KR101873674B1 - Supercharger - Google Patents

Abstract

A centrifugal compressor having a bladed wheel connected to a rotating shaft, a bearing housing accommodating a bearing for supporting the rotating shaft so as to be freely rotatable, and opposed to a rear surface of the bladed wheel, A labyrinth seal formed between a back surface of the vane car and the bearing housing, the labyrinth seal including an annular labyrinth seal plate and a labyrinth seal plate integrally formed with the labyrinth seal plate; And heat transfer promoting means configured to promote heat transfer between the lubricant oil stored in the head tank and the labyrinth seal plate.

Description

Supercharger {SUPERCHARGER}

The present disclosure relates to a supercharger capable of suppressing a temperature rise of a rotating vane car.

The exhaust turbine turbocharger is a device for transferring compressed air to an internal combustion engine by rotating a centrifugal compressor by the power of an exhaust turbine driven by an exhaust gas discharged from an internal combustion engine. The compressed air in the centrifugal compressor blades becomes hot, and some of them return to the back side of the blades. In order to prevent this, a seal member such as a labyrinth seal is conventionally formed between the back surface of the vane car and the stop wall of the bearing housing.

In the narrow passage of the labyrinth seal, the leakage flow is heated by a strong shearing force by the stop wall of the bearing housing and the rear surface of the rotating blades, and becomes higher in temperature. As a result, the labyrinth seal becomes hot, and the heat of the labyrinth seal is transferred to the blade wheel, thereby raising the temperature of the back surface of the blade wheel.

As the material of the wing car, aluminum alloy is generally used at low cost and good machinability. However, in the present situation in which the centrifugal compressor is under high pressure, the temperature of the back surface of the blades increases, and centrifugal force due to rotation is applied to the blades, which may cause creep deformation of the blades.

Therefore, conventionally, various proposals have been made for cooling the blades during operation. For example, Japanese Patent Application Laid-Open Publication No. 2002-34870 discloses a structure in which a cooling lubricating oil is supplied to an upper portion of a compressor impeller-side shield plate disposed on the back surface of a vane car, and a cooling lubricating oil is supplied to a cooling space formed on a back surface of the compressor impeller- .

Patent Document 2 discloses a configuration in which a cooling water passage for circulating cooling water is formed in a circumferential direction in a portion of a bearing housing opposed to a back surface of a vane car.

Patent Document 3 discloses a configuration in which an annular space for supplying cooling air to a labyrinth seal is formed.

Japanese Patent Application Laid-Open No. 2008-248706 Japanese Laid-Open Patent Publication No. 2009-243299 Japanese Laid-Open Patent Publication No. 2012-082689

In the injection means disclosed in Patent Document 1, when only a part of the cooling lubricating oil supplied to the exhaust turbine turbocharger is sprayed on the upper portion of the compressor impeller-side shield plate and the upper portion of the compressor impeller- It is necessary to supply the cooling lubricant to the exhaust turbine turbocharger.

 In the means disclosed in Patent Documents 2 and 3, it is necessary to form a cooling space in the bearing housing or the labyrinth seal, and to form a passage for supplying cooling water or cooling air to the cooling space. As a result, the shape of the bearing housing or the labyrinth seal becomes complicated, and the manufacturing of the exhaust turbine turbocharger becomes costly.

At least one embodiment of the present invention aims to prevent the temperature rise of the impeller by means of a simple and low-cost means by using the lubricant temporarily stored in the head tank in view of the problems of the prior art.

(1) A supercharger according to at least one embodiment of the present invention,

A centrifugal compressor having a vane wheel connected to a rotating shaft,

A bearing housing accommodating a bearing for supporting the rotation shaft so as to be freely rotatable and opposed to a back surface of the vane;

A head tank formed in the bearing housing and configured to store a lubricating oil supplied to the bearing;

A labyrinth seal formed between a back surface of the vane car and the bearing housing, the labyrinth seal including an annular labyrinth seal plate and a labyrinth seal plate integrally formed with the labyrinth seal plate,

And heat transfer promoting means configured to promote heat transfer between the lubricant oil stored in the head tank and the labyrinth seal plate.

