JP2002534647A - Thrust bearing device for high-speed rotating rotor - Google Patents

Abstract

SUMMARY OF THE INVENTION It is an object of the present invention to provide an improved thrust bearing device for a high-speed rotating rotor, which is very rigid in the axial direction and is formed very flexibly with respect to inclination. Furthermore, the axial construction space of the bearing area should be reduced. In accordance with the present invention, the object is to provide a race (16) in which a load introducing body (13) connects to a bearing collar (12), a diaphragm (17) connected to a bearing flange (6), and a race (16). A solution is provided by having a central ring (18) connected to the diaphragm (17). The load introducing body (13) is tapered from the race body (16) toward the central ring (18). The diaphragm (17) is supported on one side by an incompressible medium (23), which is arranged on the side of the diaphragm (17) opposite the bearing collar (12). Which is formed between the diaphragm (17) and the element (19) defining the hollow chamber (20), the element (19) defining the hollow chamber (20) being a bearing flange ( 6) or formed by this bearing flange.

Description

DETAILED DESCRIPTION OF THE INVENTION

The present invention relates to a thrust bearing device for a high-speed rotating rotor, provided with a device for tilt compensation.

[0002] Thrust bearing devices for high-speed rotating rotors must have sufficient axial strength, so that the elastic deflection under maximum axial load must not exceed predetermined limits. However, when the shaft and other rotors are supported, the inclination of the shaft and thus the bearing collar of the thrust bearing occurs due to manufacturing reasons. As a result, the bearing force of the bearing decreases. Numerous structural solutions for compensating tilt are known to address this danger. For example, elastic deformation with eccentric support or elastic deformation of the diaphragm (Dubbel, Taschenbuch fuer den Maschinenbau, I
SBN3-540-57650-9, 18th edition, Springer Publishers, Berlin, Heidelberg, New York, 1995, G95 / 96).

[0003] Furthermore, depending on the rotational imbalance of the high-speed rotating rotor, as used, for example, in turbochargers or other turbomachines, operation-dependent tilting occurs.
This tilting becomes even stronger when the turbomachine is subjected to additional tilting movements during operation (for example, in the case of turbochargers for marine engines).

[0004] EP 0 362 327 discloses a solution for tilt compensation in the case of a thrust bearing device for turbomachines. The inclination of the shaft and thus of the bearing collar is compensated by the elastic web. Thereby, the bearing device has sufficient elasticity for allowable deformation, to prevent excessive deformation,
It is hard to wear.

However, such tilt compensation always requires a compromise between the required axial strength and the desired flexibility for tilt. Furthermore, a relatively large structural space is required in the axial direction.

DISCLOSURE OF THE INVENTION The problem underlying the present invention is to provide an improved thrust bearing device for high-speed rotating rotors, which is very rigid in the axial direction and is formed very flexibly with respect to inclination. is there. In addition, the axial construction space of the bearing area should be reduced.

This object is achieved according to the invention in a device according to the preamble of claim 1 in which the load introduction body is connected to the bearing collar, the diaphragm connected to the bearing flange, and the race body is connected to the diaphragm. A load introducing body tapering from the race body toward the central ring, the diaphragm being supported on one side by an incompressible medium, the incompressible medium being on the side of the diaphragm opposite the bearing collar. Is filled between the diaphragm and the element defining the hollow chamber, and the element defining the hollow chamber is supported by a bearing flange or is formed by the bearing flange. It is solved by being formed.

[0008] By supporting the diaphragm on an incompressible medium, the axial flexibility of the diaphragm is avoided, thereby providing a very rigid axial thrust bearing. The use of a very soft diaphragm in the axial direction, in particular, greatly reduces the torsional strength of the thrust bearing, so that the resulting tilt can be better compensated through such a diaphragm. As a result, the supporting force of the thrust bearing is guaranteed for a long period of time, and its life is prolonged.

