JP2016196894A - Bearing housing for turbocharger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a bearing housing for a turbocharger that can reduce weight.SOLUTION: The bearing housing 100 for a turbocharger 10 stores a shaft 20 coupling a turbine 40 with a compressor 30 inside thereof and supports the shaft 20 so as to be rotatable. The bearing housing 100 for the turbocharger 10 is divided into a turbine-side housing 120 disposed on a side of the turbine 40 and a compressor-side housing 110 disposed on a side of the compressor 30. The compressor-side housing 110 is formed of an aluminum-based material.SELECTED DRAWING: Figure 3

Description

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

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

  The bearing housing of the turbocharger described in Patent Document 1 rotatably supports a shaft that connects a turbine driven by exhaust gas and a compressor that compresses intake air. Such a bearing housing is manufactured by casting using cast iron.

  However, the bearing housing manufactured using cast iron in this way is disadvantageous in that it is difficult to reduce the weight because the density of the cast iron is relatively high.

Japanese Patent Laid-Open No. 9-310620

  The present invention has been made in view of the above situation, and a problem to be solved is to provide a bearing housing for a turbocharger that can be reduced in weight.

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

  That is, according to the first aspect of the present invention, there is provided a bearing housing for a turbocharger that includes a shaft connecting the turbine and the compressor and supports the shaft so as to be rotatable, and the bearing housing for the turbocharger is disposed on the turbine side. A turbine-side housing disposed; and a compressor-side housing disposed on the compressor side, wherein the compressor-side housing is formed of an aluminum-based material, the bearing housing has a cooling water channel, and the cooling water channel is A circular arc-shaped cooling water channel whose lower part is cut out from the shaft, a water supply port formed on the lower surface of the compressor-side housing, and one end of the circular arc-shaped cooling water channel. Formed on the lower surface of the compressor-side housing. And another end of the arcuate cooling channel water outlet is intended to include a discharge water path communicating, the.

  According to a second aspect of the present invention, the arc-shaped cooling water channel is formed on at least one of a surface of the turbine side housing that contacts the compressor side housing and a surface of the compressor side housing that contacts the turbine side housing. is there.

  According to a third aspect of the present invention, the arc-shaped cooling water channel is formed along the outer peripheral surface of the compressor-side housing inside the compressor-side housing as viewed in the longitudinal direction of the shaft. The heat sink part for releasing the heat transmitted to the compressor side housing is formed.

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

  In the present invention, the weight of the bearing housing can be reduced by forming the compressor-side housing having a relatively low temperature from an aluminum-based material.

The schematic diagram which showed the outline | summary of operation | movement of the turbocharger which comprises the bearing housing which concerns on one Embodiment of this invention. Similarly, the side sectional view showing the composition of the turbocharger. The perspective view which showed the bearing housing which concerns on one Embodiment of this invention. The perspective view which showed the compressor side housing. (A) Similarly, a front view. (B) Similarly, a bottom view. Similarly, a rear view. (A) Similarly, a left side view. (B) The figure which showed the AA cross section in Fig.5 (a). (A) The figure which showed the BB cross section in Fig.5 (a). (B) The figure which similarly showed CC cross section. The perspective view which showed the turbine side housing. (A) Similarly, a front view. (B) Similarly, a right side view. Similarly, a rear view. (A) The figure which showed the DD cross section in Fig.10 (a). (B) The figure which showed the EE cross section similarly. (A) The front view which showed the bearing housing. (B) Similarly, a bottom view. Similarly, the left side view. The figure which showed the FF cross section in Fig.13 (a). The figure which showed the GG cross section in Fig.13 (a). (A) The rear view which showed the turbine side housing which concerns on other embodiment. (B) The figure which showed the HH cross section in Fig.17 (a).

  In the following description, the front-rear direction, the up-down direction, and the left-right direction are defined according to the arrows shown in the drawing.

  First, the outline of the operation of the turbocharger 10 in which the bearing housing 100 (see FIG. 3 and the like) according to an embodiment of the present invention is used will be described with reference to FIG.

  The turbocharger 10 sends compressed air into the cylinder 2 of the engine. Air is supplied to the cylinder 2 through the intake passage 1. The air passes through an air cleaner 4, a turbocharger 10, an intercooler 5, and a throttle valve 6 disposed in the middle of the intake passage 1 in order, and is supplied to the cylinder 2. At this time, since the air is compressed by the compressor 30 of the turbocharger 10, more air can be fed into the cylinder 2.

  Hot air (exhaust gas) after combustion in the cylinder 2 is exhausted through the exhaust passage 3. At this time, the exhaust gas rotates the turbine 40 of the turbocharger 10, and this rotation is transmitted to the compressor 30, whereby the air in the intake passage 1 can be compressed.

  Further, on the upstream side of the turbine 40, the exhaust passage 3 is divided and a passage that does not pass through the turbine 40 is formed separately. The passage can be opened and closed by a waste gate valve 7. The waste gate valve 7 is driven to open and close by an actuator 8. Further, the operation of the actuator 8 is controlled by a negative pressure generating mechanism 9 composed of an electromagnetic valve or the like. By opening and closing the waste gate valve 7 by the actuator 8, the flow rate of the exhaust gas sent to the turbine 40 can be adjusted.