According to the structure (1), heat transfer between the labyrinth seal plate and the lubricating oil stored in the head tank can be promoted by the heat transfer promoting means. A large amount of lubricating oil is temporarily stored in the head tank, and a large amount of lubricating oil can be used to cool the labyrinth seal. Therefore, the temperature rise of the labyrinth seal can be suppressed by a simple and low-cost means. Thus, the temperature rise of the blades can be prevented, and the creep progress can be suppressed.

The " head tank " as used herein has a capacity capable of storing a sufficient amount of lubricating oil to be supplied to parts such as bearings of the turbocharger, which are different from the recesses, air gaps and passages,

In addition, since the labyrinth seal plate is cooled by the heat transfer between the lubricant oil stored in the head tank and the labyrinth seal plate, it is not necessary to form a passage for cooling water or cooling air. Therefore, it is possible to prevent the temperature of the labyrinth seal and the blades due to the simple and low-cost means from being raised, and to suppress creep propagation.

Further, in the case of a supercharger having a head tank, the heat transfer promoting means can be easily formed at a low cost without significantly changing the design.

(2) In some embodiments, in the above configuration (1)

The labyrinth seal plate contacts the head tank,

Wherein the heat transfer promoting means comprises:

And a concavo-convex portion formed on the inner surface of the head tank.

According to the structure (2), the surface area of the head tank contacted by the labyrinth seal plate can be enlarged by forming the concave-convex portion on the inner surface of the head tank, thereby promoting heat transfer between the wall and the lubricant. Therefore, the temperature rise of the labyrinth seal and the blades can be suppressed by the simple and low-cost means, and the creep progress of the blades can be suppressed.

(3) In some embodiments, in the above-mentioned configuration (2)

Wherein the concave-convex portion is constituted by a plurality of line-shaped projections disposed in parallel,

The plurality of line-shaped projections each extend along a horizontal direction.

According to the structure (3), the concavo-convex portion is formed by the line-shaped protrusions extending in the horizontal direction, and the lubricating oil to be lowered touches the line-shaped protrusions to form a turbulent flow. Thereby, since the lubricant is stirred, the heat transfer between the wall of the head tank and the lubricant can be promoted by the stirring effect. Therefore, the temperature rise of the labyrinth seal and the blades can be suppressed by the simple and low-cost means, and the creep progress of the blades can be suppressed.

(4) In some embodiments, in the configuration (2)

Wherein the concave-convex portion is constituted by a plurality of line-shaped projections disposed in parallel,

The plurality of line-shaped protrusions extend in the vertical direction.

According to the structure (4), since the projections and depressions are formed by the line-shaped projections extending in the vertical direction, the lubricant can smoothly flow along the line-shaped projections. Therefore, lubricating oil is smoothly supplied to the bearing and the like.

(5) In some embodiments, in the above configuration (1)

Wherein the heat transfer promoting means comprises:

And a heat radiating portion formed integrally with the labyrinth seal plate and protruding into the head tank and in contact with the lubricating oil.

According to the structure (5), the thermal conductivity between the labyrinth seal plate and the heat dissipating unit can be increased, thereby promoting heat transfer between the labyrinth seal plate and the lubricant. This makes it possible to suppress the temperature rise of the labyrinth seal and the bladed wheel by a simple and low-cost means, and to suppress the creep progress of the bladed wheel.

(6) In some embodiments, in any one of the configurations (1) to (4)

Further comprising a lubricant supply pipe for supplying lubricant to the head tank,

Wherein the heat transfer promoting means comprises:

And a lubricant supply port formed in a portion of the lubricant supply pipe extending inside the head tank and opened toward the wall of the head tank.

According to the structure (6), the lubricating oil supplied from the lubricating oil supply pipe into the head tank collides with the wall of the head tank to which the labyrinth seal plate contacts. Since the impinging flow of the lubricant destroys the temperature boundary layer of the lubricant formed on the surface of the wall of the head tank, the heat transfer between the wall of the head tank and the lubricant is promoted. Therefore, heating can be suppressed by raising the temperature of the labyrinth seal and the blades by a simple and low-cost means, and the creep progress of the blades can be suppressed.