With the solution according to the invention, the required axial strength is maintained and the required axial construction space is reduced by a factor of about 3 compared to conventional tilt compensation.

It is particularly advantageous if the load introducer is formed in one piece. This increases the wear resistance of the thrust bearing.

[0011] The diaphragm has a central area connected to the central ring, an edge area connected to the element defining the hollow space, and an intermediate area, wherein the central area and the edge area are thicker than the intermediate area of the diaphragm. It is particularly advantageous if it is formed. By providing such a thickened area for receiving or transmitting the axial force of the machine, the life of the thrust bearing is further increased.

It is furthermore advantageous if the element defining the cavity is provided with an axial stop for the central ring reaching the cavity. This stopper prevents the thrust bearing from breaking in case of breakage. In the case of this failure, a loss of the incompressible medium filled in the hollow chamber occurs. The stopper also acts as a hydraulic damper.

[0013] Advantageously, the element defining the cavity is formed as a lid. This greatly simplifies fabrication and assembly.

Next, the present invention will be described in detail based on embodiments.

Only those elements that are important to the understanding of the present invention are shown. For example, the rotor of the machine connected to the shaft is not shown.

FIG. 1 shows a shaft 4 supported by radial bearings 1 and 2 and a thrust bearing (axial bearing) 3. This shaft is, for example, the shaft 4 of an exhaust turbocharger (not shown) mainly comprising a centrifugal compressor and a turbine. The radial bearings 1 and 2 and the thrust bearing 3 are arranged in a bearing housing 5. A part of the bearing housing 5 is a bearing flange 6. This bearing flange serves to fix the bearing housing 5 inside the shaft housing of the exhaust turbocharger not shown. The bearing flange 6 is connected to the bearing housing 5 via a fixing element 7 formed as a bolt. The radial bearing 1 on the compressor side is fixed to a bearing flange 6 by a lid 8. For this purpose, a fastening element 9 formed as a bolt serves. Lubricating oil supply units 10 and 11 for the radial bearing 2 or the radial bearing 1 and the thrust bearing 3 are arranged in the bearing housing 5 and the bearing flange 6.

The thrust bearing 3 has a rotating bearing collar (bearing comb) 12 fixedly connected to the shaft 4. This bearing collar cooperates with a fixed load introducer 13. Each of the bearing collar 12 and the load introducing body 13 has a rotating surface 14. A lubricating oil gap 15 of the thrust bearing 3 is formed between the rotating surfaces (FIG. 1).

The load introducing body 13 is formed integrally. The load introducing body includes a race body (rotating surface body) 16 connected to the bearing collar 12 and the diaphragm 1 connected to the bearing flange 6.
7 and a central ring 18 connecting the lace body 16 to the diaphragm, and is formed to be tapered from the lace body 16 toward the central ring 18.

On the opposite side of the load introducing body 13 from the race body 16, the lid 19 is provided with a diaphragm 17.
Between the cover 19 and the bearing flange 6 and between the lid 19 and the diaphragm 17
Are formed. Inside the lid 19 formed as an element defining the hollow chamber 20,
A supply passage 22 for an incompressible medium 23 filling the hollow chamber 20 is provided, which is closed by a stopper 21 in communication with the hollow chamber 20. Such a medium 23 is mainly a fluid, especially a synthetic oil. For this purpose, of course, other fluids such as water or solids (for example low-melting metals) are also suitable.

The lid 19 is provided with an axial stop 24 for the central ring 18 reaching into the cavity 20. The diaphragm 17 has a central area 25 connected to the central ring 18, an edge area 26 connected to the bearing flange 6, and an intermediate area 27 (FIG. 2).
. Since the central area 25 and the edge area 26 are formed thicker than the intermediate area 27 of the diaphragm 17, the original diaphragm is formed by the intermediate area 27.

