KR100723040B1 - Bearing assembly for high speed rotary body - Google Patents

Abstract

Provided is a bearing assembly for a high speed rotating body configured to selectively receive a bearing having different characteristics according to the rotational speed of the high speed rotating body. Bearing assembly according to an embodiment of the present invention includes a ball and the inner ring and the outer ring surrounding the ball, the ball bearing for supporting the load during low-speed operation of the high speed rotating body; And an inner block and an outer block each having inclined surfaces disposed to face each other, and a conical bearing supporting a load during high speed operation of the high speed rotating body. The load bearing action of the ball bearing and the conical bearing is automatically changed according to the rotational speed of the high speed rotating body. The conical bearing has a lubricating fluid film thickness between the inner block and the outer block due to the increase in the rotating speed of the high speed rotating body. Increases to support the load when the gap between both blocks exceeds the set value.

Conical, bearing, ball, sliding, wedge effect, oil film, play, journal, thrust,

Description

BEARING ASSEMBLY FOR HIGH SPEED ROTARY BODY}

1 is an exploded cross-sectional view of a bearing assembly according to an embodiment of the present invention.

FIG. 2A shows a right side view of the outer block of FIG. 1 viewed from the right side, and FIG. 2B shows a "II-II" cross-sectional view of the inner block and the outer block of FIG. 1 assembled together.

3 schematically illustrates a state in which the bearing assembly of FIG. 1 is installed in a high speed rotating body.

4A to 4C schematically show operating state diagrams for explaining the load converting action.

Figure 5 shows a right side view of the outer block in the conical bearing of the bearing assembly according to the second embodiment of the invention.

FIG. 6A schematically illustrates a state in which a bearing assembly according to a third embodiment of the present invention is installed in a high-speed rotating body, and FIG. 6B illustrates a cross-sectional view "VI-VI" of FIG. 6A.

7 illustrates a state in which a bearing assembly according to a fourth embodiment of the present invention is installed in a high speed rotating body.

The present invention relates to a bearing assembly for a high speed rotating body that is subjected to axial and radial loads, and more particularly, a bearing for a high speed rotating body configured to selectively receive a bearing having different characteristics according to the rotational speed of the rotating body. To an assembly.

High speed rotors such as turbo compressors, gas turbines, turbo chargers, and the like, may be directly driven by high speed motors and turbines, and general motors, depending on the driving method. It is divided into an indirect drive system that increases the rotation speed by using a gear increaser on the back.

When the high speed rotor rotates, axial load acting in the axial direction due to the pressure difference between the impeller inlet and the outlet regardless of the driving method, and load due to gravity acting on the rotor, in particular, indirect driving In the high speed rotary body of the method, in addition to the above loads, a combined load (that is, a combined load of a radial load and an axial load) according to a rotational force transmission using a gear increaser such as a helical gear is applied.

Therefore, the high speed rotating body is essentially provided with a bearing for supporting the loads.

The bearing may be classified into a sliding bearing and a rolling bearing according to the type of motion. The rolling bearing is operated by transmitting a load to the inner ring (or outer ring) through a rolling element between the inner ring and the outer ring, for example, a ball, and a sliding bearing. Compressed air is filled between the contact surface of the silver bearing and the journal, or oil or grease is filled.

Therefore, conventionally, a radial sliding bearing and a thrust sliding bearing are used, or the rolling bearing is used to support the high speed rotating body.

However, the rolling bearings, for example, ball bearings have advantages such as low starting friction loads and operating friction loads due to point contact, and supporting both radial and axial loads, while high loads (loads) There is a disadvantage that the durability is weak.

In addition, the sliding bearing has the advantage of being able to withstand high loads by surface contact, but has high starting friction loads, oil film is not sufficiently formed during start operation and stop operation, and wear occurs, and unbalance during rotation When the vibration occurs due to the wear and the like due to the breakage of the oil film and the contact of the metal to the metal has the disadvantage of reducing the durability.

In addition, in the conventional bearing, the lubricating fluid film pressure of the thrust bearing increases as the axial load increases due to the increase in the rotational speed of the rotating body, thereby acting as a repulsive force on the axial load. Thereby, there is a problem in that the radial vibration applied to the journal bearing increases.

In addition, because of this, the squareness of the thrust bearing which should be perpendicular to the rotational center axis is distorted, which causes problems such as abrasion or damage to the thrust bearing.

Accordingly, an object of the present invention is to provide a bearing assembly for a high speed rotating body having improved durability by configuring a bearing having different characteristics to be selectively loaded according to a driving region of the high speed rotating body.