(7) The supercharger according to at least one embodiment of the present invention,

A centrifugal compressor having a vane wheel connected to a rotating shaft,

A bearing housing accommodating a bearing for supporting the rotation shaft so as to be freely rotatable and opposed to a back surface of the vane;

A head tank formed in the bearing housing and configured to store a lubricating oil supplied to the bearing;

A labyrinth seal formed between a back surface of the vane car and the bearing housing, the labyrinth seal including an annular labyrinth seal plate and a labyrinth seal plate integrally formed with the labyrinth seal plate,

And an enlarged portion which is formed between the bearing housing and the labyrinth seal plate and has an arc-shaped space extending in an arc shape along the labyrinth seal plate and at least a part of which communicates with the inside of the head tank .

According to the structure (7), since the heat transfer area between the lubricant oil temporarily stored in the arc-shaped space formed in the enlarged portion and the labyrinth seal plate can be enlarged, heat transfer between the lubricant and the labyrinth seal plate is promoted . Therefore, the temperature rise of the labyrinth seal and the blades can be suppressed by the simple and low-cost means, and the creep progress of the blades can be suppressed.

(8) In some embodiments, in the above configuration (7)

An arc-shaped space extending in an arc shape along the labyrinth seal plate is formed in the inside of the bearing housing and the labyrinth seal plate, and at least a part of the arc-shaped space is communicated with the inside of the head tank.

The enlarged portion has an arc-shaped space extending in a C-shape inside.

According to the constitution (8), by extending the enlarged portion in a C-shape, heat transfer between the lubricant and the labyrinth seal plate can be further promoted.

(9) In some embodiments, in the configuration (7) or (8)

Further comprising a lubricant supply pipe for supplying lubricant to the head tank,

The lubricating oil supply pipe is connected to the enlarged portion.

According to the structure (9), since the lubricating oil of a relatively low temperature is supplied from the outside to the enlarged portion, the cooling effect of the labyrinth seal plate by the lubricating oil can be further enhanced.

(10) In some embodiments, in any one of the constitutions (7) to (9)

And a communication path formed in the bearing housing and extending between the enlarged portion and the bearing.

According to the structure (10), by forming the communication path, the flow velocity of the lubricating oil flowing through the enlarged portion can always be maintained at a predetermined level or higher. Therefore, heat transfer between the lubricant flowing in the arc-shaped space and the labyrinth seal plate can be promoted, and the cooling effect of the labyrinth seal plate can be improved.

(11) In some embodiments, in the configuration (7) or (8)

Wherein the enlarged portion has an opening facing the back surface of the vane car,

The labyrinth seal plate covers the opening of the enlarged portion.

According to the structure (11), since the enlarged portion has the opening opposed to the back surface of the vane car, the enlarged portion can be easily processed at a lower cost as compared with the case where the opening is not provided.

Further, since the labyrinth seal plate forms the wall surface of the arc-shaped space, the labyrinth seal plate is in direct contact with the lubricant oil, thereby further promoting the heat transfer between the labyrinth seal plate and the lubricant oil.

According to at least one embodiment of the present invention, the temperature rise of the labyrinth seal can be suppressed by a simple and low-cost means. Therefore, the temperature rise of the impeller can be suppressed, and the creep progress of the impeller can be suppressed.

1 is a perspective view of an exhaust turbine supercharger according to one embodiment.
2 is a longitudinal sectional view showing a heat transfer promoting means according to one embodiment.
3 is a longitudinal sectional view showing the heat transfer promoting means according to one embodiment.
4 is a longitudinal sectional view showing the heat transfer promoting means according to one embodiment.
5 is a longitudinal sectional view showing a heat transfer promoting means according to an embodiment.
6 is a longitudinal sectional view showing a heat transfer promoting means according to one embodiment.
Fig. 7 is a cross-sectional view taken along line AA in Fig. 6. Fig.
8 is a longitudinal sectional view showing a heat transfer promoting means according to an embodiment.
Fig. 9 is a cross-sectional view taken along line BB in Fig. 8. Fig.
10 is a partially enlarged sectional view showing a heat transfer promoting means according to an embodiment;

Hereinafter, some embodiments of the present invention will be described with reference to the accompanying drawings. However, the dimensions, materials, shapes, relative arrangements and the like of the constituent parts described in the embodiments or shown in the drawings are not intended to limit the scope of the present invention and are merely illustrative examples.

For example, expressions representing relative or absolute arrangements such as "in any direction," "along any direction," "parallel," "orthogonal," "center," "concentric," or "coaxial" Not only the arrangement but also a state in which the tolerance or the relative displacement is obtained as an angle or a distance to the extent that the same function is obtained.

