JP2012237254A - Lubrication oil passage structure and supercharger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To sufficiently prevent blocking of an oil drain port 75 by lubrication oil G by enhancing the oil draining property from the oil drain port 75.SOLUTION: An oil supply port 61 is formed on an upper part of a bearing housing 3, oil supplying passages 63, 65 are formed on the upper part of a supporting block 5, an oil draining cutout 67 is formed on a front end side on the lower part of the supporting block 5, an oil draining passage 69 is formed on a back end side on the lower part of the supporting block 5, a receiving chamber 73 is formed below the supporting block 5 inside the bearing housing 3, the oil drain port 75 is formed on the lower part of the bearing housing 3, and on a cross section perpendicular to a shaft center of a rotor shaft 19, the oil draining cutout 67 is directed vertically downward, and a passage center 69c of the oil draining passage 69 is inclined towards the opposite side of a rotating direction D of the rotor shaft 19 with respect to the vertically downward direction.

Description

  The present invention relates to a lubricating oil passage structure used in a supercharger such as a vehicle supercharger.

  Generally, a supercharger for a vehicle is provided with a bearing block having a support block on the inner side thereof, and an installation hole extending in the horizontal direction extending through the support block, and a horizontal separation within the installation hole of the support block. A plurality of radial bearings, and a rotor shaft rotatably supported by the plurality of radial bearings and integrally connecting the compressor impeller and the turbine impeller. In addition, in a turbocharger for a vehicle, lubricating oil is supplied to the sliding portion (sliding portion) of the rotor shaft and the plurality of radial bearings, and the sliding portion of the rotor shaft and the plurality of radial bearings is lubricated. A lubricating oil passage structure for draining oil to the outside of the bearing housing is used (see Patent Document 1, etc.). The configuration of the lubricating oil passage structure according to the prior art will be briefly described as follows.

  The bearing housing is formed with an oil supply port (oil intake port) for taking in the lubricating oil. Further, an oil supply passage for supplying lubricating oil to the sliding portions of the rotor shaft and the plurality of radial bearings is formed inside the bearing housing, and the oil supply passage communicates with the oil supply port.

  An oil drainage notch for draining the lubricating oil that lubricates the sliding part of the radial bearing on the rotor shaft and compressor impeller side at one end side in the axial direction (axial direction of the rotor shaft) at the lower part of the support block of the bearing housing Is formed. In addition, an oil drain passage for draining the lubricant that lubricated the sliding portion of the radial bearing on the rotor shaft and turbine impeller side is formed through the other end side in the axial direction at the lower portion of the support block of the bearing housing. ing.

  A receiving chamber is formed below the support block in the bearing housing to receive lubricating oil that lubricates the sliding portions of the rotor shaft and the plurality of radial bearings. The receiving chamber has an oil drain notch and a drain passage. Communicating with In addition, an oil discharge port is formed in the lower portion of the bearing housing so that the lubricating oil can be discharged to the outside of the bearing housing. The oil discharge port communicates with the receiving chamber.

JP 2005-214094 A

  By the way, in recent years, with the demand for higher engine output, the rotational speed of the rotor shaft also increases, and the flow rate of the lubricating oil supplied to the sliding portion between the rotor shaft and the radial bearing tends to increase. On the other hand, when the flow rate of the lubricating oil supplied to the sliding portions of the rotor shaft and the plurality of radial bearings increases, the lubricating oil that flows out from the drainage notch and the lubricating oil that flows out from the outlet side opening of the drainage passage Interference increases, oil drainage from the oil drain port (oil drainage of the lubricating oil passage structure) is impaired, and the oil drain port may be blocked (clogged) by the lubricating oil.

  Then, an object of this invention is to provide the lubricating oil path structure of a novel structure etc. which can solve the above-mentioned problem.

