JPS6220911A - Thrust bearing - Google Patents

Abstract

PURPOSE:To form a uniform liquid film made of a lubricant, by installing a core material in a ceramics disc having formed a spiral groove on both sides between a rotary shaft end part and the fixed side. CONSTITUTION:A rotary support plate 2 is locked to an end of a rotary shaft 1, while an outer surface of a bearing plate 3 or a ceramics disc is set up, in taction, in this rotary support plate 2, and a disclike fixed support plate 5 as a sliding surface member at the fixed side is set up, in taction, in the backside opposite to a surface touching the rotary support plate of the bearing plate 3. In the center of the said backside of the bearing plate 3 and the center of the surface opposed to the bearing plate 3 of the fixed support plate 5, there is provided with each of semispheric concave parts 4 and 6, and a small ball 7 as a core material is inset in these concave parts. Doing like this, the bearing plate is tiltable freely so that a uniform liquid film of a lubricant is formed in an accurate manner.

Description

DETAILED DESCRIPTION OF THE INVENTION [Object of the Invention] "Industrial Application Field" The present invention relates to a thrust bearing that is capable of forward and reverse rotation using dynamic pressure effects.

"Prior Art" Conventionally, for example, when driving a submersible pump or a submersible motor, the pump shaft may be rotated in the opposite direction due to a wiring error. In the case of a chamber shaft type pump, etc., a thrust load equal to the pump's own weight is applied to the bearing. In this case, it is necessary to use a thrust bearing that has a load capacity for reverse rotation.

As a thrust bearing that can rotate forward and backward, there is a floating type thrust bearing that uses tailing pads.

In addition, the latest proposal is the invention of a thrust bearing in Japanese Patent Application No. 1/311'f7. The invention provides a hard material having spiral grooves formed on the front surface in a direction that produces a dynamic pressure effect during forward rotation, and spiral grooves formed on the back surface in a direction that produces a hydrodynamic pressure effect during reverse rotation. A thrust bearing characterized in that an intermediate plate made of a material is interposed between opposing receiving plates, one of which rotates and the other of which is fixed, and the bearing does not move even when the rotating shaft is in the forward or reverse direction. Due to the pressure effect, the thrust load can be carried in the same way, and the bearing surface on the non-operating side generates suction force, which has the effect of strongly fixing the bearing, compared to the conventional floating type thrust bearing that uses tailing pads. It has the characteristics that the power loss is 3 minutes or less, the frictional loss heat is small, the temperature rise is small, and there is no need to particularly consider cooling.

``Problems to be Solved by the Invention'' A floating thrust bearing using a tailing pad has a large length in the axial direction, and when used in a mechanical device such as a submersible pump, the vertical length of the pump becomes large. Since a large amount of heat is generated on the sliding surface between the tailing pad and the thrust plate, sufficient cooling must be taken into consideration, and a large amount of liquid is required for both cooling and lubrication. There are many component parts, especially the manufacturing of the tailing pad, which requires a large number of man-hours and accounts for a large proportion of the cost of the thrust bearing.

The special request mentioned above! ;t-/J'14'7! The thrust bearing according to the above issue does not have the disadvantages of the floating type thrust bearing using the tailing pad 1, is inexpensive, has a short axial dimension, and has a small number of parts. And it has a much larger load capacity than a thrust bearing that uses a tailing pad, and is outside the bearing.

Although the diameter is also small, the intermediate plate (hereinafter referred to as a bearing plate) may move in the radial direction when the rotating shaft rotates forward or reverse. Therefore, it is necessary to fix a member close to the outer periphery of the bearing plate to prevent movement of the bearing plate so that the bearing plate does not shift. Therefore, if the bearing plate shifts during forward and reverse rotation, the outer periphery of the bearing plate will receive resistance, increasing bearing loss.
A problem arises in that the bearing does not operate in its normal position and sufficient dynamic pressure cannot be generated.