For example, expressions indicating that objects such as " same ", " equivalent ", and " homogeneous " are equivalent represent not only strictly equivalent states, but also tolerances, .

For example, the expression indicating a shape such as a square shape or a cylinder shape not only shows a shape such as a square shape or a cylindrical shape in a geometrically strict sense, but also includes a concave portion and a chamfer portion in a range in which the same effect can be obtained And the like.

On the other hand, the expression "having," "having," "having," "including," or "having" is not an exclusive expression excluding the existence of other elements.

An embodiment in which the present invention is applied to a marine exhaust turbine turbocharger will be described with reference to Figs. 1 and 2. Fig. 1 is an overall perspective view of an exhaust turbine turbocharger 10 according to the present embodiment.

1, the exhaust turbine turbocharger 10 is constituted by a centrifugal compressor 11, a bearing 12, and an exhaust turbine 13. As shown in Fig.

The centrifugal compressor (11) has a compressor housing (14) and a vane car (18) housed in the compressor housing (14) while being fixed to the rotor shaft (16) And has a blade 18a.

The exhaust turbine 13 has a turbine housing 20 and a turbine disk 22 housed in the turbine housing 20 in a state fixed to the rotor shaft 16. The turbine disk 22 is provided with a plurality of turbine disks 22, The wings 23 are integrally formed.

The bearing portion 12 is provided with a bearing housing 24 and a bearing housing 24 capable of freely rotating the rotor shaft 16 at two points on the side of the centrifugal compressor 11 and the side of the exhaust turbine 13 in the bearing housing 24 And a thrust bearing 28 for supporting the rotor shaft 16 at one point on the side of the centrifugal compressor 11. The radial bearing 26 has a thrust bearing 28 for supporting the rotor shaft 16 at one point on the centrifugal compressor 11 side.

The compressor housing 14 has an inlet opening 14a that opens on the axis of the rotor shaft 16 and an outlet casing 14b that has an outlet opening that opens tangentially on the outer circumferential surface.

The turbine housing 20 has an inlet casing 20a having an inlet opening that opens in a tangential direction and an outlet opening 20b that opens on the axis of the rotor shaft 16.

The exhaust gas e introduced from the inlet opening of the inlet casing 20a rotates the turbine disk 22 and the rotor shaft 16 and flows out of the outlet opening 20b.

The blade wheel 18 is rotated by the rotation of the rotor shaft 16 and the air a is sucked from the inlet opening 14a by the rotation of the vane wheel 18 and is compressed, .

A head tank 30 configured to temporarily store lubricating oil is integrally formed on an upper portion of the bearing housing 24 above the rotor shaft 16. A lubricating oil supply pipe (32) is connected to the upper wall of the head tank (30). For example, a lubricating oil storage tank (not shown) for storing lubricating oil to be supplied to the internal combustion engine main body (not shown) and the exhaust turbine turbocharger 10 is formed outside the exhaust turbine turbocharger 10, And the lubricating oil is supplied to the internal combustion engine main body and the exhaust turbine turbocharger 10 through the system. The lubricating oil supplied to the exhaust turbine turbocharger 10 is supplied to the head tank 30 through the lubricating oil supply pipe 32 and temporarily stored in the head tank 30. [

A lubricating oil passage 34 is connected to the bottom of the head tank 30. The lubricant passage 34 passes through the radial bearing 26 and the thrust bearing 28 and communicates with the oil reservoir (not shown) formed in the bottom portion of the bearing housing 24.

The lubricating oil r that has fallen into the lubricating oil passage 34 through the opening 30a (see Fig. 2) formed in the bottom wall of the head tank 30 passes through the radial bearing 26 and the thrust bearing 28, And is supplied to the oil reservoir after lubricating the bearing. The lubricating oil dropped to the oil reservoir is returned from the outlet pipe 36 to the lubricating oil storage tank, and thereafter is subjected to a process such as cooling to be circulated. Therefore, the temporary storage of the lubricating oil r in the head tank 30 includes a state in which the lubricating oil r is flowing.

The head tank 30 is supplied to parts such as the radial bearing 26 and the thrust bearing 28 and supplies a sufficient amount of lubricating oil to cool them to a storage capacity, Liter (liter) capacity.

