JPS6231205B2 - - Google Patents

Description

Detailed Description of the Invention (Field of Industrial Application) The present invention consists of two bearing members, one of which faces the rotor with a smooth surface across a bearing gap, The present invention relates to a sliding bearing in which a liquid is forcibly supplied to a gap, in which case an increase in the pressure of the lubricating medium occurs due to the relative rotational movement between the rotor and one of the bearing members.

(Prior Art) Sliding bearings are known which are provided with sliding surfaces formed as rotating surfaces and between which a film is held hydrostatically or hydrodynamically. In this case, all bearings according to the prior art with grooves on the inside of the bearing part facing the rotor, so-called annular groove bearings, are lubricated with oil or grease.
Hydrodynamic bearings must be manufactured for use with low viscosity liquids or gases. However, the present invention is directed to hydrodynamic bearings which do not have grooves on the inner surface of the bearing member facing the rotor. Each hydrodynamic bearing is theoretically designed for each lubricating medium. However, in practice, the design is difficult in principle. This is because the lubrication gap, which is the spacing between the sliding members, is also reduced when the viscosity is low. In practice, if the absolute value of the gap becomes small, economically substitutable finishes are not possible because the dimensional differences between the sliding members are small. If, on the other hand, the dimensional differences between the sliding members become too large due to temperature changes even with minimal temperature changes, the bearing gap will exceed the size required for the generation of a hydrodynamic retaining film.

When manufacturing water-lubricated bearings, the viscosity coefficient of water is approximately 100.
The viscosity coefficient of hot water is 1/3 of that, which is smaller than that of oil. Therefore, in water-lubricated bearings, the bearing clearance must be 1 to 2 μm. Although such accuracy can theoretically be obtained by precision machining, in practice the manufacturing cost is uneconomical. Moreover, such a bearing produced with the highest machining accuracy cannot be used in practice, since the two bearing parts are heated during operation and expand according to different expansion coefficients. Even if the difference in expansion coefficients is minimal, the two bearing members will have a bearing clearance of between 10 and 100 microns. High-load water-lubricated bearings with rigid bearing members are therefore only practical if operated at constant temperatures.

The present invention is directed to a sliding bearing in which the bearing member automatically follows the rotor and maintains a uniform bearing clearance even if the bearing member has certain machining tolerances and thermal expansion occurs during operation. It is possible,
By maintaining a uniform bearing clearance, it is possible to lubricate the bearing with a lubricating medium of low viscosity even when a large load is applied.

The present invention provides an elastically deformable bearing member that at least partially defines a cavity on the opposite side of the bearing gap, and that pressure is maintained in the cavity and that pressure causes the elastically deformable bearing member to hydroelastically This problem is solved by pressing the bearing against the bearing part of the bearing, and pressing it hydrodynamically using the high pressure generated at the pole part during rotation. That is, according to the invention, a pressure is generated on the side of the elastically deformable bearing member opposite the bearing gap that presses the bearing member against another rigid bearing part.

The sliding bearing according to the present invention has a
The bearing member may be formed of any rotational surface that is rotationally symmetrical with respect to the rotational axis of the rotor that receives the load. This surface of rotation can be a plane, a cylindrical surface, a spherical surface or a conical surface. All these surfaces, together with an elastically deformable bearing member which can be a flat, cylindrical or conical surface, are likewise rotationally symmetrical with respect to the axis of rotation of the rotor, delimiting a cavity and creating a corresponding pressure in the cavity. is maintained, and the elastic deformation guarantees the narrow bearing clearance necessary for preserving the hydrodynamic feeding effect of the lubricating medium.

In this case, it does not matter whether the elastically deformable bearing member forms a concave bearing surface or a convex bearing surface but is flat.

The present invention further aims to: That is to say that the surfaces of the bearing parts which are in contact with the rotor via the lubricant during operation are made of very hard materials and have an advantageous sliding effect, so that during operation
The materials do not weld or corrode to each other while the retaining lubricating film is not formed. It is particularly suitable that the electrolytically produced layer is of gold or platinum metal or of a corrosion-resistant zinc-noble metal; during processing very hard powders, in particular tungsten carbide, silicon carbide, etc. are added to the electrolytic layer. , titanium carbide, or boron carbide.