The bearing flange 6 is provided with a recess 28 for accommodating the load introducing body 13, that is, the diaphragm 17. For this purpose, the bearing flange 6 in the range of the recess 28 is provided.
A fitting portion 29 is formed between the diaphragm and the diaphragm 17. A separately manufactured load introducing body 13 is press-fitted into the fitting portion. Similarly, the bearing flange 6 and the diaphragm 17 can be integrally connected. Other fitting part 30
Is formed between the lid 19 and the diaphragm 17. In this case, the connection is welded. Of course, other integral connections (eg, brazing), frictional connections, or shape-complementary connections can be made.

The separately produced load introducer 13 is assembled before the lid 1 is assembled into the bearing flange 6.
9 and can be filled with an incompressible medium 23 in the hollow space. This allows for simple and low cost fabrication and final assembly. By using a tempered steel coated for the load introducer 13, great strength is obtained. An axial stopper 24 in the cavity 20 allows the incompressible medium 23
In the case of the loss, the axial strength of the thrust bearing 3 is prevented from being lost. By using a material with good emergency properties for the load introducer 13 (eg spring bronze), this safety concept can be further taken into account.

During operation of the exhaust turbocharger, the axial thrust of the turbine, indicated by F1, is directed towards the radial bearing and urges the thrust bearing 3 mainly in the axial direction. In this case, the generated axial force is transmitted to the bearing flange 6 via the bearing collar 12, the race body 16, the center ring 18, and the diaphragm 17. By locally increasing the thickness of the central area 25 and the edge area 26 of the diaphragm 17, the transmission of force is facilitated. On the other hand, the flexibility of the diaphragm 17 in the axial direction is different from that of the incompressible medium 23.
Only a small elastic deflection in the range of one-tenth occurs, as it is prevented by being supported on (for example, pressurized oil). In the case of pulsating axial force, the incompressible medium 2
3 acts as an axial damper, thereby counteracting the increased axial force. Otherwise, this axial force will cause breakage. The inclination of the shaft 4 and thus the inclination of the bearing collar 12 of the thrust bearing 3, which occurs structurally or as a result of operation, is compensated for by a very soft diaphragm 17 in the axial direction. As a result, the stiffness against tilting is significantly reduced compared to known solutions of the state of the art, and thus the service life of the thrust bearing 3 is increased.

The lubricating oil includes a lubricating oil supply unit 10, a circumferential groove 31 provided in the bearing housing 5,
Via the supply part 32 of the radial bearing 2 formed correspondingly, it reaches the lubricating oil gap 33 of the radial bearing. The lubricating oil gap 34 of the radial bearing 1 or the thrust bearing 13
The lubricating oil is supplied to the rotating surface 14 through the lubricating oil supply unit 11 provided in the bearing flange 6.

In the second embodiment, since the hollow chamber 20 filled with the incompressible medium 23 is formed between the diaphragm 17 and the bearing flange 6, the bearing flange is
Form the elements that define Accordingly, a supply passage 22 for the medium 19 is provided in the bearing flange 6. Similarly, the bearing flange 6 is provided with an axial stop 24 for the central ring 18 of the diaphragm 17 instead of the lid 19 (FIG. 3). Lid 1
By omitting 9, almost the same function is achieved with a simple and low-cost structure.

[Brief description of the drawings]

FIG. 1 is a partial longitudinal sectional view of a bearing part of a shaft provided with two radial bearings and one thrust bearing together with a device for compensating a tilt position.

FIG. 2 is an enlarged view of a range of the thrust bearing of FIG. 1;

FIG. 3 is a view similar to FIG. 2 of a second embodiment.

