to an improved structure of a bearing device for a vertical rotating machine.

It is common practice to directly connect a load such as a pump to the rotating shaft of a vertical rotating machine, such as a vertical electric motor. As a bearing device used in this case, one is conventionally known that is supported by a spherical rolling bearing that is inclined with respect to the rotating shaft and receives thrust load and radial load applied to the rotating shaft.

This type of bearing device can sufficiently support radial loads when the thrust load is large, but when there is no load, such as when testing in a factory, or when the load is light due to upthrust, etc. The rotor cannot support the radial load caused by the unbalanced rotor or the unbalanced magnetic attraction force, resulting in horizontal vibration of the rotating shaft, and if this becomes large, there is a risk that the rotor may come into contact with the stator.

This idea was made in order to eliminate the drawbacks of the conventional ones as described above, and the rotating shaft is supported by a disk of a simple structure that supports the radial load together with the spherical rolling bearing. .
An embodiment of this invention will be described below with reference to the drawings.

In Figures 1 to 4, reference numeral 1 denotes a spherical rolling bearing that pivotally supports the lower part of the boss part 3 that is integrated with the upper part of the rotating shaft 2 on the bracket 4 side, and ensures that both thrust load and radial load are supported when installing the load. The axial direction of the roller 1a is inclined with respect to the axial direction of the rotating shaft 2 so as to support the roller 1a. Reference numeral 5 denotes a ring for supporting a radial load, which is provided slightly below the rolling bearing 1, and is fixed to the support base 11 of the bearing.
4 is a bracket; 6 is an inner cylinder extending below the boss 3, having an outer diameter smaller than the boss 3 and coaxial with the rotating shaft 2; ing. Reference numeral 7 denotes oil passages provided in an odd number at equal pitches on the inner circumference of the ring 5.
is set equal to or slightly larger than the total area of 8 is a lubricating oil; 11 is a support table placed on the bracket 4 to support the spherical rolling bearing 1; and an oil passage 12 is provided at the bottom. The ring 5 is attached to the inner peripheral side of the support base 11 below the spherical rolling bearing 1, and is made of copper, for example.
When the downward thrust load applied to the bearing is light, it acts as a guide bearing that receives the radial load.

According to the bearing device configured as described above, the thrust load and radial load can be reliably supported by only the spherical rolling bearing 1 during load mounting operation, while the thrust load and radial load can be supported only by the spherical rolling bearing 1 during no-load or light-load operation. The load in the direction decreases and lateral vibration occurs, but since the ring 5 is provided on the outer periphery of the inner cylinder 6, this receives the radial load of the rotating shaft 2, preventing lateral vibration and floating due to the radial load. It can be restricted so as not to hinder the operation of the machine. An oil passage 7 is provided on the inner circumference of the annular ring 5 so that oil can flow at the required flow rate for lubrication and cooling of the rolling bearing 1. Since the lubricating oil flows from this part, the lubrication of the bearing 1 is maintained. There is no obstruction. FIG. 4 is an enlarged view of FIG. 2, and the reason why shaft vibration can be alleviated when there is an odd number of oil passages 7 on the circumference will be explained using this diagram. When the shaft 2 vibrates in the horizontal direction, the inner cylinder 6 also vibrates. Now, for example, when the inner cylinder 6 moves in the direction of arrow A, the inner cylinder 6
The oil film 13 between the ring 5 and the ring 5 is compressed and becomes high pressure, and the high pressure oil film exerts a restoring force to push the inner cylinder 6 back in the opposite direction (direction of arrow B).
If there is an even number of oil passages 7 on the circumference, there will be an oil film on the opposite side, so the above action will be repeated.
The vibration of shaft 2 is sustained. However, in the configuration of the present invention, since there is an odd number of oil passages 7, the oil passages 7 are on the opposite side of the oil film, and when the inner cylinder 6 is pushed back, the repulsive force does not work again, so that the shaft 2 The vibrations will attenuate. Therefore, the lateral vibration of the shaft can be reduced compared to a structure in which the oil passages 7 are provided symmetrically in an even number of locations. The inner periphery of the ring 5 can be circumferential, but in this case, in order to obtain a sufficient flow of oil to cool the bearing 1, the gap between the ring 5 and the ring 5 must be made large. The horizontal vibration of the shaft increases in proportion to the gap, which is unfavorable for operation. In this invention, the horizontal vibration of the shaft 2 is minimized, and a sufficient amount of cooling oil for the bearing 1 can be obtained.

As described above, according to this invention, by providing the ring, the rotating shaft can be rotated smoothly and smoothly even when there is no load or a light load; It can be provided at low cost because it can have a simple structure that restricts movement.

[Brief explanation of the drawing]

Fig. 1 is a sectional side view showing an embodiment of this invention, Fig. 2 is a sectional view taken along the - line in Fig. 1, and Fig. 3 is an enlarged view of the main part of the spherical roller bearing portion in Fig. 1. The cross-sectional side view, FIG. 4, is an enlarged view of FIG. 2, and is a diagram for explaining the damping effect of shaft runout. In the figure, 1 is a spherical rolling bearing, 1a is a roller,
2 is a rotating shaft, 3 is a boss portion, 4 is a bracket, 5 is an annular ring, 6 is an inner cylinder, 7 is an oil passage, 8 is a lubricating oil, 9 is a retainer, and 10 is a lubricating oil passage hole.

Claims (1)

[Scope of utility model registration request] A boss part 3 is fixed integrally around the rotating shaft 2 of a vertical rotary machine that directly connects the load to the rotating shaft 2, and a boss part 3 is integrally attached to the lower part of the boss part 3 and has an outer diameter smaller than that of the boss part 3 and an inner diameter above the above. An inner cylinder 6, which is sufficiently larger than the rotating shaft, is provided coaxially with the rotating shaft 2, and the lower end of the boss portion 3 is pivotally supported by a spherical rolling bearing 1 that receives thrust load and radial load when loaded. In this example, annular rings 5 for receiving radial loads with oil passages 7 provided in the axial direction at odd-numbered locations on the circumference are opposed,
The ring 5 is fixedly disposed on the bracket 4, and the spherical rolling bearing 1 is further provided with a retainer 9 having a lubricating oil passage hole 10 which serves as an oil supply passage to the oil passage 7. A bearing device for a vertical rotating machine characterized by: