JP5944186B2 - Bearing device - Google Patents

Description

  The present invention relates to a bearing device that rotatably supports a rotating shaft of a turbocharger.

  The turbocharger includes a rotating shaft that connects the turbine impeller and the compressor impeller. The rotating shaft is supported by a radial bearing from the radial direction. The rotating shaft is supported by a thrust bearing from the axial direction.

  It is necessary to supply lubricating oil to the radial bearing and the thrust bearing. Patent Document 1 discloses a turbocharger having an oil passage dedicated to a radial bearing and an oil passage dedicated to a thrust bearing.

Japanese Patent Laid-Open No. 9-41982 Japanese Utility Model Publication No. 4-82330 JP-A-63-92817

  However, if the oil passage is secured independently for each of the radial bearing and the thrust bearing, the oil passage and the turbocharger configuration are complicated. Also, it is difficult to form the oil passage. In particular, as shown in Patent Documents 2 and 3, when securing an oil passage in the thrust bearing, it is necessary to drill a long hole extending in the radial direction in the short shaft thin-walled thrust bearing. For this reason, the processing operation is difficult.

  The bearing device of the present invention has been completed in view of the above problems. An object of this invention is to provide the bearing apparatus with a simple structure of an oil path.

  (1) In order to solve the above problems, a bearing device of the present invention includes a radial bearing that rotatably supports a rotating shaft of a turbocharger from a radial direction, a thrust collar that is fixed to an outer peripheral surface of the rotating shaft, A thrust bearing that rotatably supports a thrust collar from an axial direction, and further includes an oil that communicates the radial bearing and the thrust bearing and guides oil from the radial bearing to the thrust bearing. A passage is provided.

  According to the bearing device of the present invention, the oil passage is common to the radial bearing and the thrust bearing. For this reason, compared with the case where the oil passage is independent between the radial bearing and the thrust bearing, the configuration of the oil passage and the turbocharger is simplified.

  (2) Preferably, in the configuration of (1), the radial bearing is in sliding contact with the rotating shaft from the radial direction, and the thrust bearing is in sliding contact with the thrust collar from the axial direction, and an outer peripheral surface of the rotating shaft A radial sliding interface defined between the inner peripheral surface of the radial bearing, an axial orientation surface facing the axial direction of the thrust collar, and an axial orientation surface facing the axial direction of the thrust bearing The oil passage communicates with the radial sliding interface and the thrust sliding interface, and extends from the radial sliding interface to the thrust sliding interface. It is better to have a structure that guides oil.

  Radial bearings and thrust bearings are so-called sliding bearings. According to this configuration, oil can be supplied to the thrust sliding interface via the oil passage without performing complicated hole processing on the thrust bearing.

  (3) Preferably, in the configuration of (2), the rotation shaft includes a small diameter portion and a large diameter portion that is continuous with one axial end of the small diameter portion and has a larger diameter than the small diameter portion, The thrust collar is fixed to the outer peripheral surface of the small-diameter portion and has a through-hole that penetrates from the inner peripheral surface to the outer peripheral surface of the thrust collar. A first flange portion that contacts the large-diameter portion; a second flange portion that is connected to the other axial end of the body portion and has a larger diameter than the body portion; and the body portion, the first flange portion, and the second flange portion A thrust bearing housing portion surrounded by a portion, wherein a radial inner end portion of the thrust bearing is housed in the thrust bearing housing portion, and the thrust sliding interface includes the first flange portion and the thrust bearing portion. Between the radial inner end of the bearing and the second flange portion and the radial inner end of the thrust bearing The oil passage communicates with the radial sliding interface and communicates with the first passage portion defined between the first flange portion and the large diameter portion and the thrust bearing housing portion. It is better to have a configuration including a third passage portion disposed in the through hole of the trunk portion and a second passage portion communicating between the first passage portion and the third passage portion.

  According to this configuration, oil can be flowed from the radial sliding interface to the thrust sliding interface via the first passage portion, the second passage portion, the third passage portion, and the thrust bearing housing portion. In particular, in the third passage portion, oil can be smoothly flowed from the radially inner side to the radially outer side by utilizing the thrust collar, that is, the centrifugal force generated by the rotation of the rotating shaft.

  (3-1) Preferably, in the configuration of (3), the first passage portion may extend in a direction intersecting the radial direction and the circumferential direction. According to this configuration, the first passage portion extends obliquely with respect to the thrust collar, that is, the rotation direction of the rotation shaft. For this reason, the rotational force of the thrust collar can be applied to the oil in the first passage portion in the direction from the radially outer side to the radially inner side. Therefore, the oil easily flows in the direction from the radially outer side to the radially inner side.