[Explanation of symbols]

 REFERENCE SIGNS LIST 1 radial bearing 2 radial bearing 3 thrust bearing 4 shaft 5 bearing housing 6 bearing flange, element 7 fixing element, bolt 8 lid 9 fixing element, bolt 10 lubricating oil supply section in bearing housing 11 lubricating oil supply section in bearing flange 12 Bearing collar 13 Load introducing body 14 Rotating surface 15 Lubricating oil gap 16 Race body 17 Diaphragm 18 Central ring 19 Lid, element 20 Hollow chamber 21 Plug 22 Supply passage 23 Medium 24 Axial stopper 25 Central area of diaphragm 26 Edge area of diaphragm 27 Intermediate range of diaphragm 28 Recess 29 Fitting part of bearing flange and diaphragm 30 Fitting part of lid and diaphragm 31 Circumferential groove 32 Supply part 33 Lubricating oil gap of radial bearing 34 Lubricating oil gap of radial bearing

[Procedural Amendment] Submission of translation of Article 34 Amendment

[Submission date] March 20, 2001 (2001. 3.20)

[Procedure amendment 1]

[Document name to be amended] Statement

[Correction target item name] Claim 1

[Correction method] Change

[Contents of correction]

[Procedure amendment 2]

[Document name to be amended] Statement

[Correction target item name] 0005

[Correction method] Change

[Contents of correction]

However, such tilt compensation always requires a compromise between the required axial strength and the desired flexibility for tilt. Furthermore, a relatively large structural space is required in the axial direction. FIG. 10 of French Patent No. 1577608 (German Patent No. 1)
The self-aligning device for sliding bearings, which is shown in FIG. 10 of 775350 (corresponding to FIG. 10), corresponds to the device described in the generic concept of the invention. In this case, the compensation of the axial inclination is provided by a fluid-filled cavity and an elastic wall. This wall part defines a cavity and connects the two bearing parts which can tilt with respect to each other. Such tilt compensation also results in a low axial strength with respect to tilt flexibility and requires a large axial construction space.
Furthermore, it is technically difficult to completely fill the hollow chamber with the liquid without confining the gas and seal it without leakage. Furthermore, U.S. Pat. No. 5,121,143 discloses a bearing in which a diaphragm is supported on a rotating shoe, the rotating shoe being tapered towards the diaphragm.

[Procedure amendment 3]

[Document name to be amended] Statement

[Correction target item name] 0006

[Correction method] Change

[Contents of correction]

DISCLOSURE OF THE INVENTION The problem underlying the invention as claimed in the appended claims is an improved for high-speed rotors, which are very rigid in the axial direction and are formed very flexibly with respect to tilt. To provide a thrust bearing device. Furthermore, the axial construction space in the bearing area should be reduced and the production simple.

[Procedure amendment 4]

[Document name to be amended] Statement

[Correction target item name] 0007

[Correction method] Change

[Contents of correction]

In the case of the thrust bearing device according to the present invention, the load introducing body includes a central ring connecting the race body to the elastic wall portion, and the load introducing body is tapered from the race body toward the central ring. ing. The wall portion is supported on one side by an incompressible medium and is arranged between the bearing collar and the cavity filled with the incompressible medium and is formed as a diaphragm.

[Procedure amendment 5]

[Document name to be amended] Statement

[Correction target item name] 0008

[Correction method] Change

[Contents of correction]

[0008] By supporting the diaphragm on one side on an incompressible medium, the axial flexibility of the diaphragm is avoided, thereby providing a very rigid axial thrust bearing. The use of a very soft diaphragm in the axial direction, in particular, greatly reduces the torsional strength of the thrust bearing, so that the resulting tilt can be better compensated through such a diaphragm. As a result, the supporting force of the thrust bearing is guaranteed for a long period of time, and its life is prolonged.

[Procedure amendment 6]

[Document name to be amended] Statement

[Correction target item name] 0009

[Correction method] Change

[Contents of correction]

With the solution according to the invention, the required axial strength is maintained and the required axial construction space is reduced by a factor of about 3 compared to conventional tilt compensation.

[Procedure amendment 7]

[Document name to be amended] Statement

[Correction target item name] 0010

[Correction method] Change

[Contents of correction]

It is particularly advantageous if the load introducer is formed in one piece. This increases the wear resistance of the thrust bearing.