  According to a first aspect of the present invention, there is provided a bearing housing having a support block on the inner side thereof and having an installation hole extending through the support block extending in the horizontal direction, and spaced horizontally in the installation hole of the support block. A plurality of radial bearings, and a rotor shaft rotatably supported by the plurality of radial bearings and integrally connecting a compressor impeller and a turbine impeller, and the rotor shaft Lubricating oil is supplied to sliding portions (sliding portions) of the plurality of radial bearings, and lubricating oil that lubricates the sliding portions of the rotor shaft and the plurality of radial bearings is discharged to the outside of the bearing housing. An oil intake structure (oil supply port) for taking the lubricant oil into the bearing housing is formed, communicated with the oil supply port inside the bearing housing, and Lubricating the sliding part of the rotor shaft and the plurality of radial bearings (the sliding part of the radial bearing on the rotor shaft and the compressor impeller side and the sliding part of the radial bearing on the rotor shaft and the turbine impeller side) An oil supply passage for supplying oil is formed, and the lubricating oil that lubricates the sliding portion of the radial bearing on the rotor shaft and the compressor impeller side at one end side in the axial direction at the lower portion of the support block is drained. A drainage notch for draining the lubricating oil that lubricates the sliding portion of the radial bearing on the turbine shaft side and the rotor shaft on the other end side in the axial direction at the lower portion of the support block is formed. An oil passage is formed through, communicated with the drainage notch and the drainage passage below the support block in the bearing housing, and a plurality of front shafts and the rotor shaft. A receiving chamber (cavity) for receiving lubricating oil that lubricates the sliding portion of the radial bearing is formed, communicated with the receiving chamber at the lower portion of the bearing housing, and can drain the lubricating oil to the outside of the bearing housing In the cross section perpendicular to the axis of the rotor shaft, the drain notch is directed vertically downward, and the passage center line of the oil drain passage is inclined with respect to the vertically downward direction. Is the gist.

  In the specification and claims of the present application, “axial direction” refers to the axial direction of the rotor shaft. The “plurality of radial bearings” is intended to include, in addition to a plurality of independent radial bearings, a plurality of integrated radial bearings such as a pair of radial bearings in a semi-floating metal.

  According to the first feature, during operation of the supercharger, lubricating oil is lubricated from the oil supply port to the sliding portions of the rotor shaft and the plurality of radial bearings via the oil supply passage. Add oil. Accordingly, the sliding portions of the rotor shaft and the plurality of radial bearings can be lubricated to prevent seizure of the rotor shaft and the plurality of radial bearings.

  On the other hand, the lubricating oil that has lubricated the sliding portions of the rotor shaft and the plurality of radial bearings flows out from the drainage notch and the outlet side opening of the drainage passage and passes through the receiving chamber to the drainage. Oil is discharged from the oil port to the outside of the bearing housing.

  Here, in the cross section orthogonal to the axis of the rotor shaft, the oil drain notch is directed vertically downward, and the passage center line of the oil drain passage is inclined with respect to the vertical downward direction. Even if the flow rate of the lubricating oil supplied to the rotor shaft and the sliding portions of the plurality of radial bearings increases, the lubricating oil that flows out from the exhaust oil notch and the lubrication that flows out from the outlet side opening of the exhaust oil passage Interference with oil can be sufficiently suppressed (reduced).

  According to a second aspect of the present invention, in the supercharger that supercharges the air supplied to the engine side using the energy of the exhaust gas from the engine, the lubricating oil passage structure according to the first feature is provided. This is the summary.

  According to the 2nd characteristic, there exists an effect | action similar to the effect | action by a 1st characteristic.

  According to the present invention, even if the flow rate of the lubricating oil supplied to the sliding portions of the rotor shaft and the plurality of radial bearings increases, the lubricating oil that flows out from the drainage notch and the outlet of the drainage passage Since the interference with the lubricating oil flowing out from the side opening can be sufficiently suppressed, the oil drainability from the oil drain port (the oil drainage property of the lubricating oil passage structure) is increased, and the oil drain port is blocked by the lubricating oil. It can be sufficiently prevented.

FIG. 1 is an enlarged view of an arrow I in FIG. 2A is a view taken along line IIA-IIA in FIG. 1, and FIG. 2B is a view taken along line IIB-IIB in FIG. FIG. 3 is a side sectional view of the vehicle supercharger according to the embodiment of the present invention.

  An embodiment of the present invention will be described with reference to FIGS. 1 to 3. In the drawings, “FF” indicates the forward direction, and “FR” indicates the backward direction.

  As shown in FIGS. 1 and 3, the vehicle supercharger 1 according to the embodiment of the present invention supercharges the air supplied to the engine using the energy of the exhaust gas from the engine (not shown). (Compressed). And the specific structure of the supercharger 1 for vehicles is as follows.