The object of the present invention described above,

A bearing assembly for supporting a high speed rotating body,

A ball bearing including a ball and an inner ring and an outer ring surrounding the ball, the ball bearing supporting a load during low speed operation of the high speed rotating body; And

A conical bearing including an inner block and an outer block each having an inclined surface disposed to face each other, the conical bearing supporting a load during high speed operation of the high speed rotating body;

It can be achieved by a bearing assembly for a high speed rotating body comprising a.

In this way, the ball bearing and conical bearing constituting the bearing assembly of the present invention are configured such that the load supporting action is automatically changed in accordance with the operating area (rotational speed) of the high speed rotating body.

For example, in the low speed operation including the start operation and the stop operation of the high speed rotating body, the ball bearing supports the load so that the conical bearing is operated under no load.

The ball bearing acts as a safety guide when abnormal radial and axial loads and vibrations occur during high speed operation.

More specifically, the ball bearing acts to prevent the rotational shaft from escaping when the load is generated in the opposite direction to the inclined surface of the conical bearing due to surging during high speed operation, and the axial load becomes abnormal, and also abnormal vibration When the lubricating fluid film of the conical bearing is destroyed, for example, the lubricating fluid film of the conical bearing serves as a safety guide temporarily responsible for the radial load until the lubricating fluid film of the conical bearing is formed again.

In addition, the conical bearing increases the gap between the inner block and the outer block of the radially loaded side as the rotation speed of the high-speed rotating body increases due to the increase in the lubricating fluid film thickness, so that the gap exceeds the set value. To support radial and axial loads, in which the ball bearings are operated under no load.

Here, the set value is determined by the difference between the set gap of the conical bearing and the set gap of the ball bearing.

Therefore, it is possible to take advantage of the ball bearings, which have lower damage and starting friction loads at the start and stop operation than the conical bearings at low speed, and can support higher loads than the ball bearings at the high speed. The advantages of bearings are available.

The inner ring of the ball bearing and the inner block of the conical bearing are fixed to the high speed rotating body so that the high speed rotating body can be integrally rotated with the high speed rotating body.

In this case, a gradient section may be formed on the inclined surface of the outer block of the conical bearing, and a lubricating fluid hole communicating with the gradient section may be formed in the outer block.

As another example, a gradient section may be formed on the inclined surface of the inner block of the conical bearing, and a lubrication fluid hole communicating with the gradient section may be formed in the inner block.

As another example, a gradient section and a non-gradient section are formed on the inclined surface of the outer block of the conical bearing, wherein the gradient section is formed on a side receiving a radial load, and a lubricating fluid hole communicating with the gradient section is formed on the outer block. It is also possible.

On the other hand, the outer ring of the ball bearing and the outer block of the conical bearing is fixed to the high speed rotating body can be rotated integrally with the high speed rotating body.

In this case, a gradient section may be formed on the inclined surface of the inner block of the conical bearing, and a lubricating fluid hole communicating with the gradient section may be formed in the inner block.

As another example, a gradient section and a non-gradation section are formed on the inclined surface of the inner block of the conical bearing, wherein the gradient section is formed on a side receiving a radial load, and a lubricating fluid hole communicating with the gradient section is formed on the inner block. It may be.

The high speed rotating body may be supported by the first bearing assembly and the second bearing assembly. In this case, the first bearing assembly may be fixed to the housing, and the second bearing assembly may be fixed to the first bearing assembly by a connecting member to allow axial movement. At this time, the connecting member is preferably formed of a material having the same coefficient of thermal expansion as the axis of the high-speed rotating body.

In addition, the conical bearing of the first bearing assembly and the conical bearing of the second bearing assembly may be installed so that respective inclined surfaces are disposed in the same direction or in opposite directions, and the length and the inclination angle of the inclined surface are radial loads and axial directions. It can be adjusted according to the load.

Hereinafter, exemplary embodiments of the present invention will be described in detail with reference to the accompanying drawings.

1 is an exploded cross-sectional view of a bearing assembly according to an exemplary embodiment of the present invention, and FIG. 2A is a right side view of the outer block of FIG. 1 viewed from the right side, and FIG. 2B is an inner block of FIG. The "II-II" cross section in the state which assembled the outer block is shown.

3 schematically illustrates a state in which the bearing assembly of FIG. 1 is installed in a high speed rotating body, and FIGS. 4A to 4C illustrate an operation state diagram for explaining a load converting action.

