KR100193685B1 - Hydrostatic bearing device - Google Patents

Abstract

The present invention relates to a hydrostatic bearing device having a self-aligning function by a spherical support mechanism.

The hydrostatic bearing device B having a self-aligning function according to the present invention includes a hydrostatic bearing pad 13 supported by a spherical support mechanism 21 on a bearing base 1 so that an operating posture can be varied. The spherical support mechanism 21 is provided with hemispherical spherical pairs 5 and 17 opposed to each other, and an oil injection space 43 is formed therebetween so as to receive the pressurized oil from the pressure oil passage 47.

Therefore, the spherical support mechanism can reduce the load acting on the inside and enable sufficient lubrication by utilizing the structure of the static pressure bearing device inherent in the self-aligning function without complicated configuration.

Description

Hydrostatic bearing device

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hydrostatic bearing device, and more particularly, to a hydrostatic bearing device having a self-alignment function by a spherical support mechanism.

In relation to large machines, appliances or structures with rotating members such as shafts, there is typically used a hydrostatic bearing arrangement of the type in which such rotating members are arranged around and supported by a plurality of individually actuated hydrostatic bearing pads. . As a bearing device of this type, each of the hydrostatic bearing pads having a positive pressure pocket is supported by a corresponding spherical support mechanism with a variable operating posture with a bearing base, so that the self-aligning function is achieved by the spherical support mechanism. Is already known.

The self-aligning function is a function for automatically compensating the operating posture of the hydrostatic bearing pads, and utilizes the self-restoration tendency due to the pressure difference in the hydrostatic pockets so that the bearing spacing between the bearing pad and the rotating shaft is parallel. Thus, in the spherical support mechanism, a pair of opposing hemispheres on the bearing pad side or the bearing base side cooperate to pivotally move relative to the pivot type.

In such a conventional hydrostatic bearing device in which the bearing load acts between a pair of opposing hemispheres of the spherical support mechanism, the self-alignment caused by the bearing load increases as the bearing load increases, which is not smooth. .

In this regard, there may be a means between the hydrostatic bearing pad and the bearing base, having a hydraulic chamber for injecting hydraulic oil such that the bearing pad has a bearing against load. However, this means requires a separate configuration to form a hydraulic chamber between the bearing pad and the bearing base.

Moreover, in order for the self-alignment to be performed smoothly, sufficient lubricant is required in addition to the corrosion resistance means for the hemispheres of the spherical support mechanism. However, in these conventional apparatuses, no active lubrication is performed on the hemispherical surface, and self-alignment is not guaranteed smoothly.

It is an object of the present invention to provide a hydrostatic bearing device having a self-aligning function which introduces a spherical support mechanism that is not structurally complex to reduce its working load and at the same time allow sufficient lubrication.

1 is a schematic view showing an application example of a radial bearing as a static pressure bearing device according to an embodiment of the present invention.

2 is a longitudinal sectional view of the hydrostatic bearing device of FIG.

3 is a plan view of the hydrostatic bearing device of FIG.

4 is a side view of the hydrostatic bearing device of FIG.

5 is a perspective view of a spherical support mechanism of the hydrostatic bearing device of FIG.

6 is a hydraulic circuit diagram of the hydraulic system of the hydrostatic bearing device of FIG.

7 is a hydraulic circuit diagram of a hydraulic system of a hydrostatic bearing device according to another embodiment of the present invention.

8 is a hydraulic circuit diagram of a hydraulic system of a hydrostatic bearing apparatus according to another embodiment of the present invention.

* Explanation of symbols for main parts of the drawings

One ; Bearing bases 3, 29; volt

5, 17; Spherical surface 7; Concave Receiving Support Member

9; Bearing surfaces 10,12,14; Oil groove

11; Hydrostatic pockets 13; Hydrostatic Bearing Pads

19; Iron board support member 21; Spherical support

23; Coupling groove 25; Anti-rotation member

27; Bonding piece 31; Manifold Member

33; Flow control valve 35; Oil pressure passage for positive pressure pocket

37; Circumferential groove 39; Lower opening

41; Inclined grooves 43; Oil injection space

45; Central opening 47; Hydraulic oil passage for reducing load

49; Hydraulic sources 51, 59; Throttle valve

53; High pressure regulating valve 55; Valve

57; Low Pressure Control Valve

According to a first aspect of the present invention for achieving the above object, there is provided a hydrostatic bearing device having a self-aligning function in which a hydrostatic bearing pad having a hydrostatic pocket is supported by a spherical support mechanism on a bearing base such that its operating position is varied. The hydrostatic bearing device is provided with an oil injection space between a pair of basically hemispherical spherical surfaces opposed to each other in a spherical support mechanism, and is provided with a pressure oil passage for supplying pressure oil to the oil injection space.

