JPH04248015A - Automatic alignment mechanism for spirally grooved thrust bearing - Google Patents

Abstract

PURPOSE:To absorb the deviation of the right angle of a spirally grooved thrust bearing. CONSTITUTION:A slight disc 1 and a slight plate 4 are formed in thick annular rings. An elastic plate 5 as an elastic support is laid between the approximately middle portion in a radial direction of the slight plate and the axial hole peripheral portion of a mainframe, slight collars 3, 3 on the upper and lower faces of which several spiral grooves are engraved are arranged in contact with the upper and lower faces of the slight disc and the slight disc is locked with elastic sleeves 2, 2.

Description

[Detailed description of the invention]

0001

[Industrial Application Field] The present invention is a self-aligning spiral groove type thrust bearing in which a thrust plate on the stationary side is provided on both sides of a thrust disk on the rotating side via thrust collars with spiral grooves carved on both sides. Regarding the mechanism.

0002

2. Description of the Related Art Such spiral groove type thrust bearings have a large load capacity per unit area and are suitable for submersible pumps with limited outer diameter dimensions.

0003

[Problems to be Solved by the Invention] However, in this type of bearing, it is necessary to maintain good flatness of the wide sliding surface of the thrust disk, and to ensure that the clearance on the sliding surface is at least the minimum oil film thickness even in small areas. There is.

[0004] This thrust disk minimizes errors in machining accuracy, assembly accuracy, or errors that occur during operation, keeps the sliding surface flat, and keeps the surface facing the sliding surface flat. The appropriate clearance mentioned above must be secured by following the above.

[0005] On the other hand, it is conceivable to form the thrust disk into a spherical seat, but this is insufficient to meet the requirements for flatness accuracy on the order of microns. In bearings, the shape of the spherical seat becomes large, making it difficult to maintain a wide seating surface with high precision.

The present invention maintains the flat state of a highly rigid thrust disk machined with high precision in as good a state as possible from the assembled state to the operating state, that is, the thrust action state, and also prevents deviations in perpendicularity. The purpose of this invention is to provide a self-aligning mechanism for a spiral groove type thrust bearing that can absorb the

[0007]

[Means for Solving the Problems] According to the present invention, a spiral groove type thrust bearing is provided in which a thrust plate on the stationary side is provided on both sides of a thrust disk on the rotating side via thrust collars in which spiral grooves are carved on both sides. The thrust disk and the thrust plate are formed into a thick toric body, and an elastic support is interposed between the substantially middle portion of the thrust plate in the radial direction and the peripheral edge of the shaft hole of the main body, and the thrust disk is secured with an elastic sleeve.

[0008] It is preferable that the elastic support member is constituted by an elastic plate whose protrusions abut respective protrusions formed at a substantially intermediate portion in the radial direction of the thrust plate and at a peripheral portion of the shaft hole of the main body.

Further, it is preferable that both sides of the inner circumferential edge of the thrust disk be supported by elastic sleeves that are easily compressed and deformed, so that surface runout during rotation of the disk can be easily absorbed.

0010

[Operation] In the self-aligning mechanism of the spiral groove type thrust bearing configured as above, when surface runout occurs in the thrust disk, a high hydraulic pressure higher than normal is generated on the surface runout side of the thrust collar, and the opposing The side oil pressure will be lower than normal. This difference in oil pressure acts on the thrust disk, but makes it easier to deform the elastic sleeve that supports the thrust disk, thereby preventing the thrust disk itself from deforming and forming a uniform gap (uniform oil film thickness).

Further, the elastic plate supports the thrust plate at a substantially intermediate portion in the radial direction where it is difficult to warp and deform, and further,
Surface runout is absorbed by being supported at approximately the middle portion in the radial direction where the sliding surface gap is less likely to become uneven.

0012

DESCRIPTION OF THE PREFERRED EMBODIMENTS Examples of the present invention will be described below with reference to the drawings.

In FIG. 1, a sleeve 13 is locked to the pump shaft 10 in the axial direction by a pair of split rings 11 and an adjustment ring 12, and in the rotational direction by a key 14. The thrust disk 1 is locked in the sleeve 13 in the rotational direction by a key 15.
Elastic sleeves 2, 2, which are easily compressible and deformed on both sides of the inner edges, are provided, and the elastic sleeves 2, 2 are axially locked by a nut 16 screwed onto the sleeve 13. Note that the reference numeral 17 in the drawings is an oil passage formed between the pump shaft 10 and the sleeve 13, and 18 and 19 are oil holes that communicate the oil passage 17 with the outside.

