JPH0312971Y2 - - Google Patents

Description

[Detailed description of the invention] This invention relates to a hydrodynamic sliding bearing, in particular, the shaft body and the bearing are relatively capable of rotational movement in forward and reverse directions, linear movement, or rotational linear movement, Dynamic pressure is generated in both forward and reverse directions by disposing arrowhead-shaped grooves for generating dynamic pressure connected facing each other in a diamond shape on at least one sliding surface of the shaft body and the bearing.

Conventional dynamic pressure type radial sliding bearings have an arrowhead-shaped groove for generating dynamic pressure on the sliding surface of the bearing, and the shaft body rotates in one direction relative to the bearing, but cannot rotate in the forward or reverse direction. Also, it cannot perform linear motion or rotational linear motion.

The purpose of this invention is to provide a hydrodynamic sliding bearing that can move in both forward and reverse directions.

That is, in this invention, as in the illustrated embodiment, the shaft body 10 and the bearings 20, 30, 40, 50 can rotate in forward and reverse directions, linearly move, or rotate linearly through their mutual sliding surfaces. The sliding surfaces 11, 21, 12, 3 are relatively movable.
1, 13, 41, 14, and 51 are formed with arrowhead-shaped grooves 60 and 70 for generating dynamic pressure.
0 and the bearings 20, 30, 40, 50, a groove 60 corresponding to one direction of movement, and a groove 70 whose arrowhead direction corresponds to the other direction of movement are connected facing each other in a diamond shape, respectively. sliding surface 11,
Grooves 60 arranged in 21, 12, 31, 13, 41, 14, 51, the arrowhead direction of which coincides with one direction of movement and the grooves 70 whose arrowhead direction corresponds with the other direction of movement, are as follows:
The present invention relates to a hydrodynamic sliding bearing characterized in that both of the bearings are located at two or more locations in the direction of motion, and at two or more locations in a direction perpendicular to the direction of motion.

Examples of this invention will be described below with reference to the drawings.

FIG. 1 shows an embodiment in which this invention is applied to a radial sliding bearing. In the same figure a, the number 10
20 represents a shaft body, and 20 represents a radial plain bearing. The radial outer surface 11 of the shaft body 10 and the radial inner surface 21 of the radial plain bearing 20 each form a sliding surface, and the shaft body 10 is It is supported by and rotates in both forward and reverse directions. As shown in Figure b, the radial inner surface 21 of the radial sliding bearing 20 is connected with a groove 60 facing downward and a groove 70 facing upward in a rhombic shape, and connecting this rhombic groove. They are arranged at approximately the same intervals in the circumferential direction and at appropriate intervals in the axial direction. Also,
Small diamond-shaped grooves 60a, 70a are provided inside the diamond-shaped grooves 60, 70 for generating dynamic pressure. The depth of these grooves is several μm ~
Appropriate selection is made within the range of several tens of micrometers.

In the bearing with the above configuration, using any one of oil, grease, air, etc. as a lubricant,
When the shaft body 10 rotates in the direction A, the downward grooves 60, 60 whose arrowhead direction coincides with the rotation direction A
Dynamic pressure is generated by the pumping action of a, the pressure at the tip increases, and the lubricant flows into the bearing gap 15 between the radial outer surface 11 and the radial inner surface 21, forming a fluid film and reducing the radial load. To support. Furthermore, when the shaft body 10 rotates in the direction B, which is opposite to the direction A, a pumping action is generated by the radially upward grooves 70, 70a whose arrow tips coincide with the rotation direction B, and the grooves 70,
Due to the lubricant flowing out from the point of arrow 70a,
A fluid film is formed in the bearing gap 15.

The above grooves for generating dynamic pressure 60, 70, 60a,
A plurality of 70a are provided at appropriate intervals in the axial direction, so that the same dynamic pressure is generated at each position in the axial direction even if the shaft body 10 rotates in either the forward or reverse direction. , this groove 60, 70, 60a, 7
0a is at least 3 at both ends and the middle part in the axial direction
It may be provided in the circumferential direction at different locations so that equal dynamic pressure is generated at at least three locations in the axial direction.

In addition, grooves 60, 70, 60a for generating dynamic pressure,
70a may be provided on the radial outer surface 11 of the shaft body 10 instead of on the radial inner surface 21 of the radial plain bearing 20 as in the above embodiment, and furthermore, it may be provided on both the radial inner surface 21 and the radial outer surface 11.

