JP6503586B1 - Turbocharger - Google Patents

Abstract

To reliably supply lubricating oil from a head tank to a bearing. A supercharger 1A includes a rotating shaft 2, a turbine wheel, a compressor wheel, a thrust disk 20, a stationary disk 30 facing the thrust disk 20 in the central axis O direction, and a thrust disk 20. A header tank 40 for storing lubricating oil to be supplied to the gap with the stationary disk 30, a pump 41 for feeding lubricating oil into the header tank 40, and supplying lubricating oil from the header tank 40 to the gap between the thrust disk 20 and the stationary disk 30 Lubricating oil supply passage 33, a communication pipe 42 for connecting the inside and the outside of the header tank 40, an air introduction pipe 43 for introducing air from the outside into the header tank 40, and an air introduction pipe 43 The check valve 4 opens only when the pressure of the air in the tank 40 becomes smaller than the pressure of the air outside the header tank 40 And, equipped with a. [Selected figure] Figure 2

Description

  The present invention relates to a turbocharger.

  Some superchargers used for a main ship of a ship, a large generator, etc. have a head tank for storing lubricating oil supplied to bearings. The head tank is generally disposed above the bearing. The lubricating oil is externally supplied to the head tank through the lubricating oil supply pipe, and is supplied to the bearing from the head tank.

  For example, if the pump for supplying lubricating oil to the head tank is stopped for some reason, the lubricating oil in the head tank flows back from the head tank to the supply pipe, and the lubricating oil is not supplied to the bearings. There was a possibility of

  Therefore, in the head tank described in Patent Document 1, a check valve is provided at the lubricating oil inlet, and only the flow of oil from the lubricating oil supply pipe toward the head tank is permitted by the check valve. The check valve described in Patent Document 1 is pushed open by the lubricating oil fed from the lubricating oil supply pipe to the head tank during operation of the pump. Therefore, if the pump is stopped during operation of the supercharger and the supply of lubricating oil to the head tank is not performed, the check valve is closed to reduce the backflow of the lubricating oil from the head tank to the lubricating oil supply pipe it can.

Japanese Utility Model Application Publication No. 4-121431

However, according to Patent Document 1, even if the supercharger normally operates without stopping the pump, if the check valve is closed for some reason, the supply of lubricating oil from the lubricating oil supply pipe to the head tank is It will not be done. Then, there is a possibility that lubricating oil runs short in the bearing.
This invention is made in view of the said situation, and it aims at providing the supercharger which can perform supply of the lubricating oil from a head tank to a bearing reliably.

The present invention adopts the following means in order to solve the above problems.
According to a first aspect of the present invention, a turbocharger includes a rotating shaft rotatably supported around a central axis, a turbine wheel provided on a first end side of the rotating shaft, and a rotating wheel of the rotating shaft. A compressor wheel provided at the second end side, a thrust disk extending radially outward from the rotation shaft and rotating integrally with the rotation shaft, and a stationary disk facing the thrust disk in the central axis direction A header tank for storing lubricating oil supplied to the gap between the thrust disk and the stationary disk, a pump for feeding the lubricating oil into the header tank, and lubrication for supplying the lubricating oil to the gap from the header tank The oil supply passage is communicated with the inside and the outside of the header tank, and the air in the header tank is made to the outside as the oil amount of the lubricating oil in the header tank fluctuates. A communicating section which put to, the interior of the header tank the communication unit causes communicate with the outside, an air introduction section for introducing air from the outside of the header tank, provided in said air inlet portion, the said communicating portion The level of the lubricating oil in the header tank becomes higher than the opening in the header tank, and the lubricating oil flows into the communicating portion to block the communication by the communicating portion, thereby causing the communicating portion to communicate with the outside. And a check valve which opens only when the pressure of air inside the header tank becomes smaller than the pressure of air outside the header tank.

With this configuration, during normal operation of the supercharger, the communication unit communicates between the inside and the outside of the header tank. Therefore, even if the amount of lubricating oil in the header tank fluctuates, The pressure of the air does not change. As a result, a pressure equivalent to the pressure outside the header tank acts on the lubricating oil in the header tank, and the supply of the lubricating oil from the header tank to the gap between the thrust disk and the stationary disk is stably performed.
During operation of the supercharger, if the pump is stopped for any reason, the feed of lubricating oil from the pump to the header tank will not be performed. At this time, if the level of the lubricating oil in the header tank is higher than the opening in the header tank of the communication portion, the lubricating oil flows into the communication pipe, and the communication between the inside and the outside of the header tank through the communication pipe is blocked. May be In this state, when the level of lubricating oil in the header tank decreases, the pressure of air in the header tank decreases. Then, the non-return valve provided in the air introduction part opens. Thus, air is introduced into the header tank from the outside of the header tank through the air introduction unit. As a result, it is suppressed that the pressure of the air in the header tank is excessively reduced, and even if the pump is stopped during operation of the supercharger, lubrication from the header tank to the gap between the thrust disc and the stationary disc The oil supply can be performed stably.

According to the second aspect of the present invention, the stationary disk according to the first aspect has a flat surface orthogonal to the central axis on the side facing the thrust disk, and the thrust disk is the flat of the stationary disk. A tapered land may be provided on the side opposite to the surface.
In general, in the case where the thrust disk has a tapered land, when the air is sucked from the inside in the radial direction of the gap between the thrust disk and the stationary disk, the sucked air spreads radially outward by the centrifugal force due to the rotation of the rotation shaft. Then, the lubricating oil to the gap between the thrust disk and the stationary disk is also likely to flow radially outward. On the other hand, in the configuration in which the thrust disk has the tapered land, the header tank is provided with the air introduction portion and the check valve, so that the thrust from the header tank is caused even when the pump is stopped during the operation of the turbocharger. The lubricating oil can be stably supplied to the gap between the disk and the stationary disk.

According to the third aspect of the present invention, the lubricating oil supply passage according to the second aspect is opened to the flat surface of the stationary disk, and a supply port for supplying the lubricating oil to the gap; The flat plate may have an outer peripheral hole opened radially outward of the supply port and having a smaller opening area than the supply port.
With this configuration, when the turbocharger is operating normally, the lubricating oil fed from the header tank through the lubricating oil supply path is supplied from the supply port to the gap between the thrust disc and the stationary disc. In this case, since the outer peripheral hole has a smaller opening area than the supply port, the lubricating oil fed from the header tank through the lubricating oil supply passage mainly flows out from the supply port.
If the pump is stopped during operation of the supercharger and air is drawn from the inside in the radial direction of the gap between the thrust disk and the stationary disk, it becomes difficult to supply lubricating oil from the supply port, but at this time the supply port The lubricating oil is supplied from the header tank to the gap between the thrust disk and the stationary disk through the outer peripheral hole provided radially outward.

According to a fourth aspect of the present invention, in the turbocharger according to the third aspect, the flat surface of the stationary disk is formed with a recess continuous from the outer peripheral hole along the flat surface. It is also good.
With this configuration, the lubricating oil supplied to the gap between the thrust disk and the stationary disk through the outer peripheral hole passes through the recess and efficiently spreads in the gap between the thrust disk and the stationary disk. Thus, the lubricating oil can be more reliably supplied to the gap between the thrust disk and the stationary disk.

According to the fifth aspect of the present invention, the recess according to the fourth aspect may extend radially outward of the central axis from the outer peripheral hole.
With this configuration, the lubricating oil supplied through the outer peripheral hole efficiently spreads radially outward in the gap between the thrust disk and the stationary disk through the recess. Thus, the lubricating oil can be more reliably supplied to the gap between the thrust disk and the stationary disk.

According to the sixth aspect of the present invention, the stationary disk according to any one of the first to fifth aspects is opposed to the outer peripheral surface of the rotating shaft at an interval in the radial direction of the central axis. It has an inner circumferential surface. Further, a seal portion for suppressing the flow of air between the inner peripheral surface of the stationary disk and the outer peripheral surface of the rotating shaft is provided on the opposite side of the stationary disk with respect to the stationary disk in the central axis direction. It may be provided.
With this configuration, when the pump is stopped during operation of the supercharger, the seal portion suppresses the flow of air between the inner circumferential surface of the stationary disk and the outer circumferential surface of the rotating shaft. Can. Thus, it is possible to suppress air being sucked in from the radial inside of the gap between the thrust disk and the stationary disk. Therefore, it is possible to suppress the outflow of the lubricating oil present in the gap between the thrust disk and the stationary disk, and maintain the lubricity.