As shown, the bearing assembly 100 according to the embodiment of the present invention includes a ball bearing 200 and a conical bearing 300.

The conical bearing 300 supports a load during the high speed operation of the high speed rotating body 400, and includes an inner block 310 and an outer block 330 each having inclined surfaces 311 and 331 disposed to face each other. Include.

Here, the lengths and inclination angles of the inclined surfaces 311 and 331 may be appropriately adjusted according to the magnitude of the radial load and the axial load.

The ball bearing 200 supports the load during the low speed operation of the high speed rotating body 400, and includes the ball 210, an inner ring 230 and an outer ring 250 surrounding the ball. Here, the low speed operation includes start operation and stop operation. The ball bearing 200 of this configuration is assembled inside the outer block 330 adjacent to the inner block 310.

In addition, the ball bearing 200 acts as a safety guide when radial and axial loads are abnormally generated or vibration occurs during the high speed operation in which the conical bearings 300 are in charge.

More specifically, surging (surging: when operating a pipe or a pipe connected to a fan, the pressure, flow rate, rotational speed, power required, etc. periodically change in any operation state, the vibration is self-excited) Ball bearing acts to prevent the shaft of the high-speed rotating body from escaping when the load is generated in the opposite direction to the inclined surface of the conical bearing due to On the other hand, when the lubricating fluid film of the conical bearing is destroyed due to abnormal vibration, etc., it acts temporarily responsible for the radial load until the lubricating fluid film of the conical bearing is formed again.

Tapered gradient sections 333 are formed on the inclined surface 331 of the outer block 330. The gradient sections 333 generate pressure in the lubricating fluid film by the wedge effect when the high speed rotor 400 rotates to increase the hydraulic pressure (fluid pressure) of the lubricating fluid film and increase the fluid film thickness. Acts as an interval for

In addition, the outer block 330 is provided with lubricating fluid holes 335 for supplying lubricating fluid, for example, oil, to the gradient sections 333. Of course, air may also be used as the lubricating fluid.

The bearing assembly 100 of such a configuration is characterized in that the load supporting action is automatically changed according to the operating area (rotational speed) of the high speed rotating body 400.

To this end, the setting gap Gc of the conical bearing 300 itself is larger than the setting gap 2Gb of the ball bearing 200 itself.

Here, the set gap Gc of the conical bearing 300 is the ball 210 of the ball bearing 200 is the inner ring 230 and the outer ring in a state in which the ball bearing 200 is coupled to the outer block 330 When it is located at the axial center X of the 250, it refers to a gap occurring between the inner block 310 and the outer block 330 in either direction in the radial direction, and the set gap 2Gb of the ball bearing 200. ) Is a ball in the difference between the inner diameter of the outer ring 250 and the outer diameter of the inner ring 230 in a radial direction in a state in which the ball 210 is located at the axial center of the inner ring 230 and the outer ring 250. The diameter of 210 refers to the limit value.

For example, as shown in FIG. 4A, the setting gap Gc of the conical bearing 300 may be formed at 0.15 mm, and the setting gap 2Gb of the ball bearing 200 may be formed at 0.10 mm. have.

The reason why the setting gap Gc of the conical bearing 300 is larger than the setting gap 2Gb of the ball bearing 200 is according to the rotational speed of the high speed rotor 400 and the ball bearing 200 and coney. The load supporting action between the curl bearings 300 is to be automatically converted.

When the setting gap 2Gb of the ball bearing 200 and the setting gap Gc of the conical bearing 300 are formed at the above values, the conical bearing 300 increases the rotation speed of the high speed rotor 400. As a result, the lubricating fluid film thickness increases between the inner block 310 and the outer block 330 of the radially loaded side by the wedge effect, which causes a gap between the inner block 310 and the outer block 330. Is increased to support the load from when the set value G1 is exceeded.

Here, the set value G1 is set to the difference between the set gap Gc of the conical bearing 300 and the set gap 2Gb of the ball bearing 200, that is, 0.05 mm (G1 = Gc-2Gb = 0.05 mm).

Therefore, when the gap of the conical bearing exceeds 0.05 mm due to the increase in the thickness of the lubricating fluid film, the load is supported by the conical bearing 300 from this time, and the ball bearing 200 is operated under no load. This will be described in more detail with reference to FIGS. 4A to 4C.

