JP6087271B2 - Turbocharger bearing housing - Google Patents

Description

  The present invention relates to a technology of a bearing housing for a turbocharger provided in an internal combustion engine.

  Conventionally, the technology of a bearing housing of a turbocharger provided in an internal combustion engine is known. For example, as described in Patent Document 1.

  Patent Document 1 describes a turbocharger bearing housing (bearing housing) that is divided into a plurality of housings (a turbine side housing and a compressor side housing) and formed by machining a cooling water passage and a lubricating oil passage. ing.

  In this way, the bearing housing is divided and the cooling water passage and the lubricating oil passage are formed by machining, so that the core for forming the cooling water passage and the lubricating oil passage is used at the stage of casting the bearing housing. There is no need.

  In the technique described in Patent Document 1, when a plurality of divided housings (the turbine side housing and the compressor side housing) are fixed to each other to form one bearing housing, a seal is provided between the plurality of housings. A material (metal gasket) is interposed and fixed to each other by a fastener such as a bolt. Thereby, it is possible to prevent the coolant and the lubricating oil from leaking from the mating surfaces (divided surfaces) of the plurality of housings.

  However, when the metal gasket is provided on the dividing surface as described above, it is disadvantageous in that the design of the cooling water passage and the lubricating oil passage is restricted.

  Specifically, in order to ensure the sealing performance by the metal gasket, it is necessary to provide a certain amount of space between adjacent spaces (for example, between the cooling water passage and the lubricating oil passage). In particular, when a bead for improving the sealing performance is formed on the metal gasket, it is necessary to arrange the bead and provide an interval sufficient to ensure a sufficient sealing performance. For this reason, restrictions arise in the design (position and size) of the cooling water passage and the lubricating oil passage. As a result, for example, it may be difficult to increase the cooling water channel and improve the cooling performance.

JP2013-209932A

  The present invention has been made in view of the above circumstances, and a problem to be solved is to provide a bearing housing for a turbocharger that can increase the degree of freedom in designing cooling water passages and lubricating oil passages. It is.

  The problem to be solved by the present invention is as described above. Next, means for solving the problem will be described.

That is, in claim 1, a bearing housing of a turbocharger that rotatably supports a shaft connecting a compressor wheel and a turbine wheel, the bearing housing being divided into a first housing and a second housing, A cooling water passage for flowing cooling water and / or a lubricating oil passage for flowing lubricating oil are formed on the dividing surfaces of the first housing and the second housing, and the first housing and the second housing Are not contacted via a seal member and are joined by welding, so that the first housing and the second housing are integrally fixed and the cooling water channel from the dividing surface and / or the loss of cooling water and / or lubricant of the lubricating oil passage is prevented, said second Haujin and the first housing Are joined to the outer surfaces of the first housing and the second housing, and the inner surfaces of the first housing and the second housing, and a part of the bearing housing includes the inner surface. It is formed by a closing body that closes the space .

According to a second aspect of the present invention, the first housing and the second housing are joined over the entire circumference of the portion where the first housing and the second housing are in contact with each other .

  As effects of the present invention, the following effects can be obtained.

In the present invention , since the leakage of cooling water and / or lubricating oil can be prevented by joining the first housing and the second housing, a sealing material is provided between the first housing and the second housing. There is no need to provide it. This eliminates the need for a space for arranging the sealing material to ensure sufficient sealing performance, and increases the degree of freedom in design (options such as the position and shape of the cooling water channel and / or the lubricating oil channel). Thereby, for example, the cooling performance can be improved by enlarging the cooling water channel or by forming the cooling water channel at a portion where the temperature tends to be higher. Moreover, since the sealing material can be eliminated, the number of parts can be reduced.

1 is a side sectional view showing an overall configuration of a turbocharger including a bearing housing according to an embodiment of the present invention. Similarly, the exploded perspective view of a bearing housing. Similarly, a plan view. Similarly, a rear view. AA sectional drawing of FIG. FIG. 6 is an exploded view of FIG. 5. BB sectional drawing of FIG. CC sectional drawing of FIG. DD sectional drawing of FIG. (A) Side surface sectional drawing which showed the welding location of a compressor side housing and a turbine side housing. (B) Similarly, an enlarged view. (A) Side surface sectional drawing which showed the welding location of the turbine side housing and the obstruction | occlusion body. (B) Similarly, an enlarged view.

  Below, according to the arrow shown in the figure, the up-down direction, the front-back direction, and the left-right direction are defined.