In the hydrostatic bearing device according to the first aspect of the present invention, oil pressure is supplied from a oil pressure passage to an oil injection space provided between a pair of basically hemispherical spherical surfaces facing each other in a spherical support mechanism. Provides load bearing forces acting between the spheres of the spherical support, reducing the bearing load acting between them. Furthermore, the hydraulic oil acts as a lubricant for the spherical support.

Therefore, according to the first aspect of the present invention, self-alignment is performed smoothly.

According to a second aspect of the invention, the oil injection space in the first aspect of the invention is given in the form of at least one circumferential groove provided concentrically with its central axis on either of the spheres.

In the hydrostatic bearing device according to the second aspect of the present invention, in the spherical support mechanism, the oil is supplied to the oil injection space formed in one of a pair of spherical surfaces and defined by a circumferential groove through a hydraulic oil passage. , Supplied

The hydraulic oil not only reduces the bearing load acting between the spheres of the spherical support mechanism, but also acts as a lubricant for the spherical support mechanism. Furthermore, the sphere of the spherical support mechanism is safe and prevents the effective area from being excessively reduced. do.

Therefore, according to the second aspect of the present invention, not only smooth self-alignment but also the effective area of the spherical surface can be sufficiently secured.

According to the third aspect of the present invention, the pressure oil passage in the first or second aspect of the present invention is connected to the pressure oil supply passage for the positive pressure pocket for supplying the pressure oil to the positive pressure pocket of the positive pressure bearing pad. Positive pressure pocket oil is supplied to the

In the static pressure bearing device according to the third aspect of the present invention, a part of the flow rate of the hydraulic oil for the positive pressure pocket is supplied to the oil injection space via the oil pressure passage, and the load bearing force acting between the spherical surfaces is caused by the positive pressure of the positive pressure pocket. Automatically responds to one bearing drag, so that the bearing load acting between the spheres in the spherical support mechanism can be appropriately reduced without oversufficiency depending on the magnitude of the current bearing drag due to the current static pressure of the hydrostatic pocket.

Therefore, according to the third aspect of the present invention, an appropriate reduction of the bearing load is always achieved.

According to the fourth aspect of the present invention, the spherical support mechanism according to any one of the first to third aspects has a spherical center coinciding with the rotation center of the hydrostatic bearing pad.

In the hydrostatic bearing device according to the fourth aspect of the present invention, the coincidence between the spherical center of the spherical support mechanism and the rotational center of the hydrostatic bearing pad is such that self-alignment is performed according to the operation attitude change operation without involving the movement of the supporting load. Do it.

Therefore, according to the fourth aspect of the present invention, it is possible to always provide a stable and desirable hydrostatic bearing device even when supporting heavy objects.

According to a fifth aspect of the present invention, in any one of the first to fourth aspects of the present invention, the hydrostatic bearing pad guides the oil overflowing from the hydrostatic pocket to the end of the spherical support mechanism for use as lubricating oil. An oil groove for forming is formed.

In the hydrostatic bearing device according to the fifth aspect of the present invention, the oil overflowed from the hydrostatic pocket is actively guided along the oil groove toward the end of the spherical support mechanism.

Therefore, according to the fifth aspect of the present invention, the spherical support mechanism can be effectively protected from corrosion by providing sufficient lubrication for the spherical support mechanism.

According to the sixth aspect of the present invention, in any one of the first to fifth aspects, the hydrostatic bearing device has a hydraulic controller capable of temporarily increasing the pressure oil supplied to the oil pressure passage.