In addition, although the bearing plate of the prior invention has a member that prevents it from coming off in the radial direction, if it is used on a horizontal rotating shaft, the bearing plate will shift during non-operation, and the outer periphery of the bearing plate will prevent the bearing plate from radially moving away. It cannot be used in machines that have a horizontal rotating shaft because it rubs against a member that prevents movement.

The present invention relates to an improvement on the invention of the earlier application, and an object of the present invention is to provide a hydrodynamic thrust bearing that can perform forward and reverse operations without the bearing plate shifting.

[Structure of the invention]

"Means for Solving the Problem" The first invention of the present application provides a sliding surface perpendicular to the axis of a rotating side sliding surface member provided at the end of a rotating shaft, and a fixed side sliding surface opposite to this sliding surface. Between the sliding surface of the surface member and the sliding surface of the rotating side sliding surface member and the fixed side sliding surface member, a ceramic disk with spiral grooves formed in opposite directions on both sides when viewed from the respective surfaces is installed. A thrust bearing interposed so as to slide on a surface has a recess formed at the center of at least one or both surfaces of the ceramic disk, and has a sliding surface facing the surface of the ceramic disk with the recess. This is a thrust bearing in which a sliding surface member is provided with a recessed portion facing the recessed portion, and a core material is accommodated across both opposing recessed portions.

The second invention of the present application is a thrust bearing in which spiral grooves in opposite directions are provided on both surfaces of a ceramic disc when viewed from the respective surfaces, and both surfaces slide against a mating sliding surface. Between the sliding surface perpendicular to the axis of the rotating sliding surface member provided in A ceramic disc and a ceramic disc that rub on the fixed side sliding surface member are arranged respectively, and a single or multiple flat plate circle including both ceramic discs is placed between the rotating side and fixed side sliding surface member. Plates and ceramic discs are arranged alternately so as to rub against each other, and each ceramic disc and a sliding surface member, each ceramic disc and a flat plate, the entire opposing surface of the disc, or the opposing central part except for one opposing surface. This is a thrust bearing in which a recess is provided on both sides of the bearing, and a core material is accommodated across both opposing recesses.

"Function" The first invention of the present application uses ceramics disposed between the sliding surface member provided at the shaft end of the rotating shaft and the stationary side sliding surface member when the rotating shaft changes the direction of rotation without once stopping. A disc or a disc sandwiched between ceramic discs may be energized in the radial direction, but because each opposing recess contains a core material, the discs or discs sandwiched between ceramic discs or ceramic discs may not be biased in the radial direction. The disc always stays centered,
Also, a ceramic disk with concave portions on both sides can bear a certain amount of radial load.

The second invention of the present application is that even if seizing or damage occurs between a plurality of ceramic discs and a flat disc and resistance increases, the function of the thrust bearing is maintained by sliding between the other ceramic discs and the flat disc. In addition to the effect of maintaining this, it also exhibits the effect of the seventh invention of the present application, and the ceramic disk and flat plate are prevented from shifting in the radial direction.

"Example" Embodiments of the present invention will be described below with reference to the drawings.

FIG. 1 is a longitudinal sectional view of an embodiment of the invention. Axis of rotation! A disc-shaped rotating receiving plate is press-fitted to the end as a sliding surface member on the rotating side via a key/a, and the front surface of the bearing plate 3, which is a ceramic disc, is in contact with the rotating receiving plate. A disk-shaped fixed receiving plate S is disposed as a fixed-side sliding surface member on the back surface of the bearing plate J, which is opposite to the surface in contact with the rotating receiving plate. The center of the back surface of the bearing plate 3 and the fixed receiving plate! Each half is located at the center of the surface facing the bearing plate 3.

Spherical recesses II and A are provided, and a small ball 7 is fitted into the recesses II and A as a core material. Fixed receiving plate! bearing plate 3
A spherical concave seat t is provided at the center of the opposite surface to the surface in contact with,
The spherical concave seat 1 is in contact with the spherical surface of the tip of the adjusting screw screwed into the fixed member. Fixed receiving plate! A detent pin 10 fixed to an immovable part is loosely fitted into an axial hole on the outer periphery of the rotor.