  First, the outline of the structure of the turbocharger 5 which comprises the bearing housing 40 which concerns on one Embodiment of this invention is demonstrated using FIG.

  The turbocharger 5 is for sending compressed air into a cylinder of an internal combustion engine (engine). The turbocharger 5 mainly includes a shaft 10, a compressor wheel 20, a turbine wheel 30, a bearing housing 40, a slide bearing 60, a thrust collar 70, and a thrust bearing 90.

  The shaft 10 connects a compressor wheel 20 and a turbine wheel 30 described later. The shaft 10 is disposed with its longitudinal direction (axial direction) directed in the front-rear direction.

  The compressor wheel 20 has a plurality of blades and compresses air by being driven to rotate. The compressor wheel 20 is fixed to the rear end portion of the shaft 10.

  The turbine wheel 30 has a plurality of blades, and generates driving force by rotating by receiving exhaust from the engine. The turbine wheel 30 is formed integrally with the front end portion of the shaft 10.

  The bearing housing 40 is a substantially box-shaped member that rotatably supports the shaft 10. A bearing portion 114 is formed in the bearing housing 40.

  The detailed configuration of the bearing housing 40 will be described later.

  The slide bearing 60 is a substantially cylindrical bearing that rotatably supports the shaft 10. The slide bearing 60 is disposed at the front end portion and the rear end portion of the bearing portion 114 of the bearing housing 40, respectively. The shaft 10 is inserted through the slide bearing 60.

  The thrust collar 70 is formed in a substantially cylindrical shape and is arranged in the front-rear direction. The shaft 10 is inserted through the thrust collar 70. The thrust collar 70 is fixed so as not to rotate relative to the shaft 10. A thrust bearing 90 is fitted on the middle portion of the thrust collar 70 before and after. The thrust bearing 90 is disposed in contact with the bearing housing 40 at the rear of the bearing portion 114. In this way, the thrust bearing 90 receives an axial load applied to the shaft 10. A seal plate 80 for preventing the lubricant from leaking from the bearing housing 40 toward the compressor wheel 20 is disposed behind the thrust bearing 90.

  Next, the configuration of the bearing housing 40 will be described in detail with reference to FIGS.

  The bearing housing 40 is formed by a plurality of divided members. The bearing housing 40 mainly includes a compressor side housing 110, a turbine side housing 130, and a closing body 150.

  A compressor-side housing 110 shown in FIGS. 2 to 9 is an embodiment of the first housing according to the present invention. The compressor side housing 110 is a member constituting a rear side (compressor wheel 20 side) portion of the bearing housing 40. The compressor side housing 110 is formed in a substantially box shape by forging. The compressor-side housing 110 mainly includes a central convex portion 111, an outer ring convex portion 112, a partition convex portion 113, a bearing portion 114, a supply oil passage 115, a first discharge oil passage 116, a second discharge oil passage 117, and a water passage recess. 118, the 1st supply water channel 119, the 2nd supply water channel 120, the 1st discharge water channel 121, and the 2nd discharge water channel 122 are formed.

  The central convex portion 111 shown in FIGS. 2, 5, 6, 7, and 9 is a portion that protrudes forward from a substantially central portion of the front surface of the compressor-side housing 110. The central convex portion 111 is formed in a columnar shape whose axis is directed in the front-rear direction. The front end of the central convex portion 111 extends forward to a predetermined position.

  The outer ring convex portion 112 is a portion protruding forward from the periphery of the central convex portion 111 on the front surface of the compressor-side housing 110. The outer ring convex portion 112 is formed concentrically with the central convex portion 111 in front view, and is formed so as to surround the central convex portion 111 from the outside. As a result, a concave portion having a circular shape in front view is formed between the central convex portion 111 and the outer ring convex portion 112. The front end of the outer ring convex portion 112 extends forward. The front end of the outer ring convex portion 112 is formed so as to be located behind the front end of the central convex portion 111 (see FIG. 7).

  2, 5, 6, and 9 is a portion protruding forward from the front surface of the compressor-side housing 110. The partition convex part 113 is formed in a substantially rectangular parallelepiped shape. The partition convex portion 113 is formed between the upper end portion of the central convex portion 111 and the upper end portion of the outer ring convex portion 112. As a result, the vicinity of the upper end portion of the concave portion having a circular shape in front view formed between the central convex portion 111 and the outer ring convex portion 112 is partitioned, and the concave portion is a concave portion having a circular shape in front view (a concave portion 118 for a water channel described later). (See FIGS. 2 and 9). The front end of the partition convex portion 113 extends forward. The front end of the partition convex portion 113 is formed so as to be located behind the front end of the central convex portion 111 and ahead of the front end of the outer ring convex portion 112 (see FIGS. 5 and 6).