On the other hand, in the above, although the setting gap (Gb) of the ball bearing 200 and the setting gap (Gc) of the conical bearing (300) were set to 0.10 mm and 0.15 mm, respectively, the size of the setting gap is to understand the present invention. This is a numerical value given to help with this, and can be set to various values depending on the lubricating fluid used. Of course, when the value of the gap is changed, it is natural that the set value G1 is also changed.

The bearing assembly 100 having the above configuration may be installed in the high speed rotating body 400 as shown in FIG. 3.

The high speed rotor 400 includes a shaft 410 on which the bearing assembly 100 is installed, and an impeller 430 at the end of the shaft 410. Here, it is assumed that the high speed rotating body 400 is a high speed rotating body driven by a direct drive method, and the shaft 410 is assumed to be a motor direct rotating shaft.

In the bearing assembly, the inner ring 230 of the ball bearing 200 and the inner block 310 of the conical bearing 300 are coupled to the shaft 410. The shaft 410 is provided with a pair of bearing assemblies spaced apart by a set distance.

In FIG. 3, the bearing assembly installed on the left side is called the first bearing assembly 100, and the bearing assembly installed on the right side is called the second bearing assembly 100 ′.

The outer block 330 of the conical bearing 300 provided in the first bearing assembly 100 and the outer block 330 'of the conical bearing 300' provided in the second bearing assembly 100 'are connected to each other. Is fixed by 130.

In this case, the connecting rod 130 is formed of a material having the same thermal expansion coefficient as that of the shaft 410, for example, the same material as the shaft 410.

In addition, the outer block 330 of the first bearing assembly 100 is fixed to the housing 110 while the outer block 330 'of the second bearing assembly 100' is not fixed to the housing 110. .

On the other hand, the housing 110 is formed with a fluid supply hole 115 in communication with the lubricating fluid hole (335).

In FIG. 3, reference numeral 450 denotes a seal assembly, 470 denotes a cap bolt, and 490 and 495 denote washers and locking bolts.

When the first and second bearing assemblies 100 and 100 'are installed as described above, the shaft 410 and the housing 110 are thermally thermally deformed according to different thermal expansion coefficients due to heat generated during the rotational operation of the high-speed rotating body 400. Although the first and second bearing assembly (100, 100 ') is connected by the connecting rod 130 of the same coefficient of thermal expansion as the shaft 410, even if it is expanded, the second bearing assembly is assembled without being fixed to the housing (100 ') is slid according to the thermal expansion and contraction of the shaft has the effect of maintaining a constant gap between the bearing assembly (100, 100').

Hereinafter, with reference to the accompanying drawings Figures 4a to 4c will be described the principle that the load supporting action is automatically converted.

Figure 4a is a view showing a state before the installation of the bearing assembly on the shaft of the high speed rotating body, Figure 4b is a view showing a stationary state of the shaft after installing the bearing assembly on the axis of the high speed rotating body, Figure 4c It is a figure which shows the state which a shaft rotates at high speed, after installing in the shaft of a high speed rotating body.

First, referring to FIG. 4A, as mentioned above, the ball bearing 200 maintains a setting gap 2Gb of 0.10 mm, and the conical bearing 300 maintains a setting gap Gc of 0.15 mm. .

In this state, when the above-described bearing assembly 100 is assembled to the shaft 410 of the high-speed rotating body 400, as shown in FIG. 4B, the ball bearing 200 is caused by a radial load due to the load of the shaft 410. Gap) and the gap of the conical bearing 300 are changed.

Hereinafter, for convenience of description, a gap formed at an upper side around the axis 410 is called an upper gap, and a gap formed at a lower side is called a lower gap.

When the bearing assembly 100 is assembled to the shaft 410 as described above, the lower gap 2Gb 'of the ball bearing 200 becomes zero, and the upper gap 2Gb "of the ball bearing 200 becomes zero. 0.20 mm, and the lower gap Gc 'of the conical bearing 300 is 0.05 mm equal to the set value G1, and the upper gap Gc "of the conical bearing 300 is 0.25 mm. Becomes

In this state, in the starting operation in which the shaft 410 starts to rotate, a radial load according to the shaft rotation is supported by the ball bearing 200, which causes the lower gap 2Gb 'of the ball bearing 200 to be zero. This is because the axis 410 is only supported by the ball bearing 200 because it is zero.

In addition, when the rotational speed of the shaft 410 is increased, pressure is generated in the lubricating fluid film filled in the lower gap Gc 'of the conical bearing 300 due to the wedge effect due to the increase of the rotational speed. Gradually, the lubricating fluid film thickness of the lower gap Gc 'is increased.