  The vehicular supercharger 1 includes a bearing housing 3, and the bearing housing 3 has a support block 5 on the inner side. The support block 5 has a front-rear direction (one in the horizontal direction). An installation hole 7 extending through is formed through. The support block 5 constitutes a part of the inside of the bearing housing 3.

  In the installation hole 7 of the support block 5, a semi-floating metal 9 is provided so as not to rotate via a rotation pin 11, and the semi-floating metal 9 has a pair of radial bearing portions 13 and 15 in the front-rear direction. Separated. In other words, a pair of radial bearing portions 13 and 15 are provided in the installation hole 7 of the support block 5 so as to be separated in the front-rear direction. A through-hole 17 is formed through the intermediate portion of the semi-floating metal 9.

  A rotor shaft (turbine shaft) 19 extending in the front-rear direction is rotatably supported by the pair of radial bearing portions 13 and 15. The rotor shaft 19 is a compressor impeller that compresses air using centrifugal force. 21 and a turbine impeller 23 that generates a rotational force (rotational torque) using pressure energy of exhaust gas are integrally connected. A thrust collar 25 is integrally provided on the rotor shaft 19 on the compressor impeller 21 side.

  On the front side of the thrust collar 25 in the bearing housing 3, there is a thrust bearing 27 that bears (supports) a thrust load in the forward direction (one side in the axial direction of the rotor shaft 19) acting on the rotor shaft 19 via the thrust collar 25. Is provided. Further, on the rear side of the thrust collar 25 in the bearing housing 3, a thrust that bears (supports) a thrust load in the rear direction (the other side in the axial direction of the rotor shaft 19) acting on the rotor shaft 19 via the thrust collar 25. A bearing 29 is provided.

  An oil drain 31 is integrally provided between the compressor impeller 21 and the thrust collar 25 in the rotor shaft 19, and an annular seal plate 33 surrounds the oil drain 31 at the front side portion of the bearing housing 3. Is provided. A front seal ring 35 is provided between the inner peripheral surface of the seal plate 33 and the outer peripheral surface of the oil drain 31 to prevent leakage of the lubricating oil G from the bearing housing 3 side to the compressor impeller 21 side. Yes. Further, a fitting insertion hole 37 into which the rotor shaft 19 can be fitted is formed in the rear side portion of the bearing housing 3. A rear seal ring 39 for preventing leakage of the lubricating oil G from the bearing housing 3 side to the turbine impeller 23 side is provided between them.

  As shown in FIG. 3, a compressor housing 41 that houses the compressor impeller 21 is provided on the front side of the bearing housing 3, and the inlet side of the compressor impeller 21 in this compressor housing 41 (the front side of the compressor housing 41). An air intake 43 for taking in air is formed. A spiral compressor scroll passage 45 is formed on the outlet side of the compressor impeller 21 inside the compressor housing 41. Further, an air discharge port 47 for discharging compressed air (compressed air) is formed at an appropriate position of the compressor housing 41, and the air discharge port 47 communicates with the compressor scroll passage 45.

  A turbine housing 49 that houses the turbine impeller 23 is provided on the rear side of the bearing housing 3, and a gas intake 51 for taking in exhaust gas is formed at an appropriate position of the turbine housing 49. Further, a spiral turbine scroll passage 53 is formed on the inlet side of the turbine impeller 23 inside the turbine housing 49, and the turbine scroll passage 53 communicates with the gas inlet 51. Further, a gas discharge port 55 for discharging exhaust gas is formed on the outlet side of the turbine impeller 23 in the turbine housing 49 (the rear side of the turbine housing 49).

  Between the turbine scroll passage 53 and the turbine impeller 23 in the turbine housing 49, a variable nozzle mechanism 57 that varies the passage area (flow rate) of the exhaust gas supplied to the turbine impeller 23 side is disposed. . The variable nozzle mechanism 57 has a known configuration disclosed in, for example, Japanese Patent Application Laid-Open No. 2009-243300 and Japanese Patent Application Laid-Open No. 2009-243431, and the detailed configuration of the variable nozzle mechanism 57 is omitted.

  Then, the principal part of embodiment of this invention is demonstrated.

  As shown in FIG. 1, the vehicular supercharger 1 includes lubricating oil on the rotor shaft 19 and the sliding portions of the pair of radial bearing portions 13 and 15 and the sliding portions of the thrust collar 25 and the pair of thrust bearings 27 and 29. A lubricating oil passage structure 59 is provided for draining the lubricating oil G that has supplied G and lubricated these sliding portions to the outside of the bearing housing 3. And the concrete structure of the lubricating oil path structure 59 which concerns on embodiment of this invention is as follows.