  According to the above-mentioned supercharger, it becomes possible to certainly supply lubricating oil from a head tank to a bearing.

It is a schematic diagram which shows the whole structure of the turbocharger in one Embodiment of this invention. It is a figure showing composition of a thrust bearing and header tank in a first embodiment of the above-mentioned supercharger. It is a figure which shows the structure of the thrust disk of the said thrust bearing, and is sectional drawing in alignment with the AA of FIG. It is a figure which shows the taper land of the said thrust disk, and is sectional drawing in alignment with the BB line of FIG. It is a figure which shows the structure of the stationary disk of the said thrust bearing, and is sectional drawing which follows the C-C line of FIG. In the said supercharger, it is a figure which shows the state which the non-return valve of the header tank opened. It is a figure which shows the structure of the thrust bearing in 2nd embodiment of this invention, and a header tank. It is a figure which shows the structure of the thrust disk of the thrust bearing in 2nd embodiment of this invention, and is sectional drawing in alignment with the DD line of FIG. It is a figure which shows the structure of the thrust bearing in 3rd embodiment of this invention, and a header tank.

Hereinafter, a turbocharger according to an embodiment of the present invention will be described based on the drawings.
First Embodiment
FIG. 1 is a schematic view showing an entire configuration of a turbocharger according to a first embodiment of the present invention.
As shown in FIG. 1, the supercharger 1A of this embodiment includes a rotating shaft 2, a turbine wheel 3, a compressor wheel 4, a radial bearing 5, a thrust bearing 6, and a header tank 40. There is. The supercharger 1A is mounted on a ship, for example, in a posture in which the central axis O of the rotation shaft 2 extends in the horizontal direction.

  The rotation shaft 2 is rotatably supported around a central axis O by a housing (not shown) of the turbocharger 1A. The rotating shaft 2 is provided by causing the first end 2a and the second end 2b on both sides in the central axis O direction to protrude to the outside of the housing.

  The turbine wheel 3 is provided on the first end 2 a side of the rotation shaft 2. The turbine wheel 3 rotates integrally with the rotating shaft 2 around the central axis O by the exhaust gas flow discharged from the main engine or the like of the ship.

  The compressor wheel 4 is provided on the second end 2 b side of the rotating shaft 2. The compressor wheel 4 rotates around the central axis O integrally with the rotating shaft 2. The compressor wheel 4 compresses air introduced from the outside and supplies the compressed air to a master machine or the like.

  The radial bearing 5 is provided in a housing (not shown) of the turbocharger 1A. A plurality of radial bearings 5 are provided at intervals in the central axis O direction, and rotatably support the rotary shaft 2 around the central axis O. The radial bearing 5 supports a load in the radial direction orthogonal to the central axis O of the rotating shaft 2. Such a radial bearing 5 is formed by a sliding bearing or the like.

  The thrust bearing 6 is provided in a housing (not shown) of the turbocharger 1A. The thrust bearing 6 supports a load in the direction of the central axis O of the rotating shaft 2. The thrust bearing 6 comprises a thrust disk 20 and a stationary disk 30.

As shown in FIGS. 2 and 3, the thrust disk 20 is disk-shaped and is formed to extend radially outward from the rotation shaft 2. The thrust disk 20 rotates integrally with the rotating shaft 2.
The thrust disk 20 includes a tapered land 22 formed on the side 21 facing the stationary disk 30.

FIG. 2 is a view showing configurations of a thrust bearing and a header tank in the first embodiment of the turbocharger. FIG. 3 is a view showing the configuration of a thrust disk of the above-mentioned thrust bearing, and is a cross-sectional view taken along the line AA of FIG. FIG. 4 is a view showing a tapered land of the thrust disk, and is a cross-sectional view taken along the line B-B of FIG.
As shown in FIGS. 2 to 4, the tapered land 22 includes a lubricating oil receiving groove 23, an oil feeding groove 24, and a tapered portion 25.
The lubricating oil receiving groove 23 is formed on the radially inner portion of the side surface 21 of the thrust disk 20. The lubricating oil receiving groove 23 is continuous in the circumferential direction around the central axis O. The lubricating oil receiving groove 23 is formed in the side surface 21 of the thrust disk 20 so as to be recessed in a direction away from the stationary disk 30.