This fixed receiving plate S functions as a leveling block and at the same time serves as a sliding surface member for the bearing plate J. When the bearing plate 3 and the fixed receiving plate S are in solid contact, there is a solid contact or a small gap between the small ball and the recessed part 6, so that the bearing plate 3 is not allowed to move in the radial direction.

As shown in the top plan view of FIG. 2, spiral grooves are provided on the front surface of the bearing plate 3 at equal intervals. The spiral grooves /l extend radially outward through the outer periphery of the bearing plate J, and do not exist in the center. A spiral groove //° similar to the spiral groove // is provided on the back surface of the bearing plate 3 (indicated by a dotted line in the figure).

The upper and lower spiral grooves //, //'' are twisted in opposite directions (FIG. 3 is a bottom view).

When viewed from the same side, the octopuses are in the same direction as shown in Figure 2.

Both sides of the bearing plate 3 are parallel to each other and have flat sliding surfaces /c, /c' with a flatness of less than lμ, and spiral grooves //,
The depth of //' is approximately 3 to 50 μm, respectively.

The spiral grooves //, //' and the recesses D and B are filled with a high viscosity lubricant such as grease. The viscosity of the lubricant used is the largest factor determining the depth of the spiral grooves // and //', and it also depends on the rotation speed. The depth is such that when a tensile force is applied in the axial direction to separate the bearing plate 3, rotating bearing plate 5, and fixed bearing plate 5, a large resistance force is exerted due to the vacuum pressure, and the viscosity of the lubricant is low. When the viscosity is large, the depth is chosen to be deep, and when the viscosity is low, the depth is chosen to be shallow. The width of the spiral groove //, l/' should be narrower in terms of bearing load capacity, but since the load capacity of this bearing is extremely large compared to a floating type thrust bearing that uses tailing pads, it is There are no restrictions.

The bearing plate 3 is made of a ceramic material such as silicon carbide (SiC),
Silicon nitride (stiN4) is used, and the rotating receiving plate 3 and the fixed receiving plate 3 are made of alumina ceramics, cemented carbide, stainless steel, high lead bronze, ordinary cast iron, or the same material as the bearing plate. The small spheres 7 are preferably made of a hard material with good thermal conductivity, and are preferably made of acicular crystals of β-8iC, which have a hard, dense body and are good conductors of heat. Alternatively, a high-strength Si3N4 dense body is also suitable.

Although the ceramic material used for the bearing plate 3 has excellent corrosion resistance, it has poor workability, so the surface has a thickness of 3 to 30 μm.
Although it is not easy to form extremely shallow spiral grooves of m in diameter, in the present invention, the surface of a ceramic workpiece of a predetermined shape is shielded with a spiral resin mask of a predetermined shape, and then fine powder is removed. Spiral grooves are formed in an extremely short time by a shot blasting method in which alumina abrasive material is sprayed onto the resin mask.

The above spiral-shaped resin mask is made by exposing and curing polyester-based liquid photosensitive resin with ultraviolet light.The manufacturing method is to first create a negative film with spiral grooves, and then place it on a glass plate. A transparent cover film is placed on top of this, and a photosensitive liquid resin is poured into it. Further, a base film is further laminated on top of this resin using a roll.

Next, the resin is exposed to ultraviolet light for a few seconds and passed through a negative film, and the exposed area of the resin hardens, creating a resin mask with spiral grooves in the same shape as the film.

The resin mask used for manufacturing the bearing plate 3 consists of a base film, an adhesive resin with a spiral groove pattern, and a protective paper. When performing shot processing, remove the protective paper, attach it to the surface of the workpiece, and remove one layer of the base film. The thickness of the bearing plate 3 is approximately -n, and the diameter is approximately as shown in the plan view 1.