  In the upper part of the bearing housing 3, an oil supply port (oil intake port) 61 for taking in the lubricating oil G by the operation of a lubricating oil pump (not shown) is formed. Lubricating oil G is applied to the upper portion of the support block 5 (inside the bearing housing 3) on the sliding portion of the rotor shaft 19 and the pair of radial bearing portions 13 and 15 and the sliding portion of the thrust collar 25 and the thrust bearing 29. A first oil supply passage 63 for supplying oil through the through hole 17 and the like is formed, and the first oil supply passage 63 communicates with the oil supply port 61. Further, a second oil supply passage 65 for supplying lubricating oil G to the sliding portions of the thrust collar 25 and the thrust bearing 27 is formed in the bearing housing 3. It communicates with the mouth 61.

  On the front end side (one end side in the axial direction of the rotor shaft 19) of the lower portion of the support block 5, the sliding portion of the rotor shaft 19 and the radial bearing portion 13 on the compressor impeller 21 side, the thrust collar 25, and a pair of thrust bearings 27, An oil drain notch 67 is formed for draining the lubricating oil G that has lubricated the 29 sliding portions. Further, on the rear end side (the other end side in the axial direction of the rotor shaft 19) at the lower part of the support block 5, lubricating oil G that lubricates the sliding portion of the rotor shaft 19 and the radial bearing portion 15 on the turbine impeller 23 side is applied. A drainage passage 69 for draining oil is formed, and most of the inlet side opening 69i of the drainage passage 69 is opposed to the radial bearing portion 15 on the turbine impeller 23 side. Furthermore, the rear end portion (end portion on the turbine impeller 23 side) of the installation hole 7 of the support block 5 is temporarily supplied with lubricating oil G that lubricates the sliding portion of the rotor shaft 19 and the radial bearing portion 15 on the turbine impeller 23 side. An annular oil reservoir 71 is formed to be stored, and this oil reservoir 71 communicates with the oil discharge passage 69.

  Below the support block 5 in the bearing housing 3, lubricating oil that lubricates the sliding portions of the rotor shaft 19 and the pair of radial bearing portions 13 and 15 and the sliding portions of the thrust collar 25 and the pair of thrust bearings 27 and 29. A receiving chamber (cavity) 73 for receiving G is formed, and the receiving chamber 73 communicates with the oil drain notch 67 and the oil drain passage 69. Further, an oil drain port 75 for draining the lubricating oil G to the outside of the bearing housing 3 is formed in the lower portion of the bearing housing 3, and the oil drain port 75 communicates with the receiving chamber 73. The lubricating oil G discharged from the oil discharge port 75 is once collected in a lubricating oil tank (not shown), and again taken into the bearing housing 3 from the oil supply port 61 by the operation of the lubricating oil pump. It has become.

  As shown in FIG. 2A, the oil drainage notch 67 is directed vertically downward in a cross section orthogonal to the axis of the rotor shaft 19. Further, as shown in FIG. 1, in the cross section including the axis of the rotor shaft 19, the passage center (passage center line) 69 c of the oil drainage passage 69 has an inlet side opening 69 i more than the turbine side impeller than the outlet side opening 69 e. It inclines with respect to the perpendicular downward so that it may approach to 23 side. As shown in FIG. 2B, in the cross section orthogonal to the axis of the rotor shaft 19, the passage center 69c of the oil drainage passage 69 is opposite to the rotational direction D of the rotor shaft 19 with respect to the vertically downward direction. Inclined.

  Here, the inclination angle θ of the oil drainage passage 69 with respect to the vertically lower side of the passage center 69c in the cross section orthogonal to the axis of the rotor shaft 19 is set to 30 to 60 degrees, preferably 40 to 50 degrees. The reason why the inclination angle θ is set to 30 degrees or more is that if the inclination angle θ is set to be less than 30 degrees, the lubricating oil G flowing out from the outlet side opening 69e of the oil drain passage 69 flows out from the oil drain notch 67. It is because it becomes easy to interfere with the lubricating oil G to do. On the other hand, the inclination angle θ is set to 60 degrees or less. If the inclination angle θ is set to exceed 60 degrees, the permeability (oil drainability) of the lubricating oil G in the oil drain passage 69 may be reduced. Because there is.