  The oil supply groove 24 is formed to extend radially outward from the lubricating oil receiving groove 23. The oil supply groove 24 is formed in the side surface 21 of the thrust disk 20 so as to be recessed in a direction away from the stationary disk 30. A plurality of fuel grooves 24 are formed in the circumferential direction around the central axis O at intervals.

  The tapered portion 25 is continuously formed in the circumferential direction from each of the oil supply grooves 24. Each tapered portion 25 is formed to be inclined so as to gradually approach the stationary disk 30 side in the circumferential direction. In other words, each tapered portion 25 is formed so that the recess size from the side surface 21 becomes smaller as it is separated from the oil supply groove 24 in the circumferential direction.

  As shown in FIG. 2, the stationary disk 30 is provided at an interval in the central axis O direction with respect to the thrust disk 20. The stationary disk 30 is supported by a bearing support 7 provided in a housing (not shown) of the turbocharger 1A. The stationary disk 30 has a flat surface 31 orthogonal to the central axis O on the side facing the thrust disk 20. The flat surface 31 is formed with a pad portion 32 made of a soft material and capable of sliding contact with the side surface 21 of the thrust disk 20.

FIG. 5 is a view showing a configuration of a stationary disk of the thrust bearing, and is a cross-sectional view taken along the line C-C of FIG.
As shown in FIGS. 2 and 5, the stationary disk 30 is provided with a lubricating oil supply passage 33. The lubricating oil supply passage 33 supplies the lubricating oil supplied from the header tank 40 to the gap between the thrust disk 20 and the stationary disk 30. The lubricating oil supply paths 33 are provided at a plurality of locations at intervals in the circumferential direction on the stationary disk 30. Each lubricating oil supply passage 33 is formed to extend radially in the stationary disk 30. A supply pipe 44 </ b> C from the header tank 40 is connected to a radially outer end of the lubricating oil supply passage 33.

  The flat surface 31 of the stationary disk 30 is provided with a supply groove (supply port) 34 continuous in the circumferential direction. The supply groove 34 opens toward the thrust disk 20 side. In other words, the supply groove 34 is formed in the flat surface 31 so as to be recessed in the direction away from the thrust disk 20. The radial inner end of the lubricating oil supply passage 33 communicates with the supply groove 34. The lubricating oil receiving groove 23 of the tapered land 22 of the thrust disk 20 and the supply groove 34 of the stationary disk 30 are provided at positions facing each other in the central axis O direction.

  As shown in FIG. 1, the header tank 40 stores lubricating oil supplied to the radial bearing 5 and the thrust bearing 6. The header tank 40 is disposed above the radial bearings 5 and the thrust bearings 6 in the vertical direction.

  As shown in FIG. 2, a pump 41 for feeding lubricating oil into the header tank 40 is provided outside the header tank 40. Further, supply pipes 44A to 44C (see FIG. 1) for supplying lubricating oil to the radial bearing 5 and the thrust bearing 6 are connected to the header tank 40, respectively.

  The lubricating oil supplied from the header tank 40 to the thrust bearing 6 through the supply pipe 44 C is supplied to the gap between the thrust disk 20 and the stationary disk 30 via the lubricating oil supply passage 33 and the supply groove 34. At this time, negative pressure is generated in the gap between the thrust disk 20 and the stationary disk 30 by the tapered lands 22 formed on the thrust disk 20. Due to this negative pressure, lubricating oil is drawn from the supply groove 34 of the stationary disk 30 into the gap between the thrust disk 20 and the stationary disk 30. The lubricating oil in the gap between the thrust disk 20 and the stationary disk 30 spreads radially outward due to the action of the centrifugal force by the thrust disk 20 which rotates with the rotating shaft 2.

Further, in the header tank 40, a communication pipe (communication portion) 42 and an air introduction pipe (air introduction portion) 43 are provided.
The communication pipe 42 communicates the inside and the outside of the header tank 40. The communication pipe 42 takes in and out air that increases and decreases in the header tank 40 as the amount of lubricating oil in the header tank 40 fluctuates. That is, when the amount of lubricating oil in the header tank 40 increases, the air in the header tank 40 is discharged to the outside. When the amount of lubricating oil in the header tank 40 decreases, air is taken into the header tank 40 from the outside. The communication pipe 42 has an opening 42 a at an upper portion in the header tank 40.