Accordingly, while the lower gap Gc 'of the conical bearing 300 exceeds the set value G1, the shaft 410 moves upward and centers due to the geometrical characteristics of the conical bearing 300. Accordingly, the conical bearing 300 supports the radial load. At this time, the lower gap 2Gb 'of the ball bearing 200 is increased as the lower gap Gc' of the conical bearing 300 is increased, so that the ball 210 is separated from the inner ring 230 and the outer ring 250. Since a constant gap (shown as 2Gb ', Gb' = 0.005 mm) is maintained, the ball bearing 200 is operated at no load while the conical bearing 300 supports the radial load.

At this time, the upper gaps 2Gb ", Gb" = 0.095 mm of the ball bearing 200 are changed to 0.19 mm, and the upper gap Gc "of the conical bearing 300 is changed to 0.24 mm.

When the conical bearing 300 supports the load as described above, when the rotational speed of the shaft 410 is reduced to a stationary driving state below a predetermined speed (falls below a predetermined speed), the conical bearing 300 Since the pressure and the thickness of the lubricating fluid film filled in the lower gap Gc 'of the are reduced, the ball bearing 200 supports the radial load as in the start operation.

Meanwhile, when the shaft 410 is rotated, an axial load is generated by the rotation of the impeller 430. The axial load and the radial load are the lubricating fluid filled in the gap Gc of the conical bearing 300. As the pressure of the membrane acts as a repulsive force, it is complexly supported by the conical bearing 300.

In addition, the ball bearing 200 is a shaft of the high-speed rotating body when the radial bearing and the axial load is abnormally generated or vibrated due to surging during high speed operation in which the conical bearing 300 is responsible for load. When the lubricating fluid film of the conical bearing is destroyed due to abnormal vibration, it acts as a journal bearing that is temporarily responsible for the radial load until the lubricating fluid film of the conical bearing is formed again. do.

As described above, the bearing assembly of the above configuration can take advantage of the ball bearings, which have low damage during start-up and stop operation and low starting friction loads, compared to conical bearings, and high-speed operation at high speeds, as described above. Take advantage of conical bearings that can support the load.

Therefore, when the bearing assembly having the above-described configuration is installed to support the shaft of the compressor in which the change of the driving and stopping states occurs frequently, the durability degradation of the bearing due to the frequent change of the driving and stopping states can be effectively prevented.

Here, the high speed operation refers to a state in which air is rotated at a rotation speed of approximately 10,000 rpm or more when air is used as a lubricating fluid of the conical bearing.

Of course, when oil is used as the lubricating fluid, the conical bearing supports the load even when the oil rotates at a lower rotational speed than that of the air.

As such, the rotational speed that is a reference for distinguishing the high speed operation and the low speed operation in which the change of the load supporting action occurs may vary depending on what is used as the lubricating fluid of the conical bearing.

On the other hand, although not shown, the gradient section may be formed only on the inclined surface under the radial load, that is, the lower side of the shaft on which the axial load acts.

5 is a right side view of the outer block in the conical bearing of the bearing assembly according to the second embodiment of the present invention, in which the conical bearing of the present embodiment is a part of the inclined surface of the outer block 330a, in particular a radius A gradient section 333a is formed only on the side receiving the directional load, and a non-gradient section 337 is formed in the remaining section. In FIG. 5, reference numeral 335a denotes a lubricating fluid hole through which lubricating fluid, such as oil, is supplied.

When the conical bearing of such a configuration is applied to a high-speed rotating body of a direct drive type, the gradient section is formed on the side receiving the radial load, that is, the side on which the load of the shaft acts, to support the load acting radially below the shaft. In the case of applying to an indirect drive type high-speed rotating body that rotates the shaft (see 410 of FIG. 3) using a gear increaser (not shown), the gradient section may be operated by the radial load of the gear increaser ( It is formed on the side opposite to the side on which the axial load acts) to effectively support the radial load acting radially upward of the shaft.

6A and 6B schematically illustrate a state in which a bearing assembly according to a third embodiment of the present invention is installed in a high speed rotating body, and includes a gradient section 313b on an inclined surface of the inner block 310b of the conical bearing 300b. ) And a lubricating fluid hole 315b communicating with the gradient section 313b is formed in the inner block 310b.

Here, gas as lubricating fluid may be supplied through the lubricating fluid hole 315b.

Even in this case, the gradient section 313b may be formed only on the side receiving the radial load or on the entire inclined surface. In FIGS. 6A and 6B, reference numeral 330b denotes an outer block.