  The bearing portion 114 shown in FIGS. 4 to 6 is a portion that supports the shaft 10 so as to be indirectly rotatable. The bearing portion 114 is formed by a hole that passes through substantially the center of the compressor-side housing 110 (on the same axis as the central convex portion 111) in the front-rear direction. The bearing portion 114 is formed to have a circular cross section. The front end of the bearing portion 114 is opened at the front end of the central convex portion 111.

  A supply oil passage 115 shown in FIGS. 5, 6, and 8 is an oil passage for guiding (supplying) lubricating oil supplied from the outside to the bearing portion 114. One end of the supply oil passage 115 is communicated with the bottom surface of the compressor side housing 110. The other end of the supply oil passage 115 communicates with the right side surface in the vicinity of the rear end portion of the bearing portion 114. The supply oil passage 115 is formed in a straight line from one end to the other end.

  The first drain oil passage 116 shown in FIGS. 2, 5, 6, and 8 is an oil passage for guiding (discharging) the lubricating oil that has lubricated the bearing portion 114 to the outside. The first oil discharge passage 116 is formed below the bearing portion 114 so as to penetrate the compressor-side housing 110 in a straight line in the front-rear direction. The front end of the first discharge oil passage 116 is opened at the front end of the central convex portion 111.

  A communication notch 116 a is formed at the front end of the central protrusion 111, which is notched so as to communicate the front end of the bearing portion 114 and the front end of the first discharge oil passage 116.

  5, 6, and 8 is an oil passage for guiding (discharging) the lubricating oil that has lubricated the bearing portion 114 to the outside. One end of the second discharge oil passage 117 is communicated with the vicinity of the rear end portion of the first discharge oil passage 116. The other end of the second discharge oil passage 117 is communicated with the bottom surface of the compressor side housing 110. The second drain oil passage 117 is formed in a straight line in the vertical direction from one end to the other end.

  2, 5, 6, 7, and 9 is a portion (concave portion) for forming a water channel for cooling water to flow around the bearing portion 114. The water channel recess 118 is an arc-shaped recess in front view formed by the central convex portion 111, the outer ring convex portion 112, and the partition convex portion 113 as described above.

  A first supply water channel 119 shown in FIGS. 2, 3, and 8 is a water channel for guiding (supplying) cooling water supplied from the outside to the water channel recess 118. One end of the first supply water channel 119 is communicated with the upper surface of the compressor-side housing 110. The other end of the first supply water channel 119 extends downward to a predetermined position. The first supply water channel 119 is formed in a straight line in the vertical direction from one end to the other end.

  The second supply water channel 120 shown in FIGS. 8 and 9 is a water channel for guiding (supplying) cooling water supplied from the outside to the water channel recess 118. One end of the second supply water channel 120 is communicated with the other end (lower end) of the first supply water channel 119. The other end of the second supply water channel 120 is communicated with one end (upper right end) of the water channel recess 118. The second supply water channel 120 is formed in a straight line in the front-rear direction from one end to the other end.

  The first discharge water channel 121 shown in FIGS. 7, 8, and 9 is a water channel for guiding (discharging) the cooling water in the water channel recess 118 to the outside. One end of the first discharge water channel 121 communicates with the other end (upper left end) of the water channel recess 118. The other end of the first discharge water channel 121 extends rearward to a predetermined position. The first discharge water channel 121 is formed in a straight line in the front-rear direction from one end to the other end.

  The second drainage channel 122 shown in FIGS. 2, 3, 7 and 8 is a channel for guiding (discharging) the cooling water in the recess 118 for the channel to the outside. One end of the second discharge water passage 122 is communicated with the other end (rear end) of the first discharge water passage 121. The other end of the second discharge water passage 122 communicates with the upper surface of the compressor side housing 110. The second drainage channel 122 is formed in a straight line in the vertical direction from one end to the other end.

  A turbine housing 130 shown in FIGS. 2 to 9 is an embodiment of the second housing according to the present invention. The turbine side housing 130 is a member that constitutes a front side (turbine wheel 30 side) portion of the bearing housing 40. The turbine side housing 130 is formed in a substantially disc shape by forging. The turbine-side housing 130 is mainly formed with a through hole 131, a closing body receiving recess 132, a water channel recess 133, and a bonding recess 134.