In the above embodiment, a case has been described in which the shaft body 10 rotates in forward and reverse directions, but the present invention can be similarly applied to a case in which the radial sliding bearing 20 rotates in forward and reverse directions.

FIG. 2 shows an example in which this invention is applied to a linear sliding bearing. In the same figure a, the shaft body 10
A cylindrical or planar linear outer surface 12 provided on the
is supported by a cylindrical or planar linear inner surface 31 provided in a linear slide bearing 30, and makes reciprocating linear movement in the axial direction. Figure b shows arrowhead-shaped grooves 60 and 70 for generating dynamic pressure formed on the linear inner surface 31 of the linear plain bearing 30, with the arrowheads pointing to the right in the axial direction, a groove 60, and a groove 7 pointing to the left in the axial direction.
0 are connected in a diamond shape and arranged at approximately the same intervals in the axial direction and at appropriate intervals in the circumferential direction or in the direction perpendicular to the axial direction.

In the bearing configured as described above, when the shaft body 10 moves linearly in the direction C, dynamic pressure is generated due to the pumping action of the groove 60 facing right in the axial direction whose arrow head direction coincides with the movement direction C, and the pressure at the arrow head portion is increased. The shaft 10 is supported by a fluid film of lubricant flowing into the bearing gap 15 between the linear outer surface 12 and the linear inner surface 31. When the shaft body 10 moves linearly in the D direction opposite to the C direction, the groove 70 is directed to the left in the axial direction and the direction of the arrow coincides with the movement direction D.
Pumping action occurs and this groove 70
A fluid film is formed by the lubricant flowing out into the bearing gap 15 from the point of the arrow.

Grooves 60, 7 for generating dynamic pressure in the above bearing
0 are provided in three rows at both ends and in the middle in the axial direction, so even if the shaft body 10 moves linearly in either the forward or reverse direction, equal large dynamic pressure is generated at at least three locations in the axial direction. do.

In this embodiment as well, the groove 6 for generating dynamic pressure
0 and 70 may be provided on the linear outer surface 12 of the shaft body 10, and the linear inner surface 31 and the linear outer surface 12
It may be provided on both sliding surfaces.

Further, the present invention can be similarly applied to a case where the shaft body 10 is fixed and the linear slide bearing 30 moves linearly in a reciprocating manner.

FIG. 3 shows an embodiment in which this invention is applied to a radial linear sliding bearing. In Figure a, the radial linear outer surface 13 of the shaft body 10 is supported by the radial linear inner surface 41 of the radial linear sliding bearing 40 and reciprocates in a spiral manner. Figure b shows arrowhead-shaped grooves 60 and 70 for generating dynamic pressure formed on the radial linear inner surface 41 of the radial linear plain bearing 40, with the downward groove 60 and the arrowhead direction being located in the lead angle θ direction. Connect the upward groove 70 in a diamond shape,
They are arranged in four rows in the axial direction parallel to the lead angle θ direction.

In the bearing configured as described above, if the direction of movement of the shaft body 10 is the E direction, dynamic pressure is generated due to the pumping action of the downward groove 60 in the lead angle θ direction whose arrow head direction coincides with this movement direction. The pressure increases and the radial/linear outer surface 13
The fluid film of the lubricant flowing into the bearing gap 15 between the shaft body 1
Support 0. On the contrary, if the direction of movement of the shaft body 10 is the direction F, then the direction of the arrow is the direction of movement F.
A pumping action is generated by the upward groove 70 in the direction of the lead angle θ, which coincides with the angle θ, and a fluid film is formed by the lubricant flowing out from the tip of the groove 70 into the bearing gap 15.

Grooves 60, 7 for generating dynamic pressure in the above bearing
0 are provided in four rows at the front end and in the middle in the lead angle θ direction, so that even if the shaft body 10 moves in the forward or reverse direction, equal large dynamic pressure is generated at at least three locations in the axial direction. do.

In this embodiment as well, the groove 6 for generating dynamic pressure
0,70 may be provided on the radial linear outer surface 13 of the shaft body 10, and may be provided on the radial linear inner surface 4
1 and the radial/linear outer surface 13 may be provided on both sliding surfaces.