  In the cross section orthogonal to the axis of the rotor shaft 19, the passage center 69 c of the oil drainage passage 69 is inclined to the opposite side of the rotational direction D of the rotor shaft 19 with respect to the vertical downward direction, instead of the rotor center to the vertical downward direction. You may incline to the rotation direction D side of the axis | shaft 19.

  Then, the effect | action and effect of embodiment of this invention are demonstrated.

  The exhaust gas taken in from the gas inlet 51 is circulated from the inlet side of the turbine impeller 23 to the outlet side (from the upstream side to the downstream side as viewed from the flow direction of the exhaust gas) via the turbine scroll passage 53, thereby The rotor shaft 19 and the compressor impeller 21 can be rotated integrally with the turbine impeller 23 by generating a rotational force (rotational torque) using the pressure energy of the gas. Thereby, the air taken in from the air intake port 43 can be compressed and discharged from the air discharge port 47 via the compressor scroll passage 45, and the air supplied to the engine can be supercharged ( Normal driving operation of the vehicle supercharger 1).

  During operation of the vehicle supercharger 1, the lubricating oil G is taken in from the oil supply port 61 by the operation of the lubricating oil pump, whereby the rotor shaft 19 and the pair of radial bearing parts 13, via the first oil supply passage 63, The lubricating oil G is supplied to the sliding portions 15 and the sliding portions of the thrust collar 25 and the thrust bearing 29, and the lubricating oil G is supplied to the sliding portions of the thrust collar 25 and the thrust bearing 27 via the second oil supply passage 65. Refuel. Thus, the sliding portion of the rotor shaft 19 and the pair of radial bearing portions 13 and 15 and the sliding portion of the thrust collar 25 and the thrust bearings 37 and 29 are lubricated, and the rotor shaft 19 and the radial bearing portions 13 and 15 and the like are lubricated. Burning or the like can be prevented.

  On the other hand, the lubricating oil G that has lubricated the sliding portions of the rotor shaft 19 and the pair of radial bearing portions 13 and 15 and the sliding portions of the thrust collar 25 and the thrust bearings 37 and 29 is disposed in the drainage notch 67 and the drainage passage 69. The oil flows out from the outlet side opening 69e and is discharged from the oil discharge port 75 to the outside of the bearing housing 3 (lubricating oil tank) via the receiving chamber 73.

  Here, in the cross section orthogonal to the axis of the rotor shaft 19, the oil drainage notch 67 is directed vertically downward, and the passage center 69 c of the oil drainage passage 69 rotates the rotor shaft 19 with respect to the vertical downward direction. Since it is inclined to the opposite side of the direction D, the lubricating oil G supplied to the sliding portion of the rotor shaft 19 and the pair of radial bearing portions 13 and 15 and the sliding portion of the thrust collar 25 and the thrust bearings 37 and 29 is provided. Even if the flow rate increases, the interference between the lubricating oil G flowing out from the oil drain notch 67 and the lubricating oil G flowing out from the outlet side opening 69e of the drain oil passage 69 can be sufficiently suppressed (reduced).

  Therefore, according to the embodiment of the present invention, the oil drainability from the oil drain port 75 (the oil drainage property of the lubricating oil passage structure 59) is enhanced and the blockage (clogging) of the oil drain port 75 by the lubricating oil G is sufficiently prevented. The leakage of the lubricating oil G from the bearing housing 3 side to the compressor impeller 21 side, the leakage of the lubricating oil G from the bearing housing 3 side to the turbine impeller 23 side, and the like are detected from the front seal ring 35 and the rear seal ring 39. It is possible to minimize the leakage of lubricating oil.

  In addition, this invention is not restricted to description of the above-mentioned embodiment, It can implement in a various aspect. Further, the scope of rights encompassed by the present invention is not limited to these embodiments.