The disk 1 is formed into a thick toric body with high rigidity, and thrust collars 3, 3 are provided in contact with the upper and lower surfaces (the left side is the upper side in the drawing), respectively. A plurality of spiral grooves 3a are formed on the upper and lower surfaces of the thrust collar 3 by a known technique as shown in FIG. 2, respectively.

A thrust plate 4 is provided in contact with the thrust collar 3, and the thrust plate 4 is formed into a thick toric body with high rigidity, and has a dowel pin 9,
It is locked in the rotational direction by 9a.

An annular protrusion 4a is formed approximately in the middle of the thrust plate 4 in the radial direction, and an annular protrusion 20a is similarly formed at the periphery of the shaft hole of the main body 20. An elastic plate 5 serving as an elastic support is interposed between the main body 20 and the thrust plate 4, and its annular protrusions 6 and 7 are in contact with the protrusions 4a and 20a, respectively. The elasticity of the elastic plate 5 is such that it can withstand an internal pressure of, for example, several tens of kg/cm<2> generated in response to a thrust load.

The thrust collar 3 constructed in this manner is in a floating state during rotation, and is in a state in which it is lightly stuck to the thrust plate 4. On the other hand, during rotation, lubricating oil circulates as shown by the arrow, and as shown in Figure 3, high oil pressure is generated between the surfaces of the thrust disk 1 and the peak is slightly closer to the inner circumference than the radial middle. A is generated, and a gap of, for example, about 10 microns is formed. When, for example, an upward thrust load acts on the pump shaft 10, both surfaces of the upper thrust collar 3 and the thrust disk 1 become sliding surfaces C1, and the lower thrust collar 3
The sliding surface C2 between the thrust disk 1 and the thrust disk 1 becomes a free surface. As shown in FIG. 3, the elastic plate 5 presses the thrust plate 4 with a reaction force B corresponding to the thrust load. Then, the surface runout of the thrust plate 4 due to the surface runout of the thrust plate 4 at an angle α or the surface runout of the thrust disk 1 is calculated as follows:
As shown in the figure, it is elastically deformed and absorbed, and the thrust plate is always supported by reaction force B.

In addition, as shown in FIG. 4, if there is misalignment between the thrust disk surface and the thrust collar surface, a hydraulic pressure A1 higher than the high hydraulic pressure A is generated on the small gap side due to the action of the spiral groove 3a, and the high pressure A1 is generated on the large gap side. A hydraulic pressure A2 lower than the high hydraulic pressure A is generated. This pressure acts on the thrust disk 1, but if the thrust disk 1 is rigidly supported, the surface of the thrust disk will be deformed as shown in FIG. On the other hand, if the thrust disk is elastically supported via an elastic sleeve, deformation of the thrust disk can be prevented as shown in FIG. 5, and a uniform gap (uniform oil film thickness) can be easily formed.

[0019]

[Effects of the Invention] Since the present invention is constructed as described above, the rigidity of the thrust disk and thrust plate is increased to prevent deformation from occurring, and furthermore, they are supported by a deformable elastic plate and an elastic sleeve. It is possible to absorb surface runout and maintain a good surface condition. Therefore, the axis can be automatically aligned, and the load capacity against the thrust load can be brought closer to the theoretical solution where the gap is constant and the load capacity is the highest.

[Brief explanation of the drawing]

FIG. 1 is a side sectional view showing one embodiment of the present invention.

FIG. 2 is a front view of the thrust collar.

FIG. 3 is a diagram illustrating the surface runout absorption state of the thrust plate.

FIG. 4 is an explanatory diagram showing surface runout when there is no elastic sleeve.

FIG. 5 is an explanatory diagram showing surface runout when an elastic sleeve is used.

[Explanation of symbols]

1... Thrust disk 2...Elastic sleeve 3...Thrust color 3a...Spiral groove 4...Thrust plate 4a... protrusion 5...Elastic plate 10...Pump shaft 13...Sleeve 16...Nut 17, 18, 19...Oil road 20...Main body

Claims (1)

[Claims] 1. A spiral groove type thrust bearing in which a stationary side thrust plate is provided on both sides of a rotating side thrust disk through thrust collars having spiral grooves carved on both sides, and the thrust disk and the thrust plate are thick. It is characterized in that it is formed into a toric body, an elastic support body is interposed between the approximately middle part of the thrust plate in the radial direction and the peripheral part of the shaft hole of the main body, and the thrust disk is locked with an elastic sleeve. Self-aligning mechanism for spiral groove type thrust bearings.