  The through holes 131 shown in FIGS. 2, 5, and 6 are formed so as to penetrate substantially the center of the turbine-side housing 130 in the front-rear direction. The through hole 131 is formed to have a circular cross section. The diameter (diameter) of the through hole 131 is formed to be smaller than the diameter of the central convex portion 111 of the compressor side housing 110.

  The closing body receiving recess 132 is a portion (recess) for receiving the closing body 150 described later. The closing body receiving recess 132 is formed so as to be recessed toward the rear substantially at the center of the front surface of the turbine-side housing 130 (around the through hole 131). The closure receiving recess 132 is formed to have a circular shape when viewed from the front.

  The water channel recess 133 shown in FIGS. 5, 6, 7, and 9 is a portion (recess) for forming a water channel for cooling water to flow around the bearing portion 114 of the compressor side housing 110. The water channel recess 133 is formed so that the approximate center (around the through hole 131) of the rear surface of the turbine housing 130 is recessed forward. The water channel recess 133 is formed to have a circular shape when viewed from the back. The diameter (diameter) of the water channel recess 133 is formed to be the same as the diameter of the water channel recess 118 of the compressor-side housing 110 (the diameter of the inner surface of the outer ring projection 112).

  5, 6, and 7 is a portion (concave portion) for receiving the central convex portion 111 of the compressor-side housing 110. The joining recess 134 is formed so as to be further recessed forward in the approximate center of the rear surface of the turbine-side housing 130, more specifically, the approximate center of the water channel recess 133 (around the through hole 131). The bonding recess 134 is formed to have a circular shape when viewed from the back. The diameter (diameter) of the bonding recess 134 is formed to be substantially the same as the diameter of the central protrusion 111 of the compressor-side housing 110.

  2, 3, 5, 6, and 7 is a member that constitutes an end portion on the front side (turbine wheel 30 side) of the bearing housing 40. The closing body 150 is formed into a substantially disk shape (circular shape in front view) by forging. The diameter (diameter) of the closing body 150 is formed to be substantially the same as the diameter of the closing body receiving recess 132 of the turbine-side housing 130. A through hole 151 is mainly formed in the closing body 150.

  The through hole 151 is formed so as to penetrate substantially the center of the closing body 150 in the front-rear direction. The through hole 151 is formed to have a circular cross section. The diameter (diameter) of the through hole 151 is formed to be substantially the same as the diameter of the bearing portion 114 of the compressor side housing 110.

  Next, the bearing housing 40 is formed by assembling the compressor-side housing 110, the turbine-side housing 130, and the closing body 150, which are configured as described above, with reference to FIGS. 1, 5, 9, 10, and 11. A method will be described.

  First, as shown in FIG. 10, the compressor side housing 110 and the turbine side housing 130 are assembled. Specifically, the front surface of the compressor side housing 110 and the back surface of the turbine side housing 130 are brought into contact with each other. At this time, the central convex portion 111 of the compressor side housing 110 is fitted into the joint concave portion 134 of the turbine side housing 130. At this time, the front end of the outer ring convex portion 112 of the compressor side housing 110 is brought into contact with the back surface of the turbine side housing 130. Hereinafter, when the front surface of the compressor-side housing 110 and the rear surface of the turbine-side housing 130 are brought into contact with each other as described above, the entire area facing each other is referred to as a “divided surface” of the bearing housing 40.

  And the part (welding location W1) where the front end of the outer ring convex part 112 of the compressor side housing 110 and the back surface of the turbine side housing 130 contacted is welded over the entire periphery. At this time, since the welding location W1 is on the outer surface of the bearing housing 40 (the compressor side housing 110 and the turbine side housing 130), the welding apparatus does not interfere with the bearing housing 40 and can be easily welded. it can.

  Further, a portion (welding point W2) where the central convex portion 111 of the compressor side housing 110 and the concave portion for joining 134 of the turbine side housing 130 are in contact is welded over the entire circumference. At this time, although the welded portion W1 is on the inner surface of the bearing housing 40 (the compressor-side housing 110 and the turbine-side housing 130), the through-hole 131 of the turbine-side housing 130 is widely opened. The welding location W2 can be welded from the front using a welding instrument. That is, also when welding the welding location W2, the welding operation can be easily performed without the welding instrument interfering with the bearing housing 40.