When the rotating shaft / is rotated in the counterclockwise direction indicated by the arrow A in FIG. 2, the rotary receiving plate λ is rotated in the same direction. Since the lubricant between the rotating receiving plate and the front surface of the bearing plate 3 is energized in the direction of the same arrow, the lubricant in the spiral groove 11 generates dynamic pressure toward the center in the groove, and the bearing plate 3 sliding surface 12 and rotating receiving plate 2
Due to the dynamic pressure generated during this time, a liquid film is formed opposite the thrust load on the rotating shaft, and fluid lubrication is performed. Bearing plate 3
On the back side of the bearing plate 3 and the fixed receiving plate 3, the lubricant between the bearing plate 3 and the fixed receiving plate 3 tries to move radially due to the spiral grooves of the bearing plate 3. A vacuum pressure is created between the centers of (According to the discussion, the lubricant is forced outward but does not move) Bearing plate 3 is a fixed receiving plate! The liquid film becomes extremely thin as it is pulled against the object, and becomes in a fixed state.

Next, when the rotating shaft l is rotated from a stationary state in the opposite direction to the above in the direction of the arrow shown in Fig. 2, the rotating receiving plate 1 rotates clockwise, so that the lubricant between the rotating receiving plate 1 and the bearing plate 3 is spiraled. Vacuum pressure is generated as the vacuum pressure is removed toward the outer periphery by the groove //, and the rotary receiving plate 3 and the bearing plate 3 are attracted and fixed, and the bearing plate 3 rotates clockwise. When the bearing plate 3 rotates clockwise, the lubricant between the fixed receiving plate and the fixed receiving plate is moved toward the center by the spiral groove //', and dynamic pressure is generated between the bearing plate 3 and the fixed receiving plate 3. A liquid film is generated to resist the thrust load and provide fluid lubrication.

If you change the direction of rotation without stopping the rotating axis l,
Regardless of whether the first direction of rotation is the counterclockwise arrow A mentioned above or the second clockwise direction, a phenomenon is observed in which the bearing plate 3 tends to shift radially from the center during the process of changing the rotation direction. It will be done. This can be confirmed by the fact that, in FIG. 1, this may occur if the small ball 7 is removed and the rotating shaft l is rotated forward or backward without stopping.

The cause of this is that when the rotation direction changes from the direction of rotation indicated by arrow A to the direction of arrow A, the bearing plate 3 and the fixed receiving plate! While the adsorption force between the bearing plate 3 and the rotary receiving plate is not completely resolved, the adsorption force between the bearing plate 3 and the rotary receiving plate is incompletely generated.
In addition, it is thought that this is because not enough dynamic pressure is generated, so the centering effect due to the vortex flow of the lubricant due to the generation of dynamic pressure is small.
Also, when changing the direction of rotation from the direction of arrow A to the direction of rotation indicated by arrow A, the adhesion between the bearing plate 3 and the fixed support plate is not completed while the adhesion force between the bearing plate J and the rotating support plate is not completely released. This can be considered to be because the above-mentioned centering effect is small because it occurs completely and dynamic pressure is not generated sufficiently.

In the present invention, the bearing plate 3 and the fixed receiving plate 3 are provided with recesses D and 6, respectively, to accommodate small balls, so the bearing plate 3 is a fixed receiving plate!
remain concentric with the center of

A load experiment of the thrust bearing of the present invention will be described.

In an experiment, highly viscous grease, oil, etc. was applied between the bearing plate 3 and the rotating bearing plate 3, and between the bearing plate J and the fixed bearing plate 3, and a thrust load was applied and the forward and reverse rotation was repeated 10,000 times. However, it was found that there was no damage to the bearing surface and that the lubricating oil was not worn out at all.

When alumina ceramics were used for the rotating receiving plate 3 and the fixed receiving plate 3 in a test environment of 7000 rpm in tap water at room temperature, both forward and reverse rotations were j! ;
When the thrust load is 00 Kgf, J! OW (watt)
The only power loss was . It was confirmed that the bearing plate 3 did not rotate between the surfaces on the side where no dynamic pressure was generated. This means that when the spiral groove has a dynamic pressure effect, the friction coefficient is 0.
．． 003, whereas the coefficient of friction between the back surface and the opposing receiving plate at this time is around 0.7, and this is because there is a difference of about 700 times or more in rotational torque value between both surfaces.