  The air introduction pipe 43 introduces air from the outside into the header tank 40 when the pressure of air in the header tank 40 becomes smaller than the pressure of air outside the header tank 40. The air introduction pipe 43 has an opening 43 a at the top in the header tank 40. The opening 43 a of the air introduction pipe 43 may be disposed higher in the header tank 40 than the opening 42 a of the communication pipe 42.

  A check valve 45 is provided at the opening 43 a of the air introduction pipe 43. The check valve 45 opens only when the pressure of the air in the header tank 40 becomes smaller than the pressure of the air outside the header tank 40. That is, in the state where the pressure in the header tank 40 is the same as the pressure outside the header tank 40 (atmospheric pressure) or in the state where the pressure in the header tank 40 is larger than the pressure outside the header tank 40, the check valve 45 It is closed and shuts off the air introduction pipe 43.

  When such a supercharger 1A is in normal operation, lubricating oil is supplied from the header tank 40 to the gap between the thrust disk 20 and the stationary disk 30 through the lubricating oil supply path 33. Due to the supply of lubricating oil into the header tank 40 by the pump 41 and the supply of lubricating oil from the header tank 40 to the gap between the thrust disk 20 and the stationary disk 30, the amount of lubricating oil in the header tank 40 fluctuates. Along with this, the amount of air in the header tank 40 also fluctuates, but since the inside and the outside of the header tank 40 are in communication with each other through the communication pipe 42, the header tank 40 is in normal operation of the turbocharger 1A. The pressure of the air inside is maintained equal to the pressure outside the header tank 40. Therefore, during normal operation of the turbocharger 1A, the supply of lubricating oil from the header tank 40 to the gap between the thrust disk 20 and the stationary disk 30 is stably performed.

FIG. 6 is a view showing a state in which the check valve of the header tank is opened in the supercharger.
If the pump 41 is stopped for any reason while the supercharger 1A is in operation, feeding of the lubricating oil from the pump 41 into the header tank 40 is not performed. At this time, as shown in FIG. 6, when the level L of the lubricating oil in the header tank 40 is higher than the opening 42a in the header tank 40 of the communication pipe 42, the lubricating oil flows into the communication pipe 42, The communication between the inside and the outside of the header tank 40 through the communication pipe 42 may be interrupted. In this shutoff state, when the level of lubricating oil in the header tank 40 decreases, the pressure of air in the header tank 40 decreases. When the pressure of the air in the header tank 40 becomes smaller than the pressure (atmospheric pressure) of the air outside the header tank 40, the check valve 45 provided in the air introduction pipe 43 opens. Thus, air is introduced into the header tank 40 from the outside of the header tank 40 through the air introduction pipe 43. As a result, the pressure of air in the header tank 40 is prevented from being excessively reduced, and the supply of lubricating oil from the header tank 40 to the gap between the thrust disk 20 and the stationary disk 30 is stably performed.

  In the supercharger 1A provided with the header tank 40 of the first embodiment described above, when the pressure of the air in the header tank 40 becomes smaller than the pressure of the air outside the header tank 40, the reverse of the air introduction pipe 43 The stop valve 45 opens. Thus, air can be introduced into the header tank 40 from the outside of the header tank 40 through the air introduction pipe 43, and the pressure of the air in the header tank 40 can be prevented from being excessively reduced. As a result, even when the pump 41 is stopped during operation of the supercharger 1A, the lubricating oil can flow down to the lubricating oil supply passage 33 and the supply groove 34 by its own weight. It is possible to stably and continuously supply the lubricating oil to the gap between the stationary disk 30 and the stationary disk 30.

  The above-described thrust disk 20 has a tapered land 22 on the side facing the stationary disk 30. In general, in the case of the configuration provided with the tapered land 22, when the pump 41 is stopped, air is sucked from the outside of the housing (not shown) into the gap between the thrust disk 20 and the stationary disk 30, and the lubricity is impaired. There is a case. However, in the first embodiment described above, the header tank 40 is provided with the air introduction pipe 43 and the check valve 45 in the configuration having the tapered land 22. Therefore, even when the pump 41 is stopped during operation of the supercharger 1A, the lubricating oil can be supplied from the header tank 40 to the gap between the thrust disk 20 and the stationary disk 30. As a result, the thrust can be obtained. The lubricity of the gap between the disk 20 and the stationary disk 30 can be stably maintained.