The present invention will be explained based on the drawings.

FIG. 1 schematically shows an arrangement in which a concave elastic bearing element, designed as an elastically deformable bearing element, consists of an annular wall 41, which together form a wall 40 and a weld seam 43. Welded to a hollow ring along 43', the cavity 46 is filled with a material of low volume change, in particular a highly viscous liquid. A pressure is built up in the cavity 45 leading to the bearing gap, which deforms the wall 40 to the condition 40', whereby the concave ring wall 41 is hydraulically pressed against the surface of the ball 42. Pressed.

FIG. 2 schematically shows an embodiment in which the concave bearing part formed as an elastically deformable bearing part consists of two mutually fitted annular parts 51 and 53, which annular parts are bounded by a boundary. They are welded together at 54. In order to achieve as uniform a formation as possible, an annular member 55 is further incorporated, and this annular member is connected to the elastic bearing members 51 and 5 through a packing 56.
This prevents liquid from entering the gap between the holes 5 and 5. Hole 5
The vacant room 59 communicates with the vacant room 57 through 8.

FIG. 3 schematically shows an embodiment in which the concave bearing part 61, which is designed as an elastically deformable bearing element, is spring-shaped at the pole part 63. The wall 64 is designed as a corrugated membrane, so that the membrane 61 and the bearing part 6
The pressure built up between the poles 63 can be propagated to the liquid in the sealed cavity 65.

FIG. 4 diagrammatically shows a conical bearing consisting of a shaft neck 72 and a bearing bush 71 designed as an elastically deformable bearing member. The wall thickness of the bearing bushing is formed to be thinner at the small diameter portion 74 than at the peripheral edge portion 75. Due to the high pressure created in the poles, the diaphragm wall 76 transmits the overpressure built up in the chamber 70 to the sealed liquid in the cavity 77.
The deformation of the wall 76 thereby causes the bearing bush 71 to flex slightly radially inward, reducing the bearing clearance. The axle neck 72 rests on the sliding ring 78 in the rest state, while in operation it is raised due to a slight expansion of the wall.

Each of the bearings shown in FIGS. 1 to 4 has an advantageous effect as a hydrodynamic bearing due to the small bearing gap.

[Brief explanation of the drawing]

1 to 3 show schematic sectional views of various plain bearings with spherical sliding surfaces according to the invention, and FIG. 4 shows a schematic sectional view of a sliding bearing with conical sliding surfaces according to the invention. . 40, 40'... Wall portion, 41... Elastic bearing member, 42... Ball (rotor), 46... Vacant room, 47
... Stator, 51 ... Elastic bearing member, 53 ...
Stator, 56...Packing, 57...Vacant room,
61...Elastic bearing member, 64...Wall portion, 65...
Empty chamber, 66...Stator, 71...Elastic bearing member, 72...Rotor neck, 76...Wall portion, 77
...Vacant room, 79...Stator.

Claims (1)

[Claims] 1. Consisting of two bearing members, one bearing member and the rotor face each other with a smooth surface across a bearing gap, and a liquid is forcibly supplied to the bearing gap, In a sliding bearing in which the pressure of the lubricating medium increases due to relative rotational movement between the upper rotor and one bearing member, (a) one of the bearing members 41, 51, 61, 71 is formed to be elastically deformable; (b) ) These elastic bearing members 41, 51, 61, 71 are the other bearing member 47 as an inelastic bearing member,
(c) A space filled with liquid is formed between the elastic bearing members 41, 51, 61, 71 and the inelastic bearing members 47, 53, 66, 79. Chambers 46, 57, 65, 77 are formed; (d) walls 40, 6 which are near the rotational axis of the bearing and are elastically deformable in the plane of rotation about the rotational axis;
4, 76 are provided, so that in addition to static pressure, dynamic pressure occurring in the lubricating medium can be propagated to the liquid in the cavities 46, 57, 65, 77 via the elastic bearing member, A sliding bearing characterized in that the elastic bearing members 41, 51, 61, 71 are thereby pushed up toward the inelastic bearing members 47, 53, 66, 79.