JP2002070847A - Thrust bearing - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve durability of thrust bearing by accommodating a thrust load of a rotating shaft appropriately. SOLUTION: A thrust collar 51 is installed on the rotating shaft 15 upon which a turbine 19 and a compressor 20 of a super charger 10 are mounted on both ends thereof, and on the other hand a bearing plate 44 is supported freely movable in axial direction in a support member 41 through which the rotating shaft 15 penetrates, a coned disc spring 50 interposed between the support member 41 and the bearing plate 44 urges the bearing plate 44 to press the thrust collar 51.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a thrust bearing for supporting a rotating shaft while receiving a load acting in an axial direction.

[0002]

2. Description of the Related Art A marine diesel engine, for example, is equipped with a turbocharger as a device for increasing its output because its fuel efficiency is good, but its output is low and it is weak even at high revolutions. This turbocharger guides the exhaust gas from the diesel engine to the blades of the turbine, turns the turbine with the gas flow, and turns the compressor installed on the same axis as the turbine, thereby compressing the intake air and burning the engine. It is sent to the room. As described above, the turbocharger can collect the exhaust energy that has been randomly discarded, thereby contributing to energy saving and increasing the output.

In this turbocharger, generally, a turbine is fixed to one end of a rotating shaft, while a compressor is fixed to multiple ends, and the rotating shaft is rotatably supported by a casing by a thrust bearing. An exhaust gas introduction passage for guiding exhaust gas to the turbine is connected to the casing, an exhaust gas exhaust passage is connected to the casing, and a suction air passage is connected to the compressor to the casing, and the intake air is supplied to the engine. Are connected to an air supply passage for supplying air to the combustion chamber.

Accordingly, the exhaust gas from the diesel engine is guided to the turbine through the exhaust gas introduction passage, rotates the turbine, and is discharged from the exhaust gas discharge passage.
By rotating a compressor provided on the same axis as the turbine, the air sucked from the intake air passage is compressed, and the compressed air can be sent to the combustion chamber through the air supply passage, increasing the output of the diesel engine. Becomes possible.

[0005]

In such a turbocharger, high-pressure exhaust gas acts on the turbine when the diesel engine is operating at high speed and high load, so that the turbine is located on the opposite side of the exhaust gas introduction passage. For example, it is pressed with a large force on the compressor side along the axial direction of the rotating shaft. In this case, when the collar integral with the rotating shaft slides on the thrust bearing fixed to the casing side, the thrust bearing receives the load in the axial direction.

However, the stress of the exhaust gas acting on the turbine changes depending on the operation state (rotation speed) of the diesel engine, and the rotation shaft of the turbine moves in the axial direction while vibrating. For this reason, the rotating shaft may be inclined and the collar may hit the thrust bearing in one direction. Then, the thrust bearing receives the thrust load of the rotating shaft by a part thereof, and the thrust bearing and the collar are partially worn or damaged, so that the thrust bearing cannot properly support the rotating shaft. In addition, due to a manufacturing error of the thrust bearing and the rotating shaft (collar), a mounting error of the turbocharger, and the like, the rotating shaft may be tilted and the collar may hit against the thrust bearing. Partial wear and damage of the thrust bearing and collar occur.

An object of the present invention is to solve such a problem, and an object of the present invention is to provide a thrust bearing in which durability is improved by properly receiving a thrust load of a rotating shaft.

[0008]

According to a first aspect of the present invention, there is provided a thrust bearing for supporting a rotary shaft while receiving a load acting in an axial direction, wherein the rotary shaft is A support member that penetrates, a bearing plate movably supported by the support member along the axial direction, and a biasing force that presses the bearing plate against the support member against an end surface of the flange portion of the rotary shaft. And a biasing member.

In the thrust bearing according to the second aspect of the present invention, a lubricating oil supply hole is formed so as to penetrate from the support member through the bearing plate and penetrate a contact surface between the bearing plate and the flange of the rotary shaft. It is characterized by that.

The thrust bearing according to the third aspect of the present invention is characterized in that a rotary shaft having a turbine and a compressor in a turbocharger attached to ends thereof is supported.

[0011]

Embodiments of the present invention will be described below in detail with reference to the drawings.

FIG. 1 shows a cross section of a thrust bearing according to one embodiment of the present invention, and FIG. 2 shows a cross section of a supercharger to which the thrust bearing of this embodiment is applied.

As shown in FIG. 2, in a supercharger 10 to which the thrust bearing of the present embodiment is applied, a casing 11
The first casing 12 in the center, the second casing 13 on the turbine side, and the third casing 14 on the compressor side are integrally fastened by bolts. The rotating shaft 15 is rotatably supported in the first casing 12 by a thrust bearing 16 and radial bearings 17 and 18, and a turbine 19 is fixed to one end and a compressor 20 is fixed to a multi-end. I have.