In the hydrostatic bearing device according to the sixth aspect of the present invention, a bearing acting between the spheres of the spherical support mechanism by temporarily increasing the pressure of the hydraulic oil supplied to the hydraulic oil passage during the initial driving. The load can be reduced by temporarily increasing it.

Thus, according to the sixth aspect of the present invention, self-alignment can be achieved with increased adaptability to initial driving and the like, and the spherical support mechanism is stably lubricated by a sufficient amount of lubricant supplied between the spherical surfaces. .

Hereinafter, exemplary embodiments of the present invention will be described in detail with reference to the accompanying drawings. The same members are denoted by the same reference numerals.

1 is a schematic view showing an application example of a radial bearing as a static pressure bearing according to an embodiment of the present invention.

A reference numeral 'A' in FIG. 1 denotes an object to be supported, which is a shaft body, and each reference numeral 'B' is a hydrostatic bearing device and used in pairs to rotatably support the shaft A. FIG. do. A pair of static pressure bearing devices B is provided in the state which inclined downward or upward in the lower left and right sides of the shaft A, respectively.

2-4 is a longitudinal cross-sectional view, a top view, and a side view of the hydrostatic bearing apparatus B, respectively. The hydrostatic bearing device (B) has a generally flat bearing base (1), the upper side of which is basically a hemispherical or hemispherical annular spherical surface (5) and its flat lower surface is formed on the upper recess of the bearing base (1). A spherical concave receiving member 7 fixed by (3), formed of a bearing surface 9 formed in a precise curve so that the upper side has a radius of curvature slightly larger than the radius of the shaft A. And a hydrostatic bearing pad 13 in which a plurality of positive pressure pockets 11 partially embedded therein are additionally formed, and a lower side thereof corresponds to the spherical surface 5 of the receiving support member 7 and is basically a semispherical shape. Or a spherical spherical surface 17 having a hemispherical ring shape, the upper flat surface of which is fastened by a bolt 15 to a lower recess of the hydrostatic bearing pad 13. Phase (凸 狀) and a board supporting member 19.

Therefore, the spherical support mechanism 21 (combination of the receiving support member 7 and the boarding support member 19) on the bearing base 1 is configured to support the static pressure bearing pad 13, whereby the pad 13 is provided. Has a variable operating position with respect to the bearing base (1).

The spherical surfaces 5, 17 of the spherical support mechanism 21 have a common center of curvature C coinciding with the center of rotation of the hydrostatic bearing pad 13, so that their hemispherical shapes are of spherical center C. It can be expressed as the radius of curvature R to the periphery.

Accordingly, the static pressure bearing pad 13 can change its operating position without involving the movement of the bearing load. The bearing base 1 is provided with a yoke-shaped anti-rotation member 25 formed with the coupling groove 23. And the coupling piece 27 which can be coupled to the coupling groove 23 by the bolt 29 is mounted on the hydrostatic bearing pad 13. As a result, the bearing pad 13 cannot be rotated by the engagement of the engaging piece 27 and the engaging groove 23.

The coupling piece 27 is installed to have a central axis at a position that matches the spherical center C of the spherical support mechanism 21 without disturbing the movement of the bearing pad 13.

The hydrostatic bearing pad 13 includes a manifold member 31 and a plurality of flow regulating valves 33 for individual flow rate adjustment for each of the positive pressure pockets 11. The manifold member 31 and the hydrostatic bearing pad 13 are provided with a plurality of hydraulic oil passages 35, and the positive pressure pockets 11 corresponding to each other to supply the adjusted hydraulic oil to the corresponding positive pressure pockets 11, respectively. ) And the flow control valve (33).

As shown in Fig. 5, a pair of circumferential grooves 37 is formed concentrically with the central axis X of the spherical surface 5 in the spherical surface 5 of the spherical recessed accommodating support member 7, and two circumferential grooves are formed. A plurality of inclined grooves 41 interconnecting the 37 and connected to the lower opening 39 of the receiving support member 7 are formed vertically along the circumference. Therefore, an oil injection space 43 composed of a circumferential groove 37 and an inclined groove 41 for guiding or injecting oil is formed between the spherical surfaces 5 and 17 which are in contact with each other.