  A vehicle supercharger according to an embodiment of the present invention (a vehicle supercharger having a lubricating oil passage structure according to an embodiment of the present invention) was prototyped as an invention product, and in a cross section orthogonal to the axis of the rotor shaft A vehicle supercharger (not shown) that differs only in that the center of the oil drainage passage is directed vertically downward was manufactured as a comparative product. And when the lubricating oil behavior observation test was done about the invention product and the comparative product, the following results could be obtained. That is, for the comparative product, when the rotational speed of the rotor shaft was 18000 rpm and the lubricating oil supply amount was 1.59 L / min, the oil outlet was blocked by the lubricating oil, and the bearing housing was filled with the lubricating oil. On the other hand, in the case of the inventive product, even when the rotational speed of the rotor shaft was 18000 rpm and the amount of lubricating oil supplied was 1.61 L / min, the oil outlet was not blocked by the lubricating oil.

G Lubricating oil 1 Vehicle supercharger 3 Bearing housing 5 Support block 7 Installation hole 9 Semi-floating metal 13 Radial bearing portion 15 Radial bearing portion 17 Through hole 19 Rotor shaft 21 Compressor impeller 23 Turbine impeller 25 Thrust collar 27 Thrust bearing 29 Thrust Bearing 35 Front seal ring 39 Rear seal ring 59 Lubricating oil passage structure 61 Oil supply port 63 First oil supply passage 65 Second oil supply passage 67 Oil drain notch 69 Oil drain passage 69c Center of the oil drain passage 69e The outlet side opening of the oil exhaust passage Portion 69i Oil drain passage entrance side opening 73 Receiving chamber 75 Oil drain port

Claims (6)

A bearing housing having a support block on the inside and having an installation hole extending in the horizontal direction penetratingly formed in the support block; and a plurality of radial bearings spaced apart in the horizontal direction in the installation hole of the support block; And a turbocharger including a rotor shaft that is rotatably supported by the plurality of radial bearings and integrally connects a compressor impeller and a turbine impeller,
Lubricating oil is supplied to sliding portions of the rotor shaft and the plurality of radial bearings, and lubricating oil that lubricates sliding portions of the rotor shaft and the plurality of radial bearings is discharged to the outside of the bearing housing. A lubricating oil passage structure,
An oil supply port for taking the lubricating oil into the bearing housing is formed, and an oil supply for communicating with the oil supply port in the bearing housing and for supplying the lubricating oil to the sliding portions of the rotor shaft and the plurality of radial bearings. Oil drainage for draining the lubricating oil that has formed a passage and lubricated the sliding portion of the radial bearing on the compressor shaft side and the rotor shaft on one end side in the axial direction of the rotor shaft at the lower portion of the support block A notch is formed to drain the lubricating oil that lubricates the sliding portion of the radial bearing on the turbine shaft and the impeller side at the other end side in the axial direction of the rotor shaft at the lower portion of the support block. An oil passage is formed penetratingly, communicating with the oil drainage notch and the oil drainage passage below the support block in the bearing housing, and the rotor shaft and a plurality of the radio A receiving chamber for receiving lubricating oil that lubricates a sliding portion of the bearing is formed, communicates with the receiving chamber at a lower portion of the bearing housing, and drains the lubricating oil to the outside of the bearing housing. Formed,
A lubricating oil passage structure characterized in that, in a cross section perpendicular to the axis of the rotor shaft, the oil drainage notch is directed vertically downward, and a passage center line of the oil drainage passage is inclined with respect to the vertical downward direction. .   2. The lubricating oil passage structure according to claim 1, wherein an inclination angle with respect to a vertically lower side of a passage centerline of the oil drainage passage in a cross section perpendicular to the axis of the rotor shaft is set to 30 to 60 degrees. .   The cross-section orthogonal to the axis of the rotor shaft is characterized in that a passage center line of the oil discharge passage is inclined to the opposite side of the rotation direction of the rotor shaft with respect to a vertically downward direction. Item 3. The lubricating oil passage structure according to Item 2.   In a cross section including the shaft center of the rotor shaft, the passage center line of the oil supply passage is inclined with respect to the vertically lower side so that the inlet side opening of the oil supply passage is closer to the turbine impeller side than the outlet side opening. The lubricating oil path structure according to any one of claims 1 to 3, wherein the lubricating oil path structure is provided.   An annular oil sump that communicates with the oil drain passage and temporarily stores lubricating oil is formed at an end of the support block in the installation hole on the turbine impeller side. The lubricating oil path structure according to claim 4. In the supercharger that supercharges the air supplied to the engine side using the energy of the exhaust gas from the engine,
A supercharger comprising the lubricating oil passage structure according to any one of claims 1 to 5.

Images