The turbine 19 has a large number of blades 19a on its outer periphery. The blades 19a are connected to the exhaust gas introduction passage 21 and the exhaust gas exhaust passage 2 of the second casing 13.
Inscribed in 2. Reference numeral 23 denotes a connection portion to which a branch pipe from an exhaust pipe (not shown) of the diesel engine is connected. On the other hand, the compressor 20 has a large number of blades 20 a on the outer peripheral portion, and the blades 20 a are inscribed in the intake air introduction passage 24 of the third casing 14, and the intake air introduction passage 24 passes through the compressor 20. The swirling chamber 25 is connected to a combustion chamber of the engine via an intake air supply passage (not shown). Reference numeral 26 denotes a filter which rectifies the intake air by passing the intake air before being taken into the intake air introduction passage 24.

Further, a lubricating oil supply passage 27 is formed in the first casing 12, and a base end of the lubricating oil supply passage 27 is connected to an oil pump of the engine, while a multi-end is formed of three branch passages. The thrust bearing 16 and the radial bearings 17, 18 are connected via 28, 29, 30 to supply lubricating oil to the bearings 16, 17, 18.

Further, a seal member 31 is attached to the end of the first casing 12 on the side of the turbine 19 so as to extend over the second casing 13, and the seal member 31 slides on the turbine 19 so that the exhaust gas is exhausted. Leakage is prevented. On the other hand, a seal member 32 is attached to an end of the first casing 12 on the compressor 20 side, and the seal member 32 slides against the compressor 20 to prevent leakage of intake air.

Further, the side opposite to the exhaust gas introduction side in the turbine 19, that is, the turbine 19 and the seal member 3
Air chamber 33 having a ring shape at a position defined by 1
The first casing 12 has an air passage 34 formed from the spiral chamber 25 on the compressor 20 side to the air chamber 33. This air passage 3
A vacuum breaker, which is connected to an open air passage (not shown) and is opened and closed by the compressor 20 in accordance with the pressure of the supplied air, is attached to 4.

By the way, the thrust bearing 16 of this embodiment is
In this case, the thrust load of the rotating shaft 15 can be properly received even if the rotating shaft 15 is tilted due to vibration, manufacturing error, assembly error, or the like. That is, in the thrust bearing 16, as shown in FIG. 1, the support member 41 bolted to the first casing 12 has a ring shape in which a through hole 42 through which the rotating shaft 15 penetrates is formed in a central portion, and has an outer periphery. An outer peripheral wall 43 is formed in the portion along the circumferential direction. The bearing plate 44 has a ring shape in which a through hole 45 through which the rotary shaft 15 penetrates is formed at the center, and is housed inside the support member 41. The bearing plate 44 holds the pressing member 4 fixed by bolts 46 along the outer peripheral wall 43 of the support member 41.
7, and is supported by a regulating pin 49 so that it cannot rotate relative to the support member 41. A disc spring 50 as an urging member is interposed in the gap 48 to urge the bearing plate 44 against the support member 41 in one axial direction of the rotating shaft (to the right in FIG. 1). ing.

On the other hand, a ring-shaped thrust collar 51 as a flange portion is integrally formed on the rotary shaft 15, and the end face of the thrust collar 51 and the bearing plate 44 urged and supported by the disc spring 50 are supported. Plate 52
Is in contact through. Further, the lubricating oil supply holes 53 (43 a, 47 a, 44) penetrate from the outer peripheral wall 43 of the support member 41, penetrate the pressing member 47, the bearing plate 44, and penetrate the contact surface between the bearing plate 44 and the support plate 52.
The lubricating oil supply hole 53 communicates with the branch passage 28.

In the turbocharger 10 configured as described above, when the exhaust gas from the diesel engine is guided to the turbine 19 through the exhaust gas introduction passage 21 of the supercharger 10, as shown in FIG. The turbine 19 is rotated by the gas flow of the gas, and the exhaust gas is discharged from the exhaust gas discharge passage 22. Then, the turbine 19 and the rotating shaft 15
The compressor 20 integrally provided on the same axis rotates through the filter, and the air passes through the filter 26 and the intake air introduction passage 2
4 and is swirled into the swirl chamber 2 by the compressor 20.
5, and the compressed air is sent into the combustion chamber of the engine through the intake air supply passage, so that the output of the diesel engine can be increased.