The lower end opening 39 of the spherical recessed receiving member 7 is limited so that its lower side is blocked by the bearing base 1, and the upper side of the spherical recessed receiving member 7 has a central opening 45 of the spherical iron supporting member 19. In communication. Therefore, the pressure oil is supplied from the load reducing pressure passage 47 opened toward the center opening 45 past the bottom of the positive pressure bearing pad 13. In addition to the lower opening 39 of the receiving support member 7, the central opening 45 of the boarding supporting member 19 is filled with the hydraulic oil through the pressure oil passage 47, and thus the inclined groove 41 and the circumference thereof. The groove 37 is also filled with pressure oil supplied.

In the arcuate bearing surface 9 of the hydrostatic bearing pad 13, a plurality of oil grooves 10, 12 extend along its periphery. In the upwardly or downwardly inclined arrangement of the hydrostatic bearing device B shown in FIG. 1, the bearing pad 13 has one side higher than the other side, and the relatively high side (right side in FIGS. 2 and 3, front in FIG. 4). Side) is formed with an oil groove 14 in communication with the oil groove (10). The oil groove 14 collects oil overflowed from the positive pressure pocket 11 and distributes oil collected from the oil groove 10 to the spherical support mechanism 21. In other words, in the bearing device B disposed inclined upwardly or downwardly in FIG. 1, when oil overflows from the positive pressure pocket 11, the overflowed oil is collected in the oil groove 10, and these oils are provided in the oil groove 14. It flows to the bottom of the hydrostatic bearing pad 13 through, where it penetrates into the spherical support mechanism 21 along the bottom surface and flows in between the spherical surfaces 5 and 17. This will lubricate the spherical support mechanism 21 and at the same time prevent the spherical surfaces 5, 17 from corroding.

6 shows a hydraulic circuit diagram of the hydraulic system of the hydrostatic bearing device B. As shown in FIG. This hydraulic system is provided with a single hydraulic pressure source 49, such as a hydraulic pump, for supplying hydraulic oil to each of the corresponding positive pressure pockets 11 via one of the flow control valves 33. The hydraulic oil supplied from the single hydraulic pressure source 49 is regulated and supplied by the flow control valves 33 installed correspondingly so as to flow sufficiently for each of the positive pressure pockets 11, and the hydraulic oil passages 35 for the positive pressure pockets are provided. The appropriate amount is supplied to the positive pressure pocket 11 through the corresponding passage in the middle. The flow control valve 33 may be a variable throttle valve.

One of the hydraulic oil pressure passages 35 for the positive pressure pocket is branched as a pressure reducing oil passage 47 for supplying the oil pressure corresponding to the hydraulic oil provided for the positive pressure pocket 11 to the oil injection space 43. . The pressure reduction hydraulic passage 47 for reducing the load is provided with a throttle valve 51 for restricting the flow of oil.

According to this configuration, as already mentioned, the oil injection space 43 defined by the circumferential groove 37 and the inclined groove 41 between the spherical surfaces 5 and 17 of the spherical support mechanism 21 is used for reducing the load. The hydraulic oil for the positive pressure pocket is supplied through the oil pressure passage 47 to have a load bearing force acting between the spheres 5 and 17 of the spherical support mechanism 21.

Thus, the bearing load acting between the spheres 5, 12 in the spherical support mechanism 21 is reduced. Moreover, the lubrication action on the sliding contact surface of the spherical support mechanism 21 is forcibly performed by the supplied hydraulic oil. Therefore, irrespective of a given bearing load, a proper and smooth self-alignment can be made to automatically compensate for the operating posture of the hydrostatic bearing pad 13 so that the bearing gap between the hydrostatic bearing pad 13 and the rotational axis A is kept in parallel. (In the case of a radial bearing, the self-regulating centering operation of the static pressure bearing pad 13) is performed.

Moreover, as the positive pressure pocket pressure oil is supplied to the oil injection space 43, the load bearing force acting between the spherical surfaces 5 and 17 automatically corresponds to the bearing drag force due to the static pressure in the positive pressure pocket 11. The bearing load acting between the spherical surfaces 5 and 17 of the spherical support mechanism 21 is reduced without being excessive or insufficient depending on the bearing drag caused by the static pressure in the positive pressure pocket 11.