  (4) Preferably, in the configuration of (3), the first flange portion has a radial groove portion that is recessed in one axial end surface, extends in the radial direction, and is covered by the large diameter portion, The first flange portion and the body portion are recessed in an inner peripheral surface, extend in the axial direction, are covered with the small diameter portion, and have an axial groove portion connecting the through hole and the radial groove portion. Preferably, the first passage portion is disposed in the radial groove portion, and the second passage portion is disposed in the axial groove portion.

  According to this configuration, it is possible to secure not only the third passage portion but also the first passage portion and the second passage portion only by processing the thrust collar. For this reason, processing of a rotating shaft is unnecessary. However, the configuration of the above (3) naturally includes a form in which the rotating shaft is processed.

  (5) Preferably, in the configuration of the above (2), the rotation shaft includes a small diameter portion and a large diameter portion connected to one axial end of the small diameter portion and having a larger diameter than the small diameter portion, The thrust collar is connected to the body part fixed to the outer peripheral surface of the small-diameter part, and is connected to the large-diameter part with a diameter larger than that of the body part. A first flange portion having a through-hole penetrating to the other end surface in the direction, a second flange portion connected to the other axial end of the body portion and having a larger diameter than the body portion, the body portion and the first flange portion, A thrust bearing housing portion surrounded by the second flange portion, wherein a radial inner end portion of the thrust bearing is housed in the thrust bearing housing portion, and the thrust sliding interface is formed by the first flange. Between the first flange portion and the radially inner end of the thrust bearing, and between the second flange portion and the thrust bearing. The oil passage has a fourth passage portion that communicates with the radial sliding interface and the thrust bearing housing portion and is disposed in the through hole of the first flange portion. It is better to have a configuration.

  According to this configuration, oil can be flowed from the radial sliding interface to the thrust sliding interface via the fourth passage portion and the thrust bearing housing portion. The fourth passage portion is disposed in the through hole. The through hole penetrates the first flange portion from one axial end surface to the other axial end surface. For this reason, the through hole, that is, the fourth passage portion extends in a direction intersecting the radial direction. Accordingly, the oil is not easily affected by the thrust collar, that is, the centrifugal force caused by the rotation of the rotating shaft.

  (6) Preferably, in any one of the above configurations (2) to (5), the radial bearing is in sliding contact with the rotating shaft and the housing of the turbocharger, and the radial sliding interface is the rotating shaft. It is better to have a configuration partitioned between the outer peripheral surface of the radial bearing and the inner peripheral surface of the radial bearing, and between the inner peripheral surface of the housing and the outer peripheral surface of the radial bearing. The radial bearing is a so-called full floating type radial bearing. According to this configuration, the radial sliding interface is set on the inner peripheral surface side and the outer peripheral surface side of the radial bearing.

  According to the present invention, it is possible to provide a bearing device having a simple oil passage configuration.

It is a partial axial direction sectional view of a turbocharger with which a bearing device of a first embodiment is arranged. It is an enlarged view in the frame II of FIG. It is a fragmentary sectional view of the bearing device. It is a partial axial direction sectional view of the bearing device of a reference form. It is a fragmentary sectional view of the bearing device. (A) is a right end view of a thrust collar of a bearing device according to another embodiment (part 1). (B) is a right end view of a thrust collar of a bearing device according to another embodiment (part 2).

  Hereinafter, embodiments of the bearing device of the present invention will be described. In the following description, the left-right direction corresponds to the “axial direction” of the present invention, the left side corresponds to the “other axial direction” side of the present invention, and the right side corresponds to the “one axial direction” side of the present invention.

<First embodiment>
[Configuration of turbocharger]
First, the structure of the turbocharger in which the bearing device of this embodiment is arranged will be described. FIG. 1 shows a partial axial sectional view of a turbocharger in which the bearing device of the present embodiment is arranged. As shown in FIG. 1, the turbocharger 1 includes a housing 20, a rotating shaft 21, a compressor impeller 22, a turbine impeller (not shown), a retainer 24, a collar 25, a large diameter seal ring 26, a small diameter. The seal ring 27, the deflector 28, the nut 32, the snap ring 33, and the bearing device 4 are provided.