Second Embodiment
Next, a second embodiment according to the present invention will be described based on the drawings. The second embodiment described below is different from the first embodiment only in the configuration including the outer peripheral hole 51 and the groove 52, so the same parts as those in the first embodiment will be described with the same reference numerals. Duplicate descriptions will be omitted.

FIG. 7 is a view showing configurations of a thrust bearing and a header tank in the second embodiment of the turbocharger. FIG. 8 is a view showing the configuration of a thrust disk of the above-mentioned thrust bearing, and is a cross-sectional view taken along the line D-D of FIG.
As shown in FIGS. 7 and 8, the turbocharger 1 </ b> B provided with the header tank 40 in this embodiment includes the outer peripheral hole 51 and the groove (recess) 52 in the stationary disk 30.

  The outer peripheral hole 51 extends in the direction of the central axis O and is in communication with each lubricating oil supply passage 33. As a result, a plurality of outer peripheral holes 51 are formed in the stationary disk 30 in the circumferential direction. Each of the outer peripheral holes 51 opens radially outward of the supply groove 34 on the flat surface 31 of the stationary disk 30. The total opening area of the plurality of outer peripheral holes 51 in the flat surface 31 is smaller than the opening area of the supply groove 34 in the flat surface 31. For example, the total opening area of the plurality of outer peripheral holes 51 can be about 1/20 to 1/10 of the opening area of the supply groove 34.

  The groove 52 is continuously formed radially outward along the flat surface 31 from the outer peripheral hole 51. The groove 52 is formed in the flat surface 31 so as to be recessed in the direction away from the thrust disk 20 in the central axis O direction.

  When the supercharger 1B described above is in normal operation, lubricating oil is supplied from the header tank 40 to the gap between the thrust disk 20 and the stationary disk 30 through the lubricating oil supply passage 33. At this time, since the total opening area of the plurality of outer peripheral holes 51 is smaller than the opening area of the supply groove 34, lubricating oil is mainly supplied from the supply groove 34 to the gap between the thrust disk 20 and the stationary disk 30. Ru.

  During operation of the supercharger 1B, air taken in from the outside of the housing (not shown) intrudes from the inside in the radial direction into the gap between the thrust disk 20 and the stationary disk 30, and bites into the tapered land 22. The negative pressure generated in the gap between the disk 20 and the stationary disk 30 is reduced. Then, the lubricating oil is supplied from the lubricating oil supply passage 33 to the gap between the thrust disk 20 and the stationary disk 30 through the plurality of outer peripheral holes 51 formed radially outward of the supply groove 34. The lubricating oil supplied from the outer peripheral hole 51 spreads radially outward in the gap between the thrust disk 20 and the stationary disk 30 through the groove 52 by the centrifugal force of the thrust disk 20 which rotates integrally with the rotary shaft 2. Thereby, the lubricity between the thrust disk 20 and the stationary disk 30 is maintained at least in the radially outer portion of the gap between the thrust disk 20 and the stationary disk 30. At this time, since the outer peripheral hole 51 is formed radially outward of the supply groove 34, the lubricating oil supplied from the outer peripheral hole 51 to the gap between the thrust disk 20 and the stationary disk 30 is radially inner. A larger centrifugal force acts than the lubricating oil supplied from the supply groove 34. As a result, a negative pressure is generated in a region radially inward of the lubricating oil supplied from the outer peripheral hole 51, and the negative pressure lubricates the gap between the thrust disk 20 and the stationary disk 30 from the radially inner supply groove 34. The effect of sucking out oil is also expected.

  Therefore, according to the second embodiment described above, by providing the outer peripheral hole 51 radially outward of the supply groove 34, even if air is caught in the gap between the thrust disk 20 and the stationary disk 30 from the radially inner side, The lubricity of the gap between the thrust disk 20 and the stationary disk 30 can be stably maintained.