Next, a configuration in the vicinity of the centrifugal compressor 11 and the head tank 30 will be described based on Fig.

A plurality of vanes 18a are radially protruded from the outer circumferential surface of the hub of the vane car 18. The air a introduced from the inlet opening 14a by the rotation of the vane car 18 passes through the vane 18a and is compressed and thereafter the diffuser vane 18a formed in the flow passage downstream of the vane 18a And the dynamic pressure of the flow is converted to the rise of the static pressure.

The high-pressure air (a) is discharged from the outlet opening of the outlet casing 14b, and is supplied to the internal combustion engine main body as combustion air.

The bearing housing 24 has an annular partition wall facing the rear face 18b of the vane pulley 18 and having a clearance therebetween and the rotor shaft 16 penetrates the partition wall. The wall 30b of the head tank 30 on the side of the vane car 18 constitutes a part of the annular partition wall of the bearing housing 24 .

A labyrinth seal (40) is disposed between the partition wall of the bearing housing (24) and the impeller (18). The labyrinth seal 40 forms a labyrinth flow path fc which is narrowed down and suppresses a leakage flow flowing between the partition wall of the bearing housing 24 and the impeller 18.

The labyrinth seal 40 has a labyrinth pin 44 disposed at the peripheral edge of the back surface 18b of the vane wheel 18. [ The labyrinth pin 44 is formed integrally with the peripheral edge portion of the back surface 18b of the vane wheel 18 and is constituted by a plurality of annular protrusions which are separated from each other in the radial direction.

The labyrinth seal 40 has an annular labyrinth seal plate 42. The labyrinth seal plate 42 is fixed to the partition wall of the bearing housing 24 in a state where the back surface of the labyrinth seal plate 42 closely contacts the partition wall of the bearing housing 24 including the wall 30b of the head tank 30.

In the labyrinth seal plate 42, a labyrinth fin 46 is integrally formed. The labyrinth fin 46 is formed by a plurality of annular projections that are separated from each other in the radial direction and forms a labyrinth flow path fc between the labyrinth fin 44 and the labyrinth fin 44. [

The inner surface of the wall 30b of the head tank 30 to which the labyrinth seal plate 42 is fixed is provided with a recessed portion for enlarging the contact area with the lubricating oil r temporarily stored in the head tank 30 A plurality of linear projections 48 are formed. The plurality of linear projections 48 extend in the horizontal direction and are arranged in parallel with an interval in the vertical direction.

In this configuration, the head tank 30 is supplied with the lubricating oil r at a normal temperature from the lubricating oil storage tank and is temporarily stored. The heat of the air which has become hot when passing through the labyrinth flow path fc is transferred to the lubricating oil r stored in the head tank 30 through the labyrinth seal plate 42 and the wall 30b.

At this time, the line-shaped protrusion 48 is formed as the concave / convex portion on the inner surface of the wall 30b, and the contact area between the wall 30b and the lubricant oil r, that is, And the lubricant oil r. As a result, the temperature rise of the labyrinth seal 40 can be prevented, and the temperature rise of the vane wheel 18 can be suppressed, so that creep progression of the vane wheel 18 can be suppressed.

Particularly, since the line-shaped projections 48 are arranged along the horizontal direction, the lubricating oil r falling down in the head tank 30 touches the line-shaped projections 48 to form a turbulent flow. Thereby, the lubricating oil r is stirred. The temperature boundary layer around the linear projections 48 becomes thin due to the stirring effect and the heat transfer between the wall 30b of the head tank 30 and the lubricant oil r can be promoted.

Fig. 3 shows a modification of the embodiment. In this modified example, the plurality of line-shaped projections 50 formed on the wall 30b extend in the vertical direction and are arranged in parallel with an interval in the horizontal direction. The other configurations are the same as those of the above embodiment.

According to this modified example, since the linear projections 50 are arranged along the vertical direction, the lubricant oil r contacts the linear projections 50 to promote the heat transfer therebetween, and the lubricant oil r, The lubricant oil r is smoothly supplied to the radial bearing 26 and the thrust bearing 28, smoothly.