Further, the present invention can be similarly applied to a case where the shaft body 10 is fixed and the radial linear slide bearing 40 reciprocates in a spiral manner.

FIG. 4 shows an embodiment in which this invention is applied to a thrust slide bearing. In the same figure a, the shaft body 10
The thrust end face 14 of the thrust bearing is supported in the axial direction by the thrust bearing face 51 of the thrust sliding bearing and rotates in both forward and reverse directions. Figure b shows arrowhead-shaped grooves 60 and 70 for generating dynamic pressure formed on the thrust bearing surface of the thrust sliding bearing 50, with the arrowheads pointing downward in the circumferential direction of the groove 60 and grooves 70 pointing upward in the circumferential direction. 3 in the radial direction connected in a diamond shape
They are arranged in columns.

In the bearing with the above configuration, when the shaft body rotates in the G direction, dynamic pressure is generated due to the pumping action of the groove 60 facing downward in the circumferential direction whose arrow head direction coincides with this rotation direction, and the pressure at the arrow head portion increases. The thrust load is supported by a fluid film of lubricant flowing into the bearing gap 15 between the thrust end face 14 and the thrust bearing surface 51. When the shaft body 10 rotates in the H direction, a pumping action is generated by the groove 70 facing upward in the circumferential direction whose arrow head direction coincides with the rotation direction H, and the lubricant flows out from the arrow head portion of the groove 70 into the bearing gap 15. A fluid film is formed by In either case, equal large dynamic pressures are generated at three locations in the radial direction of the sliding surface.

In this embodiment as well, the groove 60 for generating dynamic pressure,
70 may be provided on the thrust end surface 14 of the thrust receiver, or may be provided on the thrust receiving surface 51 and the thrust end surface 1.
4 may be provided on both sliding surfaces.

Alternatively, the shaft body 10 can be used as the stationary side and the thrust slide bearing 50 can be used as the rotating side.

In the corner embodiment, the groove 6 for generating dynamic pressure
The depth of 0, 70, 60a, 70a is from several μm to several
Since it is 10μm, these grooves 60, 70, 60a,
Not only sliding surfaces other than 70a, but also grooves 60 and 7
Since the portions of 0, 60a, and 70a can also receive loads, the contact surface pressure is small and the wear resistance is significantly improved.

In addition, grooves 60, 70, 60a for generating dynamic pressure,
The number of grooves 70a arranged does not necessarily have to be the same, but if the magnitude of the load corresponding to the direction of movement of the shaft body and bearing is different, for example, the number of grooves arranged in which the arrowhead direction coincides with the positive direction of movement. can be made larger than the number of grooves in which the arrowhead direction coincides with the direction of movement in the opposite direction, so that the number of grooves in the arrangement is appropriate for each operating condition.

Groove 60 for generating dynamic pressure in each of the above embodiments,
Since 70, 60a, and 70a are prevented from protruding from the bearing gap 15, even when oil or grease is used as a lubricant, leakage of the lubricant can be suppressed to a minimum. Especially groove 6
0, 70, 60a, and 70a are connected facing each other in a diamond shape, so even if the shaft body and bearing move in both forward and reverse directions, the lubricant moves inside the grooves, preventing lubricant leakage. can be effectively prevented.

FIGS. 5 and 6 respectively show examples of radial plain bearings in which the lubricant leakage prevention effect is enhanced when oil or grease is used as the lubricant.

FIG. 5 shows an annular lubricant reservoir groove 16 provided at both axial ends of the radial inner surface 21 of the radial plain bearing 20 having the dynamic pressure generation grooves 60 and 70 shown in FIG. Indicate the case. The depth of the groove 16 for lubricant reservoir is appropriately selected within the range of 0.1 to 1.0 mm.

FIG. 6 shows grooves 60 and 70 for generating dynamic pressure arranged on the radial inner surface 21 of the radial plain bearing 20.
A case is shown in which a plurality of circular recesses 17 are provided at appropriate intervals between them. The depth of this recess 17 is 0.1
Select as appropriate within the range of ~1.0mm.

As shown in FIG. 5 or FIG. 6, by providing the groove 16 or recess 17 for lubricant reservoir, the oil or grease flowing out from the grooves 60, 70 for generating dynamic pressure can be removed from the annular groove 16 or recess 17. It can be stored inside.