[Procedure amendment 8]

[Document name to be amended] Statement

[Correction target item name] 0011

[Correction method] Change

[Contents of correction]

[0011] The diaphragm has a central area connected to the central ring, an edge area connected to the element defining the hollow space, and an intermediate area, wherein the central area and the edge area are thicker than the intermediate area of the diaphragm. It is particularly advantageous if it is formed. By providing such a thickened area for receiving or transmitting the axial force of the machine, the life of the thrust bearing is further increased.

[Procedure amendment 9]

[Document name to be amended] Statement

[Correction target item name] 0012

[Correction method] Change

[Contents of correction]

It is furthermore advantageous if the element defining the cavity is provided with an axial stop for the central ring reaching the cavity. This stopper prevents the thrust bearing from breaking in case of breakage. In the case of this failure, a loss of the incompressible medium filled in the hollow chamber occurs. The stopper also acts as a hydraulic damper.

[Procedure amendment 10]

[Document name to be amended] Statement

[Correction target item name] 0013

[Correction method] Change

[Contents of correction]

[0013] Advantageously, the element defining the cavity is formed as a lid. This greatly simplifies fabrication and assembly.

[Procedure amendment 11]

[Document name to be amended] Statement

[Correction target item name] 0014

[Correction method] Change

[Contents of correction]

Next, the present invention will be described in detail based on embodiments.

[Procedure amendment 12]

[Document name to be amended] Statement

[Correction target item name] 0018

[Correction method] Change

[Contents of correction]

The load introducing body 13 is formed integrally. The load introducing body includes a race body (rotating surface body) 16 connected to the bearing collar 12 and the diaphragm 1 connected to the bearing flange 6.
7 and a central ring 18 connecting the lace body 16 to the diaphragm, and is formed to be tapered from the lace body 16 toward the central ring 18.

[Procedure amendment 13]

[Document name to be amended] Statement

[Correction target item name] 0019

[Correction method] Change

[Contents of correction]

On the opposite side of the load introducing body 13 from the race body 16, the lid 19 is provided with a diaphragm 17.
Between the cover 19 and the bearing flange 6 and between the lid 19 and the diaphragm 17
Are formed. Inside the lid 19 formed as an element defining the hollow chamber 20,
A supply passage 22 for an incompressible medium 23 filling the hollow chamber 20 is provided, which is closed by a stopper 21 in communication with the hollow chamber 20. Such a medium 23 is mainly a fluid, especially a synthetic oil. For this purpose, of course, other fluids such as water or solids (for example low-melting metals) are also suitable.

[Procedure amendment 14]

[Document name to be amended] Statement

[Correction target item name] 0020

[Correction method] Change

[Contents of correction]

The lid 19 is provided with an axial stop 24 for the central ring 18 reaching into the cavity 20. The diaphragm 17 has a central area 25 connected to the central ring 18, an edge area 26 connected to the bearing flange 6, and an intermediate area 27 (FIG. 2).
. Since the central area 25 and the edge area 26 are formed thicker than the intermediate area 27 of the diaphragm 17, the original diaphragm is formed by the intermediate area 27.

[Procedure amendment 15]

[Document name to be amended] Statement

[Correction target item name] 0021

[Correction method] Change

[Contents of correction]

The bearing flange 6 is provided with a recess 28 for accommodating the load introducing body 13, that is, the diaphragm 17. For this purpose, the bearing flange 6 in the range of the recess 28 is provided.
A fitting portion 29 is formed between the diaphragm and the diaphragm 17. A separately manufactured load introducing body 13 is press-fitted into the fitting portion. Similarly, the bearing flange 6 and the diaphragm 17 can be integrally connected. Other fitting part 30
Is formed between the lid 19 and the diaphragm 17. In this case, the connection is welded. Of course, other integral connections (eg, brazing), frictional connections, or shape-complementary connections can be made.