Next, another embodiment of the present invention will be described with reference to Fig. In this embodiment, a through hole 52 penetrating through the wall 30b is formed in place of the above-described linear projections 48 or 50, and on the back surface of the labyrinth seal plate 42, Like heat dissipating portion 54 protruding from the through-hole 52 to the inside of the head tank 30 is formed integrally with the heat dissipating portion 42 of the same material. The plate-shaped heat-radiating portions 54 are arranged along the horizontal direction. The wall 30b and the back surface of the labyrinth seal plate 42 are in close contact with each other in an oil tight manner so that the lubricating oil r is not leaked from the through hole 52 to the outside of the head tank 30. The other configurations are the same as those of the above embodiment.

The thermal conductivity between the labyrinth seal plate 42 and the heat dissipating portion 54 can be increased to a high level because the labyrinth seal plate 42 and the heat dissipating portion 54 are integrally formed of the same material And the heat transfer effect between the labyrinth seal plate 42 and the lubricant oil r can be improved. Since the radiator 54 is disposed along the horizontal direction in the head tank 30, the lubricant r falls down while contacting the radiator 54 when the lubricant r flows down into the opening 30a, The heat transfer effect between the portion 54 and the lubricant oil r can be improved.

In addition, the shape and size of the heat dissipating portion 54 are appropriately determined. For example, a plurality of through holes 52 extending in the horizontal direction may be formed in the wall 30b, and the heat dissipating portion 54 may be formed of a plurality of bars. In the through holes 52, May be inserted.

Next, another embodiment of the present invention will be described with reference to Fig. In the present embodiment, in the inside of the head tank 30, the tip end of the lubricating oil supply pipe 32 is provided (led) until it becomes flush with the wall 30b. The front end opening 32a of the lubricating oil supply pipe 32 is opposed (faces to the front) toward the wall 30b. The other configuration is the same as the configuration of the embodiment shown in Fig. 1 in which the line-shaped projections 48 are not formed.

In this configuration, the lubricating oil r supplied from the lubricating oil supply pipe 32 is injected into the wall 30b. The temperature boundary layer of the lubricating oil r formed on the surface of the wall 30b can be made thin by the impinging flow of the lubricating oil r so that the heat transfer between the wall 30b and the lubricating oil r can be promoted have. Therefore, the cooling effect of the air passing through the labyrinth flow path fc by the labyrinth seal plate 42 can be enhanced.

As a modification of the above embodiment, the opening of the lubricating oil supply pipe 32 disposed opposite to the wall 30b does not necessarily have to be formed at the tip of the lubricating oil supply pipe 32. [ For example, one or a plurality of openings may be formed on the side surface of the lubricating oil supply pipe 32.

Next, another embodiment of the present invention will be described based on Fig. 6 and Fig.

6, the exhaust turbine supercharger according to the present embodiment includes a centrifugal compressor 11, a bearing portion 12, and an exhaust turbine 13 in the same manner as the exhaust turbine turbocharger 10 shown in Fig. 1 have.

The centrifugal compressor (11) has a compressor housing (14) and a vane car (18) housed in the compressor housing (14) while being fixed to the rotor shaft (16) And has a blade 18a.

The head tank 30 is formed in the bearing housing 24 and configured to store the lubricating oil supplied to the radial bearing 26 and the thrust bearing 28. [ The labyrinth seal 40 is formed between the vane wheel 18 and the bearing housing 24 and includes a labyrinth pin 44 disposed at the peripheral edge of the back surface 18b of the vane wheel 18, And a pin 46 is integrally formed with a labyrinth seal plate 42. That is, the heat exchanger has the same configuration as that of the embodiment shown in Fig.

The enlarged portion in the present embodiment is formed between the bearing housing 24 and the labyrinth seal plate 42 and has an arc-shaped space Sr extending in an arc shape along the labyrinth seal plate 42 And a part of the arc-shaped space Sr is communicated with the inside of the head tank 30. The arc-shaped space Sr is formed in the partition wall of the rear wall of the bearing housing 24 facing the wall 30b of the rear wall of the head tank 30 and the rear wall 18b of the blade wheel 18, (42).

As shown in Fig. 7, the arc-shaped space Sr has a C-shape in the cross section perpendicular to the rotor axis 16, and the lubricating oil supply pipe 32 communicates with one end of the arc-shaped space Sr, The other end of the arc-shaped space Sr communicates with the head tank 30 through a communication hole 56. [ The back surface of the annular labyrinth seal plate 42 is disposed in close contact with the wall 30b of the head tank 30 and the partition wall of the bearing housing 24 as in the above embodiment.