Note that if the thrust load of the rotating shaft l is a negative value, that is, the bearing plate J
Even against a load in a direction that separates each receiving plate λ, 3, an adsorption force is generated and there is a resistance force, and the load in this direction can also be resisted.

FIG. 7 is a diagram comparing the power loss of a floating plate thrust bearing using a conventional tailing butt and a thrust bearing of the present invention, in which the rotating plate, fixed plate, and Board! Normal cast iron (FCCO2)
Power loss up to 100,100O0 (square mark in the figure) is shown when using a tailing pad bearing, which is conventionally used in underwater motors, etc. (triangle mark in the figure) is shown. The conventional bearing seizes at 100 Kff, and the power loss at this time is as large as 1λoovr, whereas the product of the present invention does not seize even under a high load of 10,000 to 4 f, and the power loss is extremely small at 2,101 kff.

Furthermore, when tested in a slurry liquid, the above performance was demonstrated, and the bearing plate 3 and each bearing plate,! No infiltration of slurry was observed between the two.

FIG. 3 shows the recesses at the center of the sliding surface member that slides against the bearing plate of the ceramic disk, and the shape of the core material accommodated in both recesses.

In FIG. 3(a), the core material is a small ball 7, the concave portion 6 is a conical hole. According to this embodiment, by selecting the diameter of the small ball, the concave portion is
It is easy to adjust the gap between 6 and the small ball.

In Fig. 3 (1)), the core material is a small ball, and the recess 11. A is small ball 7
It is a cylindrical hole with the same diameter as the sphere. In this embodiment, machining accuracy can be ensured by grinding the cylindrical hole.

Figures 1 (C) and 3 (d) are ellipsoids of rotation whose core material is an ellipsoid in cross section and whose center is the rotation axis l, and Figure 8 (C) is The concave portion 17. is short in the axial direction, and long in the axial direction in FIG. 8(d). A has a shape along the ellipsoids /A and /7, respectively.

In Fig. S (e), the core material is a cylinder/l, and the recess II, A has a cylindrical shape into which the same cylinder fits.

In the example, a highly viscous liquid was held between the bearing plate and each receiving plate, but if the bearing plate or receiving plate is made of a porous member, it will have wettability, so if it is impregnated with lubricant, the bearing plate should Even if the lubricant between the and the receiving plate runs out, restarting is easy and operation is possible.

In the embodiment, a high viscosity lubricant such as grease is held between the bearing plate and each receiving plate, so it can be used regardless of whether it is in the atmosphere or in liquid. The entire thrust bearing can be used in liquids, for example underwater.

In the embodiment, the recesses 1 and 6 are provided between the bearing plate and the fixed receiving plate, but a recess 1 at the center between the bearing plate and the rotating receiving plate may be provided, and the small ball may be fitted into this recess. In this case, if small balls are arranged on both sides of the bearing plate, a certain amount of radial load can be supported.

In the embodiment, the rotary receiving plate is attached to the rotating shaft/I, but it goes without saying that the rotating shaft/end may be used as a sliding surface member for the bearing plate (see the following second invention of the present application).

FIG. 6 is a longitudinal cross-sectional view showing a main part of an embodiment of the second invention of the present application. The end face of the rotation axis l is the rotation plane /! The rotating plane 15 and the bearing plate 3-/ are in contact with each other. The rotating plane corresponds to the sliding surface of the rotating receiving plate in the first embodiment. The bearing plate 3-/ is the same as the bearing plate 3 of the first embodiment. The fixed receiving plate is a circular plate with parallel surfaces on both sides, and is a fixed receiving plate! The relationships between -/ and the bearing plate, the surfaces 3-/, the small balls 7-/ and the recesses DA, 6, etc. are the same as those between the fixed receiving plate and the bearing plate 3 in the first embodiment. A bearing plate 3-co is in contact with the lower surface of the fixed receiving plate j'-/ via a small ball 7, and the lower surface of the bearing plate 3-= is a fixed receiving plate that also serves as a leveling block via a small ball 7! touches.