7 illustrates a state in which a bearing assembly according to a fourth embodiment of the present invention is installed in a high speed rotating body, and illustrates a high speed rotating body rotating by a high speed motor or the like.

In this embodiment, a pair of bearing assemblies 100 are used to support the high-speed rotating body, and the inner block 310c of the conical bearing 300c is fixed to the shaft 410 'to the outside of the conical bearing 300c. The outer ring 250c of the block 330c and the ball bearing 200c is installed to rotate together with the impeller 430, and the inclined surfaces of the left conical bearing and the right conical bearing are installed in opposite directions.

Although the preferred embodiments of the present invention have been described above, the present invention is not limited thereto, and various modifications can be made within the scope of the claims and the detailed description of the invention and the accompanying drawings.

As described above, in the bearing assembly for the high speed rotating body of the present invention, since the ball bearing supports the load during the starting operation and the stopping operation of the high speed rotating body, the starting friction load and the driving friction load are low, and thus power consumption can be reduced. In addition, conical bearings can be protected from wear and damage.

In addition, since the conical bearing supports the load during the high speed operation of the high speed rotating body, the high load can be supported and the generation of vibration due to unbalance or the like during rotation can be suppressed.

Thus, the durability of the bearing assembly can be effectively improved.

In addition, since the ball bearing acts as a safety guide during the high speed operation in which the conical bearing supports the load, it is possible to improve stability and the like.

Claims (16)

A bearing assembly for supporting a high speed rotating body, A ball bearing for a journal and thrust comprising a ball and an inner ring and an outer ring surrounding the ball; And Conical bearings comprising an inner block and an outer block, each having an inclined surface disposed to face each other Including; And the ball bearing supports a load during low speed operation of the high speed rotating body, and the conical bearing supports a load during high speed driving of the high speed rotating body. The method of claim 1, The conical bearing is characterized in that the lubricating fluid film thickness between the inner block and the outer block increases due to the increase in the rotational speed of the high-speed rotating body to support the load from when the gap between the two blocks exceeds a set value Bearing assembly for high speed rotors. The method of claim 2, The setting value is determined by the difference between the setting gap of the conical bearing and the setting gap of the ball bearing. The method of claim 3, wherein The setting gap of the conical bearing is formed larger than the setting gap of the ball bearing bearing assembly for a high-speed rotating body. The method of claim 4, wherein And the ball bearing is assembled inside the outer block of the conical bearing. The method of claim 5, The high speed rotating body is a bearing assembly for a high speed rotating body is supported by the first bearing assembly and the second bearing assembly. The method of claim 6, The inclined surface of the conical bearing of the first bearing assembly and the conical bearing of the second bearing assembly are arranged in the same direction. The method of claim 6, And the inclined surfaces of the conical bearings of the first bearing assembly and the conical bearings of the second bearing assembly are arranged in opposite directions. The method of claim 6, The first bearing assembly is fixed to the housing, the second bearing assembly is fixed to the first bearing assembly by a connecting member to enable the axial movement, the connecting member is made of a material having the same coefficient of thermal expansion as the high speed rotating body Bearing assembly for a high-speed rotating body characterized in that made. The method according to any one of claims 1 to 9, An inner ring of the ball bearing and an inner block of the conical bearing are fixed to the high speed rotating body to be rotated. The method of claim 10, A grade section is provided on the inclined surface of the outer block of the conical bearing, and the outer block is provided with a lubricating fluid hole communicating with the grade section. The method of claim 10, A gradient section is provided on the inclined surface of the inner block of the conical bearing, and the inner block is provided with a lubricating fluid hole communicating with the gradient section. The method of claim 10, The outer block inclined surface of the conical bearing is provided with a gradient section and a non-gradient section, the gradient section is provided on the side receiving the radial load, the outer block is characterized in that the lubricating fluid hole communicating with the gradient section is provided. Bearing assembly for high speed rotating body. The method according to any one of claims 1 to 8, An outer ring of the ball bearing and an outer block of the conical bearing are fixed to the high speed rotating body to be rotated. The method of claim 14, A gradient section is provided on the inclined surface of the inner block of the conical bearing, and the inner block is provided with a lubricating fluid hole communicating with the gradient section. The method of claim 14, A gradient section and a non-gradation section are provided on the inner block inclined surface of the conical bearing, and the gradient section is provided on a side receiving a radial load, and the inner block is provided with a lubricating fluid hole communicating with the gradient section. Bearing assembly for high speed rotating body.

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