  The housing 20 constitutes the outer shell of the turbocharger 1. In the housing 20, a storage chamber 200, an oil chamber 201, a drain 202, and an oil supply path 203 are formed. The storage chamber 200 is open on the left side. The oil chamber 201 is disposed below the storage chamber 200 (below the rotating shaft 21 described later). The drain 202 is opened at the lower end of the oil chamber 201. The oil supply path 203 is open to the storage chamber 200. Lubricating oil is supplied at a predetermined pressure from an oil supply path 203 to a bearing device 4 to be described later, and is discharged from a drain 202 via an oil chamber 201.

  The rotating shaft 21 has a stepped round bar shape and is inserted into the storage chamber 200. The rotating shaft 21 extends in the left-right direction. The rotating shaft 21 includes a small diameter portion 210 and a large diameter portion 211. The large diameter portion 211 has a larger diameter than the small diameter portion 210. The large diameter portion 211 continues to the right side of the small diameter portion 210. The nut 32 is screwed to the left end of the small diameter portion 210.

  As will be described later, the compressor impeller 22, the collar 25, and the thrust collar 41 are sandwiched and fixed between the nut 32 and the step portion between the large diameter portion 211 and the small diameter portion 210. Yes. These members rotate integrally with the rotating shaft 21.

  The compressor impeller 22 is disposed on the right side of the nut 32. The compressor impeller 22 is exposed to the compressor chamber 23. On the other hand, a turbine impeller is fixed to the right end of the rotating shaft 21.

  The collar 25 has a cylindrical shape. The collar 25 is disposed on the right side of the compressor impeller 22. The retainer 24 has a cup shape. A through hole 240 is formed in the center of the retainer 24 in the radial direction. The retainer 24 is disposed in the storage chamber 200. The collar 25 is inserted through the through hole 240 of the retainer 24. The large-diameter seal ring 26 is interposed between the inner peripheral surface of the storage chamber 200 and the outer peripheral surface of the retainer 24. The small-diameter seal ring 27 is interposed between the inner peripheral surface of the through hole 240 and the outer peripheral surface of the collar 25. The snap ring 33 is disposed in the storage chamber 200. The snap ring 33 is disposed on the left side (outside) of the retainer 24. The snap ring 33 fixes the retainer 24. The deflector 28 is fixed to the inner peripheral surface of the retainer 24. The deflector 28 is disposed on the radially outer side of the collar 25.

[Configuration of bearing device]
Next, the configuration of the bearing device of the present embodiment will be described. FIG. 2 shows an enlarged view in the frame II of FIG. In FIG. 3, the fragmentary sectional view of the bearing apparatus of this embodiment is shown. For convenience of explanation, the rotary shaft 21 is shown through.

  As shown in FIGS. 1 to 3, the bearing device 4 of this embodiment includes a radial bearing 40, a thrust collar 41, a thrust bearing 42, an oil passage L, radial sliding interfaces R <b> 1 and R <b> 2, and a thrust slide. Dynamic interfaces T1 and T2.

  The radial bearing 40 is a full floating type bearing. The radial bearing 40 is a sliding bearing. The radial bearing 40 has a cylindrical shape. The radial bearing 40 has a through hole 400 extending in the radial direction. The radial bearing 40 is interposed between the inner peripheral surface of the housing 20 and the outer peripheral surface of the large-diameter portion 211 of the rotary shaft 21.

  As indicated by a thick line in FIG. 2, the radial sliding interface R <b> 1 is disposed between the inner peripheral surface of the housing 20 and the outer peripheral surface of the radial bearing 40. An oil film is formed on the radial sliding interface R1 by the oil O supplied from the oil supply path 203. As indicated by a thick line in FIG. 2, the radial sliding interface R <b> 2 is disposed between the outer peripheral surface of the large diameter portion 211 and the inner peripheral surface of the radial bearing 40. An oil film is formed on the radial sliding interface R2 by the oil O supplied from the through hole 400. When the rotating shaft 21 rotates, the radial bearing 40 rotates in the same direction as the rotating shaft 21 at a slower speed than the rotating shaft 21.

  The thrust collar 41 is mounted on the outer peripheral surface of the small diameter portion 210. As described above, the thrust collar 41 is fixed to the outer peripheral surface of the small diameter portion 210 together with the compressor impeller 22 and the collar 25 by the screwing force of the nut 32.

  The thrust collar 41 includes a body portion 410, a first flange portion 411, a second flange portion 412, and a thrust bearing housing portion 413. The body 410 has a cylindrical shape. The body 410 includes a through hole 410a. The through hole 410a penetrates the body portion 410 in the radial direction.