[Procedure amendment 16]

[Document name to be amended] Statement

[Correction target item name] 0022

[Correction method] Change

[Contents of correction]

The separately produced load introducer 13 is assembled before the lid 1 is assembled into the bearing flange 6.
9 and can be filled with an incompressible medium 23 in the hollow space. This allows for simple and low cost fabrication and final assembly. By using a tempered steel coated for the load introducer 13, great strength is obtained. An axial stopper 24 in the cavity 20 allows the incompressible medium 23
In the case of the loss, the axial strength of the thrust bearing 3 is prevented from being lost. By using a material with good emergency properties for the load introducer 13 (eg spring bronze), this safety concept can be further taken into account.

[Procedure amendment 17]

[Document name to be amended] Statement

[Correction target item name] 0023

[Correction method] Change

[Contents of correction]

During operation of the exhaust turbocharger, the axial thrust of the turbine, indicated by F1, is directed towards the radial bearing and urges the thrust bearing 3 mainly in the axial direction. In this case, the generated axial force is transmitted to the bearing flange 6 via the bearing collar 12, the race body 16, the center ring 18, and the diaphragm 17. By locally increasing the thickness of the central area 25 and the edge area 26 of the diaphragm 17, the transmission of force is facilitated. On the other hand, the flexibility of the diaphragm 17 in the axial direction is different from that of the incompressible medium 23.
Only a small elastic deflection in the range of one-tenth occurs, as it is prevented by being supported on (for example, pressurized oil). In the case of pulsating axial force, the incompressible medium 2
3 acts as an axial damper, thereby counteracting the increased axial force. Otherwise, this axial force will cause breakage. The inclination of the shaft 4 and thus the inclination of the bearing collar 12 of the thrust bearing 3, which occurs structurally or as a result of operation, is compensated for by a very soft diaphragm 17 in the axial direction. As a result, the stiffness against tilting is significantly reduced compared to known solutions of the state of the art, and thus the life of the thrust bearing 3 is increased.

Claims (8)

[Claims] 1. A device for tilt compensation, a rotating bearing collar (12) fixedly connected to a shaft (4) and a fixed load introducer (13), comprising a thrust bearing. A thrust bearing device for a high-speed rotor, wherein the load introducing body (13) is accommodated by a bearing flange (6), wherein the load introducing body (13) is connected to a bearing collar (12). (16), a diaphragm (17) connected to the bearing flange (6), and a center ring (18) connecting the race body (16) to the diaphragm (17). The body (16) is tapered from the body (16) towards the central ring (18), the diaphragm (17) being supported on one side by an incompressible medium (23) which is opposite the bearing collar (12). Die A hollow chamber (20) arranged on the side of the diaphragm (17) is filled, this hollow chamber being formed between the diaphragm (17) and the element (19) defining the hollow chamber (20), Thrust bearing device characterized in that the element (19) defining (20) is supported on or formed by a bearing flange (6). 2. The thrust bearing device according to claim 1, wherein the load introducing body (13) is formed integrally. 3. A central area (25) where the diaphragm (17) connects to the central ring (18) and an edge area (26) connected to the elements (19, 6) defining the cavity (20). And an intermediate area (27), wherein the central area (25) and the edge area (26) are formed thicker than the intermediate area (27) of the diaphragm (17). 3. The thrust bearing device according to 2. 4. An element (19, 6) defining a cavity (20) is provided with a cavity (2).
4. The thrust bearing device according to claim 3, wherein an axial stop (24) for the central ring (18) is provided, which extends into 0). 5. The thrust bearing device according to claim 4, wherein the element defining the hollow space is formed as a lid. 6. A thrust bearing device according to claim 1, wherein the incompressible medium is a fluid, in particular a synthetic oil. 7. The thrust bearing device according to claim 1, wherein the load introducing body is made of tempered steel having good fatigue strength. 8. The thrust bearing device according to claim 1, wherein the load introducing body is made of bronze having high strength and good emergency characteristics.