Furthermore, the oil injection space 43 composed of the circumferential groove 37 and the inclined groove 41 is provided without excessively reducing the effective areas of the respective spherical surfaces 5 and 17. That is, the effective surfaces of the spheres 5 and 17 are sufficiently secured.

In addition, as shown in Figure 2, the receiving support member 7 is for reducing the load determined by the area of the circle having a diameter equal to the diameter D of the larger one of the circumferential groove 37 of the pair of circumferential groove 37 Since it has a pressure receiving surface, the degree of load reduction can be set by arbitrarily selecting the diameter D of the circumferential groove 37 with a large diameter.

The pressure oil supplied to the oil injection space may be different from the pressure oil for the positive pressure pocket, or may be given at a different pressure. For example, as shown in FIG. 7, the pressure reducing passage 47 for reducing load may be directly connected to the hydraulic pressure source 49. Incidentally, in the example of Fig. 7, a variable throttle valve 59 may be employed instead of the flow regulating valve.

Furthermore, the pressure reducing pressure oil supplied to the oil injection space 43 may have a higher line pressure than usual so as to increase the self-aligning effect as in the initial driving.

In such a case, for example, as shown in FIG. 8, a combination of the high pressure regulating valve 53 and the low pressure regulating valve 57 connected through the on / off valve 55 may be applied. The on-off valve 55 may be normally open to have a line pressure regulated for the positive pressure in the low pressure control valve 57, and may be closed to have a line pressure regulated by the high pressure control valve 53 at the time of initial driving. .

In this way, the pressure oil supplied through the pressure reducing hydraulic passage 47 is temporarily raised during initial driving, such that the reduction rate of the bearing load acting between the spheres 5 and 17 of the spherical support mechanism 21 is increased. Temporarily raises the For example, if the reduction ratio of the normal bearing load is 90%, the initial driving can be set to be more than 95%, or even more than 100%, in which case the upper spherical surface 17 of the spherical support mechanism 21 is It will float or be lifted from the lower spherical surface 5.

Furthermore, when the upper spherical surface 17 rises with respect to the opposite lower surface 5 in the spherical support mechanism, a sufficient amount of lubricant is supplied between the spherical surfaces 5 and 17 so that the spherical support mechanism 21 can be lubricated stably. have.

Therefore, according to the present invention, it is possible to reduce the bearing load without structurally complicated in the spherical support mechanism, lubrication can be performed to a sufficient degree, and there is an effect that a smooth self-aligning function can be achieved.

The hydrostatic bearing device according to the present invention is not limited to a radial bearing, but may be applied to a thrust bearing or a linear motion bearing.

Although the present invention has been described in detail only with respect to the described embodiments, it will be apparent to those skilled in the art that various modifications and variations are possible within the technical scope of the present invention, and such modifications and modifications are within the scope of the appended claims.

Claims (6)

In a hydrostatic bearing device having a self-aligning function, in which a hydrostatic bearing pad having a hydrostatic pocket is supported by a spherical support mechanism on a bearing base such that its operating posture is variable. An oil injection space provided between the spherical pairs of basically hemispherical spheres opposed to each other in the spherical support mechanism; And A pressure oil passage for supplying pressure oil to the oil injection space; A hydrostatic bearing device comprising a. The method of claim 1, The oil injection space is formed in any one of the spherical pair, the hydrostatic bearing device characterized in that it is defined by at least one circumferential groove concentric with the central axis. The method according to claim 1 or 2, And said pressure oil passage is in communication with a pressure oil supply passage for a positive pressure pocket for supplying pressure oil to the positive pressure pocket of said positive pressure bearing pad, so that the pressure oil for said positive pressure pocket is supplied. The method according to any one of claims 1 to 3, And the spherical center of the spherical support mechanism is formed to coincide with the center of rotation of the hydrostatic bearing pad. The method according to any one of claims 1 to 4, And said oil pressure bearing pad formed in said hydrostatic bearing pad an oil groove for guiding oil overflowed from said hydrostatic pocket for use as lubricant at the end of said spherical support mechanism. The method according to any one of claims 1 to 5, The hydrostatic bearing device is characterized in that the hydrostatic bearing device characterized in that it comprises a hydraulic controller that can adjust the temporary increase in the pressure oil supplied to the oil pressure passage.