  Further, by providing the groove 52 continuously extending along the flat surface 31 to the outer peripheral hole 51, the lubricating oil supplied through the outer peripheral hole 51 can be efficiently spread in the gap between the thrust disk 20 and the stationary disk 30. it can. Thus, the lubricating oil can be more reliably supplied to the gap between the thrust disk 20 and the stationary disk 30.

  Furthermore, since the groove 52 extends from the outer peripheral hole 51 to the outer side in the radial direction of the central axis O, the lubricating oil supplied from the outer peripheral hole 51 has a diameter in the gap between the thrust disk 20 and the stationary disk 30 by centrifugal force. It spreads out to the direction outside efficiently. Thus, the lubricating oil can be more reliably supplied to the gap between the thrust disk 20 and the stationary disk 30.

  Further, as in the first embodiment, by providing the air introduction pipe 43 and the check valve 45, even when the pump 41 is stopped during the operation of the supercharger 1B, the thrust disc 20 from the header tank 40 is The lubricating oil can be reliably supplied to the gap between the stationary disk 30 and the stationary disk 30.

In the second embodiment, the groove 52 is formed to extend radially outward of the outer peripheral hole 51, but the invention is not limited thereto. For example, the groove 52 may be formed to extend radially inward from the outer peripheral hole 51. The groove 52 may be formed to extend in the circumferential direction from the outer peripheral hole 51.
Furthermore, in the second embodiment, the case where the groove 52 is formed as the recess is illustrated, but the shape of the recess may be any shape.

Third Embodiment
Next, a third embodiment of the present invention will be described based on the drawings. The third embodiment described below is different from the first and second embodiments only in the configuration provided with the seal portion 60 between the rotating shaft 2 and the stationary disk 30, so the first and second embodiments will be described. The same parts as those of the embodiment will be described with the same reference numerals, and the redundant description will be omitted.

FIG. 9 is a view showing a configuration of a thrust bearing and a header tank in the third embodiment of the present invention.
As shown in FIG. 9, the supercharger 1 </ b> C including the header tank 40 in this embodiment includes a seal portion 60 on the opposite side of the stationary disk 30 to the stationary disk 30 in the central axis O direction. The seal portion 60 includes an outer peripheral side convex portion 62 and an inner peripheral side convex portion 63.
The stationary disk 30 is formed with an extending portion 61 extending in the direction opposite to the thrust disk 20 along the central axis O direction. The outer circumferential convex portion 62 protrudes radially inward from the extending portion 61. A plurality of outer peripheral side convex portions 62 are provided at intervals in the central axis O direction.

  The inner circumferential convex portion 63 protrudes radially outward from the outer circumferential surface 2 f of the rotary shaft 2. A plurality of inner peripheral side convex portions 63 are provided at intervals in the central axis O direction. The respective inner peripheral side convex portions 63 are arranged to be shifted in the central axis O direction with respect to the outer peripheral side convex portions 62. The plurality of outer peripheral side convex portions 62 and the plurality of inner peripheral side convex portions 63 constitute a so-called labyrinth seal which is disposed to be engaged with each other.

  By providing such a seal portion 60, when the pump 41 is stopped during operation of the supercharger 1C, the seal portion 60 allows the inner circumferential surface 30g of the stationary disk 30 to be received from the outside of the housing (not shown). It can suppress that air flows in between the outer peripheral surfaces 2f of the rotating shaft 2.

  Therefore, according to the supercharger 1C including the header tank 40 of the third embodiment described above, the air is generated between the inner peripheral surface 30g of the stationary disk 30 and the outer peripheral surface 2f of the rotary shaft 2 by the seal portion 60. It is possible to suppress the inflow. Thus, air is prevented from being sucked into the gap between the thrust disk 20 and the stationary disk 30 from the inner side in the radial direction. Therefore, it is possible to suppress the outflow of the lubricating oil present in the gap between the thrust disk 20 and the stationary disk 30, and maintain the lubricity.

  Further, as in the first embodiment, by providing the air introduction pipe 43 and the check valve 45, even when the pump 41 is stopped during the operation of the turbocharger 1C, the thrust disc 20 from the header tank 40 is The lubricating oil can be reliably supplied to the gap between the stationary disk 30 and the stationary disk 30.