  By assembling the compressor-side housing 110 and the turbine-side housing 130 in this way, an arc shape in front view that surrounds the periphery of the bearing portion 114 by the water channel recess 118 and the water channel recess 133 on the split surface of the bearing housing 40. A (substantially circular) cooling water channel is formed (see FIG. 9).

  Further, the bearing 114 and the first exhaust oil passage 116 of the compressor side housing 110 and the through hole 131 of the turbine side housing 130 are connected in communication, and a connecting portion (divided surface) between the compressor side housing 110 and the turbine side housing 130 is connected. ) Is formed (see FIG. 5).

  In addition, since the split surfaces of the bearing housing 40 are joined by welding, leakage of cooling water and lubricating oil from the split surfaces does not occur.

Next, as shown in FIG. 11, the closing body 150 is assembled to the turbine side housing 130. Specifically, the closing body 150 is fitted into the closing body receiving recess 132 of the turbine side housing 130. Thereby, the space inside the bearing housing 40 including the welding point W2 is closed from the front.
In FIG. 11, since the through hole 151 of the closing body 150 is opened, the space inside the bearing housing 40 is not completely closed. However, in practice, as shown in FIG. 1, the through hole 151 of the closing body 150 is closed by the shaft 10, so that the space inside the bearing housing 40 is closed by the closing body 150.

  And the part (outer peripheral part of the said closure body 150) (welding location W3) which the closure body receiving recessed part 132 and the closure body 150 of the turbine side housing 130 contact | abutted is welded over the perimeter. At this time, since the welding point W3 is on the front end surface of the bearing housing 40, the welding tool does not interfere with the bearing housing 40, and the welding operation can be easily performed.

Next, the manner in which cooling water and lubricating oil circulate in the bearing housing 40 configured as described above will be described with reference to FIGS.
In the figure, the flow of cooling water is indicated by solid arrows, and the flow of lubricating oil is indicated by broken arrows.

  The cooling water supplied from the outside passes through the first supply water channel 119 and the second supply water channel 120 (see FIG. 8) and enters the arc-shaped cooling water channel formed by the water channel recess 118 and the water channel recess 133. Supplied (see FIG. 9). The cooling water flows through the arc-shaped cooling water channel so as to surround the periphery of the bearing portion 114, and then is discharged to the outside through the first discharge water channel 121 and the second discharge water channel 122 (FIG. 7 and FIG. 7). (See FIG. 8).

  Further, the lubricating oil supplied from the outside is supplied to the bearing portion 114 via the supply oil passage 115 (see FIG. 8). Lubricating oil lubricates the inside of the bearing portion 114 (the shaft 10 and the plain bearing 60 (see FIG. 1)) and then passes from the front end of the bearing portion 114 through the communication cutout portion 116a (or the space inside the through hole 131). And flows out to the first discharge oil passage 116 (see FIG. 5). The lubricating oil is discharged to the outside through the first discharge oil passage 116 and the second discharge oil passage 117.

  At this time, the cooling water passage through which the cooling water flows and the lubricating oil passage through which the lubricating oil flows are partitioned so as not to leak by welding (welding point W2 in FIG. 10). Therefore, it is possible to prevent one of the cooling water or the lubricating oil from leaking out and mixing into the other through the split surface of the bearing housing 40.

  As described above, the bearing housing 40 of the turbocharger 5 according to the present embodiment is the bearing housing 40 of the turbocharger 5 that rotatably supports the shaft 10 that connects the compressor wheel 20 and the turbine wheel 30. The housing 40 is divided into a compressor-side housing 110 (first housing) and a turbine-side housing 130 (second housing), and cooling is performed so that cooling water flows on the dividing surfaces of the compressor-side housing 110 and the turbine-side housing 130. A water passage and a lubricating oil passage through which lubricating oil flows are formed, and the compressor side housing 110 and the turbine side housing 130 are joined together, so that the compressor side housing 110 and the turbine side housing 130 are integrally fixed. Wherein in which leakage of the cooling water and lubricating oil cooling channel and the lubricating oil passage can be prevented from the dividing plane while being.