  The first flange portion 411 has a disk shape having a larger diameter than the body portion 410. The first flange portion 411 continues to the right side of the body portion 410. The right end surface of the first flange portion 411 is in contact with the left end surface of the large diameter portion 211. A radial groove 411 a is recessed in the right end surface of the first flange portion 411. The radial groove 411a extends in the radial direction. The radially outer end of the radial groove 411a is sealed. The radial groove 411a is covered by the left end surface of the large diameter portion 211 from the right side. On the inner peripheral surfaces of the first flange portion 411 and the body portion 410, an axial groove portion 410b is recessed. The axial groove 410b extends in the axial direction. The axial groove portion 410b is covered with the outer peripheral surface of the small diameter portion 210 from the radially inner side. The right end of the axial groove 410b is continuous with the radially inner end of the radial groove 411a. The left end of the axial groove portion 410b is continuous with the radially inner end of the through hole 410a.

  The second flange portion 412 has a disk shape having a larger diameter than the body portion 410. The second flange portion 412 continues to the left side of the body portion 410.

  The thrust bearing housing portion 413 includes an outer peripheral surface of the body portion 410, a left surface of the first flange portion 411 (included in the “axially oriented surface” of the present invention), and a right surface of the second flange portion 412 (“ Included in the “axially oriented plane”.

  The thrust bearing 42 has a partial disk shape. The thrust bearing 42 is a sliding bearing. The radial outer end 421 of the thrust bearing 42 is sandwiched and fixed between the retainer 24 and the housing 20 from the left and right directions. A radially inner end portion 420 of the thrust bearing 42 is accommodated in the thrust bearing accommodating portion 413.

  As shown by a thick line in FIG. 2, the thrust sliding interface T1 is formed between the left surface of the first flange portion 411 and the right surface of the radially inner end portion 420 (included in the “axially oriented surface” of the present invention). Arranged between. An oil film is formed on the thrust sliding interface T1 by oil O supplied from an oil passage L described later. As shown by a thick line in FIG. 2, the thrust sliding interface T2 is formed between the right surface of the second flange portion 412 and the left surface of the radially inner end portion 420 (included in the “axially oriented surface” of the present invention). Arranged between. An oil film is formed on the thrust sliding interface T2 by oil O supplied from an oil passage L described later.

  The oil passage L includes a first passage portion L1, a second passage portion L2, and a third passage portion L3. The 1st channel | path part L1 is arrange | positioned at the radial direction groove part 411a. The second passage portion L2 is disposed in the axial groove portion 410b. The third passage portion L3 is disposed in the through hole 410a.

[How oil flows]
Next, how oil flows in the bearing device of this embodiment will be described. As shown in FIG. 2, the oil O is first supplied from the oil supply path 203 to the radial sliding interfaces R1 and R2 at a predetermined hydraulic pressure. An oil film is formed on the radial sliding interfaces R1 and R2. Next, the oil O flows into the first passage portion L1 from the radial sliding interfaces R1, R2. The oil O flows from the radially outer side toward the radially inner side. Subsequently, the oil O flows into the second passage portion L2. The oil O flows from the right side to the left side. Then, the oil O flows into the third passage portion L3. The oil O flows from the radially inner side toward the radially outer side. Thereafter, the oil O flows into the thrust bearing housing 413. The oil O is divided into the right side and the left side from the downstream end of the second passage portion L2. The oil O branched to the right side is supplied to the thrust sliding interface T1. An oil film is formed on the thrust sliding interface T1. The oil O branched to the left side is supplied to the thrust sliding interface T2. An oil film is formed on the thrust sliding interface T2.

  Thus, between the radial sliding interfaces R1, R2 and the thrust sliding interfaces T1, T2, the first passage portion L1, the second passage portion L2, the third passage portion are arranged from the upstream side toward the downstream side. L3, a thrust bearing accommodating portion 413 is disposed. Oil O is guided from the radial sliding interfaces R1 and R2 to the thrust sliding interfaces T1 and T2 through these spaces.

[Function and effect]
Next, the effect of the bearing device of this embodiment will be described. According to the bearing device 4 of the present embodiment, the oil passage L is shared by the radial bearing 40 and the thrust bearing 42. For this reason, as compared with the case where the oil passage L is independent between the radial bearing 40 and the thrust bearing 42, the configuration of the oil passage L and the turbocharger 1 is simplified.