  Although the case where the seal portion 60 has the labyrinth structure has been described in the third embodiment described above, the seal portion 60 is not limited to the seal portion having the labyrinth structure, and various seal members and the like can be used.

(Other modifications)
The present invention is not limited to the above-described embodiment, and includes the above-described embodiment with various changes added thereto, without departing from the spirit of the present invention. That is, the specific shape, configuration, and the like described in the embodiment are merely examples, and can be changed as appropriate.
For example, the outer peripheral hole 51 and the groove 52 shown in the second embodiment and the seal part 60 shown in the third embodiment can be combined.

Further, the configuration of the tapered land 22 is not limited to the configuration shown in the above embodiment, and can be changed as appropriate.
Furthermore, the configuration of each part of the superchargers 1A, 1B, and 1C can be appropriately changed within the scope of the present invention.
In addition, although the case where the use of superchargers 1A, 1B, and 1C was for ships was explained, it is not limited to for ships. For example, the use of the turbochargers 1A, 1B, 1C may be a generator or the like.

1A to 1C Turbocharger 2 Rotor shaft 2a First end 2b Second end 2f Outer peripheral surface 3 Turbine wheel 4 Compressor wheel 5 Radial bearing 6 Thrust bearing 7 Bearing support 20 Thrust disc 21 Side 22 Taper land 23 Lubricating oil reception Groove 24 Oil supply groove 25 Tapered portion 30 Stationary disk 30 g Inner circumferential surface 31 Flat surface 32 Pad portion 33 Lubricating oil supply passage 34 Supply groove (supply port)
40 header tank 41 pump 42 communication pipe (communication part)
42a Opening 43 Air introduction pipe (air introduction part)
43a Openings 44A to 44C Supply pipe 45 Check valve 51 Outer peripheral hole 52 Groove (concave portion)
60 seal portion 61 extension portion 62 outer peripheral side convex portion 63 inner peripheral side convex portion O central axis

Claims (6)

A rotating shaft rotatably supported around a central axis,
A turbine wheel provided on a first end side of the rotating shaft;
A compressor wheel provided on the second end side of the rotating shaft;
A thrust disk which extends radially outward from the rotation shaft and rotates integrally with the rotation shaft;
A stationary disk opposed to the thrust disk in the central axis direction;
A header tank for storing lubricating oil supplied to a gap between the thrust disk and the stationary disk;
A pump for feeding the lubricating oil into the header tank;
A lubricating oil supply passage for supplying the lubricating oil from the header tank to the gap;
A communication portion for communicating the inside and the outside of the header tank, and for communicating the air in the header tank with the fluctuation of the amount of the lubricating oil in the header tank;
An air introducing unit for introducing air from the outside of the header tank to the inside of the header tank in which the communicating unit communicates with the outside ;
The level of the lubricating oil in the header tank is higher than the opening in the header tank of the communication portion provided in the air introducing portion, the lubricating oil flows into the communication portion, and the communication by the communication portion is A non-return valve that opens only when the pressure of air inside the header tank that is shut off and causes the communication portion to communicate with the outside is smaller than the pressure of air outside the header tank;
Equipped with a supercharger. The stationary disk has a flat surface perpendicular to the central axis on the side facing the thrust disk,
The supercharger according to claim 1, wherein the thrust disk has a tapered land on the side facing the flat surface of the stationary disk. The lubricating oil supply path is
A supply port that opens to the flat surface of the stationary disk and supplies the lubricating oil to the gap;
An outer peripheral hole that opens radially outward of the supply port on the flat surface of the stationary disk and has an opening area smaller than the supply port;
The supercharger according to claim 2, comprising   The supercharger according to claim 3, wherein the flat surface of the stationary disk is formed with a concave portion continuous from the outer peripheral hole along the flat surface.   The supercharger according to claim 4, wherein the recess extends radially outward of the central shaft from the outer peripheral hole. The stationary disc is
It has an inner circumferential surface facing the outer circumferential surface of the rotation shaft at intervals in the radial direction of the central axis,
A seal portion is provided on the opposite side of the stationary disk to the stationary disk in the central axis direction, between the inner peripheral surface of the stationary disk and the outer peripheral surface of the rotary shaft to prevent air from flowing in. The supercharger according to any one of claims 1 to 5.

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