In this configuration, the lubricating oil r is directly supplied to the arc-shaped space Sr from the lubricating oil supply pipe 32. The lubricating oil r supplied to the arc-shaped space Sr circulates in the arc-shaped space Sr and flows into the head tank 30 from the communication hole 56.

According to the present embodiment, the relatively low-temperature lubricating oil r before being supplied to the main body of the head tank 30 can be directly supplied to the arc-shaped space Sr as the enlarged portion of the head tank 30, The cooling effect of the rinse seal plate 42 can be further enhanced.

The heat of the labyrinth seal plate 42 is transmitted to the lubricating oil r flowing in the arc-shaped space Sr through the partition walls of the bearing housing 24 in the substantially entire circumferential direction so that the wall 30b and the bearing The contact area of the housing 24 with the partitions can be increased. Therefore, heat transfer between the labyrinth seal plate 42 and the lubricant oil r can be promoted.

The lubricating oil r flows into the arc space Sr from the lubricating oil supply pipe 32 and flows out to the main body of the head tank 30 through the communication hole 56. [ Therefore, the lubricating oil r in the arc-shaped space Sr has a larger flow velocity than the lubricating oil r in the head tank 30. This can further promote the heat transfer between the labyrinth seal plate 42 and the lubricant oil r.

Next, another embodiment of the present invention will be described with reference to Figs. 8 and 9. Fig.

This embodiment is characterized in that, in the same manner as the embodiment shown in Figs. 6 and 7, the partition wall of the bearing housing 24 including the wall 30b of the rear wall of the head tank 30 is provided with a C- Is formed. One end of the arc-shaped space Sr constituting the enlarged portion of the head tank 30 communicates with the main body of the head tank 30 through the communication hole 56. The other end of the arc- And communicates with the lubricant oil passage 34 through the oil passage 58. The other configurations are the same as those of the embodiment shown in Figs.

In the present embodiment, the lubricating oil r supplied to the main body of the head tank 30 flows into the arc-shaped space Sr as the enlarged portion, and after approximately circulating the arc-shaped space Sr, (Not shown).

According to the present embodiment, since the lubricating oil r supplied to the main body of the head tank 30 flows out to the lubricating oil passage 34 through the communication hole 56 and the arc-shaped space Sr, The flow rate of the lubricating oil flowing in the space Sr can always be maintained at a predetermined level or higher. Therefore, the heat transfer of the lubricating oil flowing through the arc-shaped space Sr and the labyrinth seal plate 42 can be promoted, and the cooling effect of the labyrinth seal plate 42 can be improved.

Next, another embodiment of the present invention will be described with reference to Fig.

In the present embodiment, the arc-shaped space Sr has an annular opening 60 opened to the labyrinth seal plate 42 side. An annular fitting wall 42a which is fitted to the annular opening 60 from the back surface of the labyrinth seal plate 42 is projected. In the present embodiment, the enlarged portion has an annular fitting wall 42a, and the annular opening 60 is closed.

That is, the annular fitting wall 42a has a step with respect to the back surface of the labyrinth seal plate 42, has the same thickness throughout the entire back surface, and has a flat surface. The annular fitting wall 42a is fitted in the annular opening 60, and the space between them is in an oil-tight state. The other configurations are the same as those of the embodiment shown in Figs.

According to the present embodiment, since the arc-shaped space Sr has the annular opening 60, the machining of the arc-shaped space Sr can be facilitated and reduced in cost as compared with the case where the annular opening 60 is not provided .

Since the annular fitting wall 42a integrally formed with the labyrinth seal plate 42 is in direct contact with the lubricating oil r introduced into the arc-shaped space Sr, the labyrinth seal plate 42 and the lubricant r Lt; RTI ID = 0.0 > heat transfer < / RTI >

In addition, in some of the above embodiments in which the arc-shaped space Sr is formed, the arc-shaped space Sr may not necessarily extend over the entire circumferential direction. At least, an enlarged portion forming the arc-shaped space Sr may be formed on the wall 30b of the head tank 30. [

Industrial availability

According to at least one embodiment of the present invention, temperature rise of the labyrinth seal formed on the back surface of the vane car can be suppressed by a simple and low-cost means, for example, in an exhaust turbine turbocharger formed in an internal combustion engine for a ship . Therefore, it is possible to suppress the temperature rise of the impeller and suppress the creep deformation of the impeller.