  Further, according to the bearing device 4 of the present embodiment, the oil O is supplied to the thrust sliding interfaces T1 and T2 without performing complicated hole machining on the thrust bearing 42 even though the thrust bearing 42 is a sliding bearing. can do.

  Further, according to the bearing device 4 of the present embodiment, the first passage portion L1, the second passage portion L2, the third passage portion L3, and the thrust bearing housing from the radial sliding interfaces R1, R2 to the thrust sliding interfaces T1, T2. The oil O can be flowed through the part 413. In particular, in the third passage portion L3, the oil O can smoothly flow from the radially inner side to the radially outer side by utilizing the centrifugal force generated by the rotation of the thrust collar 41, that is, the rotating shaft 21.

  Further, according to the bearing device 4 of the present embodiment, the oil passage L can be secured only by forming the radial groove portion 411a, the axial groove portion 410b, and the through hole 410a in the thrust collar 41. For this reason, the process of the rotating shaft 21 is unnecessary.

< Reference form>
The difference between the bearing device of the reference form and the bearing device of the first embodiment is that the oil passage extends linearly. Here, only differences will be described. FIG. 4 shows a partial axial sectional view of the bearing device of the reference embodiment. In addition, about the site | part corresponding to FIG. 2, it shows with the same code | symbol. FIG. 5 shows a partial cross-sectional view of the bearing device. In addition, about the site | part corresponding to FIG. 3, it shows with the same code | symbol.

  As shown in FIGS. 4 and 5, the first flange portion 411 of the thrust collar 41 includes a through hole 411b. The through hole 411b passes through the first flange portion 411. The through hole 411b extends linearly from the upper right to the lower left.

  The oil passage L includes a fourth passage portion L4. The fourth passage portion L4 is disposed in the through hole 411b. The oil O flows into the thrust bearing accommodating portion 413 from the radial sliding interfaces R1 and R2 via the fourth passage portion L4. Then, the oil O is supplied to the thrust sliding interfaces T1 and T2.

The bearing device according to the reference embodiment and the bearing device according to the first embodiment have the same functions and effects with respect to parts having the same configuration. Further, according to the bearing device 4 of the reference form, the through hole 411b, that is, the fourth passage portion L4 extends in a direction intersecting the radial direction. Therefore, the flow of the oil O is not easily affected by the centrifugal force caused by the rotation of the thrust collar 41, that is, the rotary shaft 21. The oil passage L is linear. For this reason, compared with the case where the oil passage L is curved, the flow path resistance when the oil O flows is small.

<Others>
The embodiments of the bearing device of the present invention have been described above. However, the embodiment is not particularly limited to the above embodiment. Various modifications and improvements that can be made by those skilled in the art are also possible.

  The shape, length, and number of arrangement of the oil passage L are not particularly limited. FIG. 6A shows a right end view of the thrust collar of the bearing device of the other embodiment (part 1). FIG. 6B is a right end view of the thrust collar of the bearing device according to another embodiment (part 2). In addition, about the site | part corresponding to FIG. 2, it shows with the same code | symbol.

  As shown in FIG. 6A, each of the four first passage portions L1 has a linear shape. The first passage portion L1 extends in a direction intersecting the radial direction and the circumferential direction. The first passage portion L1 is inclined in the direction opposite to the rotational direction A with respect to the radial direction from the radially inner side toward the radially outer side. If it carries out like this, with respect to the oil which flows through the 1st channel | path part L1, the component of the rotational force of the thrust collar 41 can be made to act in the direction which goes to a radial inside from a radial direction outer side. Therefore, the oil easily flows in the direction from the radially outer side to the radially inner side.

  As shown in FIG. 6B, each of the three first passage portions L1 has an arc shape that swells outward in the radial direction. The first passage portion L1 extends in a direction intersecting the radial direction and the circumferential direction. The first passage portion L1 is inclined in the direction opposite to the rotational direction A with respect to the radial direction from the radially inner side toward the radially outer side. For the same reason as FIG. 6A, this makes it easier for oil to flow from the radially outer side to the radially inner side.

  The arrangement method of the oil passage L is not particularly limited. The oil passage L may be secured by disposing a recess in at least one of the thrust collar 41 and the rotating shaft 21. Similarly, the oil passage L may be secured by arranging convex portions on at least one of the thrust collar 41 and the rotating shaft 21.

  At least one of the radial bearing 40 and the thrust bearing 42 may be a rolling bearing. Even in this case, the oil O can be supplied from the radial bearing 40 to the thrust bearing 42 via the oil passage L.