In this case, the twisting direction of the spiral groove is shown in Figure 2 when viewed from above in Figure 6 (hereinafter, the rotation direction in Figure 6 is shown in Figure 2).
bearing plate J-/ is in the same direction as bearing plate 3 (first invention), or bearing plate 3-. 2 can be used.

When the rotating shaft / rotates counterclockwise in FIG. 2, it usually slides on the rotating plane 13 of the rotating shaft / and the upper surface of the bearing plate 3-/, and moves toward the fixed receiving plate. 2. Fixed receiving plate! is stationary. (Taking inertia, static friction, and kinetic friction into account, the first result is as follows. When the rotating shaft / rotates in the opposite direction to the above, the rotating plane /3 and the upper surface of the bearing plate 3-/ are fixed by suction, and the bearing plate j-/ It slides and rotates between the fixed receiving plate !-/.

If the resistance force increases due to seizing between the bearing plate 3-/ and the rotating plane IS or damage to the sliding surface, the bearing plate 3-/ and the fixed receiving plate will be damaged when the rotating shaft rotates counterclockwise! Since the j-/ is fixed by suction, the fixed receiving plate j-7 acts as a rotating plate and rotates, and the space between the fixed receiving plate j-/ and the bearing plate 3-co acts as a sliding surface and rotates.

Similarly, bearing plate 3-/ and fixed bearing plate! - If the resistance increases due to seizing or damage to the sliding surface between
During the rotation, the rotating plane /3 of the rotating shaft l and the bearing plate 3-/ are fixed by suction, and the fixed receiving plate 5-/ is rotated clockwise and fixed by suction to the bearing plate 3-/, and the bearing plate 3-/ is fixed by suction. 1 rotates clockwise, dynamic pressure is generated between the bearing plate 3-= and the fixed receiving plate 5, and it acts as a thrust bearing.

As described above, this embodiment is suitable for thrust bearings that require a high degree of safety and reliability.

Expanding the technical concept of this embodiment, safety can be improved by alternately stacking small balls on the bearing plate and each receiving plate.

In addition, in such a thrust bearing in which the bearing plate and each receiving plate are stacked in multiple layers, blades or a shape equivalent to a blade are provided on the outer periphery of the bearing plate and the receiving plate so as to lower the relative rotation speed of each sliding surface. High speed rotation is possible by maintaining the relative rotation ratio.

In Fig. 6, the surface without small balls is the rotating plane and the bearing plate 3.
-7, but the number of opposing sliding surfaces not provided with small balls is limited to one location, but it may be between any sliding surfaces. Of course, if a small ball is provided between the rotating shaft/bearing 3-1 and one small ball is placed between all sliding surfaces, the radial load can be supported.

〔Effect of the invention〕

The first invention of the present application has a sliding surface perpendicular to the axis of a rotating sliding surface member provided at the end of a rotating shaft and a sliding surface of a fixed sliding surface member opposing the rotating shaft. In a thrust bearing in which a ceramic disk having spiral grooves formed in opposite directions when viewed from the surface side is interposed so as to slide on the sliding surfaces of a rotating side sliding surface member and a stationary side sliding surface member, the ceramic A recess is formed in the center of at least one surface or both surfaces of the disc, and a recess is provided opposite to the recess on a sliding surface member having a sliding surface facing the surface of the ceramic disc with the recess, A thrust bearing in which a core material is accommodated across both opposing recesses eliminates the phenomenon in which the bearing plate moves in the radial direction due to force 1, and can be used in forward and reverse directions, and can also be used in horizontal machines. When using small balls, the bearing plate can be tilted freely so that a precisely uniform film of lubricant is formed.

The small balls are made of dense ceramics with excellent wear resistance, and if the recesses and spiral grooves into which the small balls enter are coated with a highly viscous liquid, such as fluorinated oil with low vapor pressure, etc., the dry method can be used. Even in this state, the starting torque is small and it can be rotated. In addition, in this case, when dynamic pressure is generated, a film of highly viscous liquid is formed in the high pressure section, and when it is stopped, it stagnates in the spiral groove again, so consumption of the high viscous liquid is extremely small, making it practical to operate under dry conditions for a long period of time. can.