With this configuration, the compressor-side housing 110 and the turbine-side housing 130 can be joined to prevent leakage of cooling water and lubricating oil. There is no need to provide a sealing material between them. This eliminates the need for a space for arranging the sealing material to ensure sufficient sealing performance, and increases the degree of freedom in design (options such as the position and shape of the cooling water channel and / or the lubricating oil channel). Thereby, for example, the cooling performance can be improved by enlarging the cooling water channel or by forming the cooling water channel at a portion where the temperature tends to be higher. Moreover, since the sealing material can be eliminated, the number of parts can be reduced.
In addition, since the cooling water passage and the lubricating oil passage are completely partitioned by welding, it is not necessary to consider the sealing property between the cooling water passage and the lubricating oil passage, and can be formed arbitrarily close to each other. It becomes like this.
Further, since the seal material is not required, the bearing housing 40 can be reduced in size, and the turbocharger 5 can be reduced in size. This can be expected to improve earthquake resistance.

  The compressor side housing 110 and the turbine side housing 130 are joined by welding.

  By comprising in this way, the compressor side housing 110 and the turbine side housing 130 can be joined, preventing leakage of cooling water and lubricating oil more reliably.

  Further, the compressor-side housing 110 and the turbine-side housing 130 are joined at a portion (welding location W1 and welding location W2) different from the portion (bearing portion 114) that supports the shaft 10.

  With this configuration, the compressor-side housing 110 and the turbine-side housing 130 can be joined without hindering the support of the shaft 10.

  The compressor-side housing 110 and the turbine-side housing 130 are joined to each other on the outer side surfaces of the compressor-side housing 110 and the turbine-side housing 130 and on the inner side surfaces of the compressor-side housing 110 and the turbine-side housing 130. Part of 40 is formed by a closing body 150 that closes a space including the inner side surface after performing a joining operation on the inner side surface.

  By comprising in this way, the joining operation | work of the compressor side housing 110 and the turbine side housing 130 can be performed easily.

  The configuration of the bearing housing 40 according to the present embodiment is an example, and the shape and the like can be arbitrarily changed within the scope of the present invention.

  In the present embodiment, both the cooling water passage and the lubricating oil passage are formed on the dividing surface of the bearing housing 40. However, the present invention is not limited to this, and the cooling water passage and the lubricating oil passage are provided. Only one of these may be formed on the dividing surface.

  Further, in the present embodiment, the compressor side housing 110 and the turbine side housing 130 are joined by welding, but the present invention is not limited to this, and for example, joining using an adhesive, etc. Is possible.

  Moreover, in this embodiment, although it was set as the structure which welds to the welding location W1, the welding location W2, and the welding location W3, this invention is not restricted to this. That is, any portion can be welded so long as it is different from the bearing portion 114, avoiding the bearing portion 114 that supports the shaft 10 (slide bearing 60). However, also in this case, it is necessary to perform welding so as to partition the cooling water passage and the lubricating oil passage so that leakage of the cooling water and the lubricating oil from the cooling water passage and the lubricating oil passage can be prevented.

  In the present embodiment, the closing body 150 is fixed to the turbine-side housing 130 by welding. However, the present invention is not limited to this, and may be fixed by a fastener such as a bolt.

  In the present embodiment, the bearing housing 40 (the compressor side housing 110, the turbine side housing 130, and the closing body 150) is formed by forging. However, the present invention is not limited to this, and the bearing housing is not limited thereto. The 40 manufacturing methods and materials can be arbitrarily selected.

5 Turbocharger 10 Shaft 20 Compressor wheel 30 Turbine wheel 40 Bearing housing 110 Compressor side housing 114 Bearing portion 130 Turbine side housing 150 Closure

Claims (2)

A turbocharger bearing housing that rotatably supports a shaft connecting a compressor wheel and a turbine wheel,
The bearing housing
Divided into a first housing and a second housing,
In the dividing surface of the first housing and the second housing, a cooling water passage for circulating cooling water and / or a lubricating oil passage for flowing lubricating oil is formed,
The first housing and the second housing are brought into contact with each other without a seal member and joined by welding, so that the first housing and the second housing are integrally fixed and the divided Leakage of cooling water and / or lubricating oil from the cooling water passage and / or lubricating oil passage from the surface is prevented ,
The joining of the first housing and the second housing is
Outer surfaces of the first housing and the second housing;
Inner surfaces of the first housing and the second housing;
Applied in
A part of the bearing housing is
It is formed by a closing body that closes the space including the inner surface,
Turbocharger bearing housing. The joining of the first housing and the second housing is
The first housing and the second housing are applied over the entire circumference of the contact portion,
The bearing housing of the turbocharger according to claim 1.

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