10: exhaust turbine supercharger
11: Centrifugal compressor
12: Bearing part
13: Exhaust turbine
14: Compressor housing
14a: entrance opening
14b: outlet casing
16: Rotor shaft
18: Wing tea
18a: Wings
18b:
20: Turbine housings
22: Turbine disk
23: turbine blade
24: Bearing housing
26: Radial bearing
28: Thrust bearing
30: head tank
30a: bottom opening
30b: wall
32: Lube oil supply pipe
34: Lubricant passage
36: Exit piping
40: labyrinth seal
42: Labyrinth seal plate
42a: annular fitting wall
44, 46: labyrinth pin
48, 50:
52: Through hole
54:
56: communication hole
58:
60: annular opening
Sr: Circular arc space (enlarged part)
a: air
e: Exhaust gas
fc: labyrinth seal oil flow
r: lubricant

Claims (11)

A centrifugal compressor having a vane wheel connected to a rotating shaft,
A bearing housing accommodating a bearing for supporting the rotation shaft so as to be freely rotatable and opposed to a back surface of the vane;
A head tank formed in the bearing housing and configured to store a lubricating oil supplied to the bearing;
A labyrinth seal formed between a back surface of the vane car and the bearing housing, the labyrinth seal including an annular labyrinth seal plate and a labyrinth seal plate integrally formed with the labyrinth seal plate,
And a heat transfer promoting means configured to promote heat transfer between the lubricant oil stored in the head tank and the labyrinth seal plate. The method according to claim 1,
The labyrinth seal plate contacts the head tank,
Wherein the heat transfer promoting means comprises:
And an uneven portion formed on the inner surface of the head tank. 3. The method of claim 2,
Wherein the concave-convex portion is constituted by a plurality of line-shaped projections disposed in parallel,
And the plurality of line-shaped projections extend along a horizontal direction, respectively. 3. The method of claim 2,
Wherein the concave-convex portion is constituted by a plurality of line-shaped projections disposed in parallel,
And the plurality of line-shaped projections extend along the vertical direction, respectively. The method according to claim 1,
Wherein the heat transfer promoting means comprises:
And a heat dissipating portion formed integrally with the labyrinth seal plate and protruding into the head tank and in contact with the lubricating oil. 5. The method according to any one of claims 1 to 4,
Further comprising a lubricant supply pipe for supplying lubricant to the head tank,
Wherein the heat transfer promoting means comprises:
And a lubricating oil supply port formed in a portion of the lubricating oil supply pipe extending inside the head tank and opened toward a wall of the head tank. A centrifugal compressor having a vane wheel connected to a rotating shaft,
A bearing housing accommodating a bearing for supporting the rotation shaft so as to be freely rotatable and opposed to a back surface of the vane;
A head tank formed in the bearing housing and configured to store a lubricating oil supplied to the bearing;
A labyrinth seal formed between a back surface of the vane car and the bearing housing, the labyrinth seal including an annular labyrinth seal plate and a labyrinth seal plate integrally formed with the labyrinth seal plate,
And an enlarged portion which is formed between the bearing housing and the labyrinth seal plate and has an arc-shaped space extending in an arc shape along the labyrinth seal plate, and at least a part of which is in communication with the inside of the head tank Characterized in that it is a supercharger. 8. The method of claim 7,
An enlarged portion formed between the bearing housing and the labyrinth seal plate and having an arc-shaped space extending in an arc shape along the labyrinth seal plate, the enlarged portion at least partially communicating with the inside of the head tank, And an arc-shaped space extending in a C-shape is formed inside the supercharger. 9. The method according to claim 7 or 8,
Further comprising a lubricant supply pipe for supplying lubricant to the head tank,
And the lubricating oil supply pipe is connected to the enlarged portion. 9. The method according to claim 7 or 8,
And a communication passage formed in the bearing housing and extending between the enlarged portion and the bearing. 9. The method according to claim 7 or 8,
Wherein the enlarged portion has an opening facing the back surface of the vane car,
And the labyrinth seal plate covers the opening of the enlarged portion.

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