  In the above embodiment, a full floating type bearing is used as the radial bearing 40. The radial bearing 40 slides on both the inner peripheral surface of the housing 20 and the outer peripheral surface of the large diameter portion 211. For this reason, two radial sliding interfaces R1 and R2 are formed. However, a semi-floating type bearing may be used as the radial bearing 40. In this case, the radial bearing 40 is fixed to the inner peripheral surface of the housing 20. The radial bearing 40 slides only on the outer peripheral surface of the large diameter portion 211. For this reason, a single radial sliding interface R2 is formed.

1: turbocharger, 20: housing, 200: storage chamber, 201: oil chamber, 202: drain, 203: oil supply path, 21: rotating shaft, 210: small diameter portion, 211: large diameter portion, 22: compressor impeller, 23: compressor chamber, 24: retainer, 240: through hole, 25: collar, 26: large diameter seal ring, 27: small diameter seal ring, 28: deflector, 32: nut, 33: snap ring.
4: bearing device, 40: radial bearing, 400: through hole, 41: thrust collar, 410: trunk, 410a: through hole, 410b: axial groove, 411: first flange, 411a: radial groove, 411b : Through-hole, 412: second flange portion, 413: thrust bearing housing portion, 42: thrust bearing, 420: radially inner end portion, 421: radially outer end portion.
L: Oil passage, L1: First passage portion, L2: Second passage portion, L3: Third passage portion, L4: Fourth passage portion, O: Oil, R1: Radial sliding interface, R2: Radial sliding interface T1: Thrust sliding interface, T2: Thrust sliding interface.

Claims (3)

A radial bearing that rotatably supports the rotating shaft of the turbocharger from the radial direction;
A thrust collar fixed to the outer peripheral surface of the rotating shaft;
A thrust bearing that rotatably supports the thrust collar from the axial direction;
A bearing device comprising:
Further, the radial bearing and the thrust bearing communicate with each other, and an oil passage that guides oil from the radial bearing to the thrust bearing is provided,
The radial bearing is in sliding contact with the rotating shaft from a radial direction,
The thrust bearing is in sliding contact with the thrust collar from the axial direction,
A radial sliding interface defined between the outer peripheral surface of the rotating shaft and the inner peripheral surface of the radial bearing;
A thrust sliding interface defined between an axial orientation surface facing the axial direction of the thrust collar and an axial orientation surface facing the axial direction of the thrust bearing;
With
The oil passage communicates the radial sliding interface and the thrust sliding interface, guides the oil from the radial sliding interface to the thrust sliding interface,
The rotating shaft has a small diameter portion and a large diameter portion connected to one end in the axial direction of the small diameter portion and having a larger diameter than the small diameter portion,
The thrust collar includes a body portion fixed to the outer peripheral surface of the small-diameter portion, a first flange portion connected to one end in the axial direction of the body portion and having a larger diameter than the body portion and in contact with the large-diameter portion, A second flange portion connected to the other axial end of the body portion and having a larger diameter than the body portion; and a thrust bearing housing portion surrounded by the body portion, the first flange portion, and the second flange portion. And
The radial inner end of the thrust bearing is accommodated in the thrust bearing accommodating portion,
The thrust sliding interface is defined between the first flange portion and the radially inner end portion of the thrust bearing, and between the second flange portion and the radially inner end portion of the thrust bearing. ,
The body portion has a through-hole penetrating from its inner peripheral surface to its outer peripheral surface,
The oil passage communicates with the radial sliding interface and communicates with the first passage portion defined between the first flange portion and the large-diameter portion and the thrust bearing housing portion. bearing device for a third passage portion disposed in the hole, and a second passage portion communicating between the said first passage portion and said third passage, wherein Rukoto to have a.   The first flange portion is recessed in one axial end surface, has a radial groove extending in the radial direction and covered by the large diameter portion,
  The first flange portion and the body portion are recessed in an inner peripheral surface, extend in the axial direction, are covered with the small diameter portion, and have an axial groove portion connecting the through hole and the radial groove portion. Have
  The first passage portion is disposed in the radial groove portion,
  The bearing device according to claim 1, wherein the second passage portion is disposed in the axial groove portion.   The radial bearing is in sliding contact with the rotating shaft and the turbocharger housing,
  The radial sliding interface is defined between an outer peripheral surface of the rotating shaft and an inner peripheral surface of the radial bearing, and between an inner peripheral surface of the housing and an outer peripheral surface of the radial bearing. The bearing device according to claim 2.

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