The second invention of the present application slides a ceramic disk and a flat disk in which spiral grooves are provided alternately between a rotating side sliding surface member and a stationary side sliding surface member, and all or part of each opposing sliding surface side is rubbed. Since recesses are provided in all but one of the centers and the core material is disposed across the opposing recesses, the ceramic disc and the flat disc do not deviate in the radial direction and can freely rotate in the forward and backward directions. Even if an increase in Iζ resistance or seizure occurs between the sliding surfaces of any of the ceramic discs and other flat discs, the other ceramic discs operate and function as a thrust bearing, increasing reliability.

Each embodiment has the same effect as the embodiment of the first invention of the present application.

[Brief explanation of drawings]

7 is a longitudinal sectional view of the embodiment of the first invention of the present application, FIG. 2 is a plan view of the bearing plate, FIG. 3 is a bottom view of the bearing plate, FIG. FIGS. 3(a) to 3(6) are longitudinal sectional views showing other embodiments of the recess and the core material, and FIG. 6 is a longitudinal sectional view showing essential parts of the embodiment of the second invention of the present application. l...Rotating shaft /a...Key K...Rotating receiving plate j,
j-/ , ,? -20・Bearing plate II, A・・Concavity! ,! -/,! --am fixed receiving plate? , 7-/ ,
Ku J @ m small ball! ... Spherical concave seat Ta... Adjustment screw 10... Stopping pin //, //'-
・Spiral groove /, 2. /Co2・Fist sliding surface/!・・・
Rotation plane /lh, /7...Ellipsoid. Figure 1 Figure 4 Suramato $T (k5f) Figure 8 (b)

Claims (1)

[Scope of Claims] 1. A sliding surface perpendicular to the axis of a rotating sliding surface member provided at the end of the rotating shaft, and a sliding surface of a stationary sliding surface member opposing this sliding surface. During this process, a ceramic disc having spiral grooves formed in opposite directions when viewed from the respective surfaces is slid onto the sliding surfaces of the rotating side sliding surface member and the stationary side sliding surface member. In the interposed thrust bearing, a recess is formed at the center of at least one surface or both surfaces of the ceramic disk, and the recess is formed in a sliding surface member having a sliding surface facing the surface of the ceramic disk with the recess. A recess is provided facing the
A thrust bearing that accommodates a core material across both opposing recesses. 2. The thrust bearing according to claim 1, wherein the core material is a small ball. 3. The thrust bearing according to claim 2, wherein the recess is semispherical. 4. The thrust bearing according to claim 2 or 3, wherein the small balls are made of a dense ceramic material. 5. Claim 2 or 3, in which a high viscosity liquid is preliminarily attached to the concave portion and the spiral groove portion into which the small sphere enters.
Thrust bearings listed in section. 6. Spiral grooves are provided on both sides of the ceramic disk in opposite directions when viewed from the respective surfaces, and are provided at the shaft end of the rotating shaft in a thrust bearing where both surfaces slide against the mating sliding surface. A ceramic disc is provided between the sliding surface of the rotating sliding surface member perpendicular to the axis and the sliding surface of the stationary sliding surface member opposing this sliding surface, which slides against both the rotating sliding members. A ceramic disc that slides on the sliding surface member on the rotating side and the fixed side is placed between the sliding surface member on the rotating side and the fixed side. The disks are arranged alternately so as to rub, and each ceramic disk and the sliding surface member, each ceramic disk and the entire opposing surface of the flat disk, or both sides of the opposing center except for one opposing surface. A thrust bearing in which a recess is provided and a core material is accommodated across both opposing recesses. 7. The thrust bearing according to claim 6, wherein the core material is a small ball. 8. The thrust bearing according to claim 7, wherein each recess has a hemispherical shape. 9. The thrust bearing according to claim 7 or 8, wherein the small balls are made of a dense ceramic material. 10. The thrust bearing according to claim 7 or 8, wherein the small balls are made of a dense ceramic material and are coated with a highly viscous fluid.