Further, since the lubricant reservoir groove 16 and the recess 17 are filled with lubricant before operation, oil leakage within the bearing gap 15 can be prevented.

Although FIGS. 5 and 6 are examples of rotational motion, the linear motion, rotary linear motion, and rotational motion examples shown in FIGS. 2 to 4 also include grooves for lubricant reservoirs or A recess can be provided.

Moreover, when the bearings 20, 30, 40, and 50 are made of synthetic resin, the wear resistance of the sliding surfaces increases.

As is clear from the above explanation, this device has an arrowhead-shaped groove on at least one of the sliding surfaces of the shaft and the bearing, the arrowhead direction of which coincides with the direction of movement of the shaft and the bearing, and Arrowhead-shaped grooves whose arrow tips coincide with the direction are connected facing each other in a rhombus shape, and are provided on the sliding surface. Therefore, according to this invention, even if one of the shaft body and the bearing moves in either the forward or reverse direction, it is possible to generate dynamic pressure on the sliding surface of the shaft body and the bearing. A hydrodynamic sliding bearing capable of movement in both directions is obtained. Further, according to this invention, even if the shaft body and the bearing move in both forward and reverse directions, the lubricant moves inside the groove, so leakage of the lubricant can be effectively prevented.

Furthermore, according to this invention, the grooves whose arrowheads coincide with one direction of motion and the grooves whose arrowheads coincide with the other direction of motion are both located at two or more locations in the direction of motion,
and at two or more places in the direction perpendicular to the direction of motion, so either one of the shaft body and the bearing is supported relative to the other at two or more places in the direction of motion and at two or more places in the direction perpendicular to the direction of motion. No matter which direction you move, the shaft will not tilt relative to the bearing.
You can exercise stably.

[Brief explanation of the drawing]

Figure 1 shows an embodiment of this invention for a radial plain bearing, Figure a is a sectional view, Figure b is a developed view of the radial inner surface, and Figure 2 is an example of this invention for a linear sliding bearing. FIG. 3 shows an embodiment of this invention for a radial linear plain bearing, FIG. is a developed view of the radial/linear inner surface, 4th
The figures show an embodiment of this invention regarding a thrust sliding bearing, in which figure a is a sectional view, figure b is a plan view of the thrust bearing surface, and FIGS. 5 and 6 are other embodiments of this invention, respectively. Examples are shown in Figs. 5a and 6a are cross-sectional views, Figs. 5b and 6b are developed views of the radial inner surface, and Figs. 5c and 6c.
are sectional views taken along line A-A in FIGS. 5b and 6b, respectively. In the figure, 10 is a shaft; 11, 12, 13, and 14 are respectively the radial outer surface, linear outer surface, radial/linear outer surface, and thrust end surface of the shaft; 20 is a radial sliding bearing; 21 is its radial inner surface;
0 is a linear sliding bearing, 31 is its linear inner surface, 40 is a radial linear sliding bearing, 41
is its radial linear inner surface, 50 is a thrust sliding bearing, 51 is its thrust bearing surface, 60, 7
0 is a groove for generating dynamic pressure.

Claims (1)

[Claims for Utility Model Registration] (1) The shaft body and the bearing are relatively capable of any one of rotational movement in forward and reverse directions, linear movement, and rotational linear movement through mutual sliding surfaces, An arrowhead-shaped groove for generating dynamic pressure is formed on at least one of the sliding surfaces, and the groove for generating dynamic pressure has an arrowhead direction that corresponds to one direction of movement of the shaft body and the bearing; Grooves whose arrowheads coincide with the direction of motion of the other are connected facing each other in a rhombus shape, and are arranged on the sliding surface, and grooves whose arrowheads coincide with the direction of motion of one and the direction of motion of the other. A hydrodynamic sliding bearing characterized in that the grooves are located at two or more locations in the direction of motion and at two or more locations perpendicular to the direction of motion. (2) A groove for lubricant reservoir deeper than the depth of the groove for generating dynamic pressure is provided at both ends of at least one of the sliding surfaces of the shaft body and the bearing as described in claim 1 of the utility model registration claim. hydrodynamic plain bearing. (3) A recess deeper than the depth of the groove for generating dynamic pressure is provided between the groove for generating dynamic pressure on the sliding surface of at least one of the shaft body and the bearing.Claim 1 of Utility Model Registration Dynamic pressure type plain bearings as described in .