At this time, in the thrust bearing 16, the bearing plate 44 presses the thrust collar 51 of the rotating shaft 15 via the support plate 52 by the urging force of the disc spring 50 to receive the thrust load of the rotating shaft 15. I have. Therefore, the pressure fluctuation of the exhaust gas acting on the turbine, the thrust bearing 16, and the thrust collar 51 of the rotating shaft 15.
Even if the rotating shaft 15 is tilted due to a manufacturing error, an assembly error, or the like, the bearing plate 44 is pressed via the support plate 52 and tilts following the tilt of the thrust collar 51. As a result, no one-side contact occurs on the contact surface between the thrust collar 51 and the bearing plate 44. Therefore, the thrust bearing 16 appropriately receives the thrust load of the rotating shaft 15 as a whole, and partial wear and damage of the thrust bearing 16 and the thrust collar 51 can be prevented, and the durability can be improved.

Further, the lubricating oil is supplied from the lubricating oil supply passage 27 to the thrust bearing 16 and the radial bearings 17 and 18 via the respective branch passages 28, 29 and 30.
6, the lubricating oil supply holes 53 (43a, 43a,
47a, 44a), it is surely supplied between the bearing plate 44 and the thrust collar 51. In this regard, the wear of the thrust bearing 16 and the thrust collar 51 is suppressed, and the durability can be improved. .

As described above, in the turbocharger according to the present embodiment, the turbocharger 10
A thrust collar 51 is provided on a rotating shaft 15 having an end mounted at the end thereof, and a thrust bearing 16 is supported in a support member 41 through which the rotating shaft 15 passes so that a bearing plate 44 is movably supported in the axial direction. A disc spring 50 is interposed between the member 41 and the bearing plate 44 so as to urge the bearing plate 44 against the thrust collar 51.

Therefore, even if the rotating shaft 15 is inclined,
With the inclination of the thrust collar 51, the bearing plate 44 follows and inclines, so that the thrust collar 51 and the bearing plate 44 do not hit each other, and the thrust bearing 16 appropriately adjusts the thrust load of the rotating shaft 15 as a whole. Therefore, partial wear and damage of the thrust bearing 16 and the thrust collar 51 are prevented.

In the embodiment described above, the thrust bearing of the present invention is applied to a supercharger mounted on a marine diesel engine, but may be a supercharger for a gasoline engine for a vehicle. Not only the feeder, but also a structure that supports the rotating shaft while receiving a load acting in the axial direction,
It can be applied as appropriate.

[0026]

As described above, according to the thrust bearing of the first aspect of the present invention, the bearing plate is supported by the support member through which the rotating shaft passes so as to be movable in the axial direction. The bearing plate is pressed against the end face of the flange portion of the rotary shaft by the member, so that even if the rotating rotary shaft is inclined, the bearing plate is tilted with the inclination of the flange portion. As a result, the flange and the bearing plate do not contact each other, and the thrust bearing properly receives the thrust load of the rotating shaft as a whole. Damage is prevented and durability can be improved.

According to the thrust bearing of the second aspect of the present invention, the lubricating oil supply hole is formed so as to penetrate through the bearing plate from the support member and penetrate the contact surface between the bearing plate and the flange portion of the rotating shaft. Lubricating oil is reliably supplied to the thrust bearing through the lubricating oil supply hole, so that abrasion of the thrust bearing is suppressed and durability can be improved.

According to the thrust bearing of the third aspect of the present invention, since the thrust bearing supports the rotary shaft of the turbocharger having the turbine and the compressor attached to the ends, the thrust bearing and the rotary shaft Partial wear and damage are prevented, the thrust load on the rotating shaft is properly received, and the rotating shaft is smoothly rotated, so that the intake air compression efficiency of the turbocharger can be improved.

[Brief description of the drawings]

FIG. 1 is a sectional view of a thrust bearing according to one embodiment of the present invention.

FIG. 2 is a cross-sectional view of a supercharger to which the thrust bearing of the present embodiment is applied.

[Explanation of symbols]

 Reference Signs List 10 supercharger 11 casing 15 rotating shaft 16 thrust bearing 19 turbine 20 compressor 27 lubricating oil supply passage 28 branch passage 41 support member 44 bearing plate 47 holding member 49 regulating pin 50 disc spring (biasing member) 51 thrust collar (flange portion) ) 53 Lubricating oil supply hole

Claims (3)

[Claims] 1. A thrust bearing for supporting a rotary shaft while receiving a load acting in an axial direction, wherein the support member has the rotary shaft penetrating therethrough, and the bearing is movably supported in the axial direction by the support member. A thrust bearing, comprising: a plate; and a biasing member that biases the bearing plate against the end surface of the flange portion of the rotating shaft against the support member. 2. The thrust bearing according to claim 1, wherein
A thrust bearing, wherein a lubricating oil supply hole is formed from the support member so as to penetrate the bearing plate and penetrate a contact surface between the bearing plate and a flange portion of the rotating shaft. 3. A thrust bearing according to claim 1, wherein the thrust bearing supports a rotary shaft having a turbocharger and a compressor mounted at ends thereof in a supercharger.