  Next, the outline of the configuration of the turbocharger 10 will be described with reference to FIG.

  The turbocharger 10 mainly includes a shaft 20, a compressor 30, a turbine 40, a bearing housing 100, a compressor housing 60, a turbine housing 70, a slide bearing 80, a collar turbo seal 81, a thrust bearing 82, and a retainer seal 83.

  The shaft 20 is disposed with its longitudinal direction facing the front-rear direction. The compressor 30 is fixed to one end (rear end) of the shaft 20, and the turbine 40 is fixed to the other end (front end) of the shaft 20. In this way, the shaft 20 connects the compressor 30 and the turbine 40. The shaft 20 is made of a steel material.

  The bearing housing 100 includes the shaft 20 and rotatably supports the shaft 20. The shaft 20 is disposed so as to penetrate the bearing housing 100 in the front-rear direction, the compressor 30 is disposed behind the bearing housing 100, and the turbine 40 is disposed forward of the bearing housing 100.

  The compressor housing 60 contains the compressor 30. The compressor housing 60 is fixed to the rear portion of the bearing housing 100 and is formed so as to cover the compressor 30.

  The turbine housing 70 contains the turbine 40. The turbine housing 70 is fixed to the front portion of the bearing housing 100 and is formed so as to cover the turbine 40.

  The slide bearing 80 is interposed between the shaft 20 and the bearing housing 100 and is for smoothly rotating the shaft 20. The slide bearing 80 is made of a copper-based material.

  The color turbo seal 81 is inserted through the shaft 20 behind the slide bearing 80. The thrust bearing 82 is fitted on the collar turbo seal 81 behind the slide bearing 80, and the retainer seal 83 is fitted on the collar turbo seal 81 behind the thrust bearing 82.

  Next, the structure of the bearing housing 100 will be described with reference to FIGS.

  The bearing housing 100 mainly includes a compressor side housing 110, a turbine side housing 120, and a metal gasket 150. The bearing housing 100 is configured by fixing the compressor side housing 110 and the turbine side housing 120 side by side in the front-rear direction.

  The compressor side housing 110 shown in FIGS. 2 to 8 is a member constituting a portion of the bearing housing 100 on the compressor 30 side. The compressor side housing 110 mainly includes a main body portion 111 and a flange portion 112.

  The main body part 111 is a part formed in a substantially cylindrical shape with its axis line directed in the front-rear direction. A lower surface (bottom surface) that is a plane parallel to the front-rear direction and the left-right direction is formed in the lower portion of the main body 111. In the main body 111, an O-ring groove 111a, a bearing 111b, and a heat sink 111c are formed.

  The O-ring groove 111a is a recess formed at a substantially central portion on the rear surface of the main body 111 and having a predetermined depth. The cross section (back view) of the O-ring groove 111a is formed in a substantially circular shape.

  The bearing part 111b is a part which supports the shaft 20 so that rotation is possible. The bearing portion 111b is configured by a through hole formed so as to penetrate the main body portion 111 in the front-rear direction. More specifically, the bearing portion 111b is formed to communicate with the front surface of the main body portion 111 and a thrust bearing oil passage 143a described later, and to be parallel to the front-rear direction.

  The heat sink part 111 c is a part for releasing the heat transmitted to the compressor side housing 110. The heat sink portion 111 c is formed on the outer peripheral surface of the main body portion 111 (more specifically, a surface other than the front and rear surfaces of the main body portion 111 and the plane formed on the lower portion of the main body portion 111). The heat sink portion 111c is formed on the outer peripheral surface of the main body portion 111 so that a plurality of flat plate (fin-shaped) portions are arranged.

  The flange portion 112 is a portion formed in a substantially disc shape with its plate surface facing in the front-rear direction. The flange portion 112 is formed integrally with the main body portion 111 on the outer periphery of the rear end portion of the main body portion 111.

  The compressor side housing 110 configured in this way is formed by aluminum die casting (die casting using an aluminum-based material).

  The turbine-side housing 120 shown in FIGS. 2 and 3 and FIGS. 9 to 12 is a member constituting a portion of the bearing housing 100 on the turbine 40 side. The turbine-side housing 120 mainly includes a flange portion 121 and a thick portion 122.

  The flange portion 121 is a portion formed in a substantially disc shape with its plate surface facing in the front-rear direction.

  The thick portion 122 is a portion formed so that the plate thickness of the central portion of the flange portion 121 formed in a substantially disc shape is thicker than the plate thickness of other portions. More specifically, the thick portion 122 is formed in a substantially cylindrical shape with its axis line directed in the front-rear direction, and is formed so as to protrude forward from the front surface of the flange portion 121. The thick portion 122 is formed integrally with the flange portion 121. A through hole 122 a is formed in the thick portion 122.

  The through hole 122a is formed so as to penetrate the thick portion 122 of the turbine side housing 120 in the front-rear direction.

  The turbine-side housing 120 configured in this way is formed by sheet metal processing using stainless steel.

  In the compressor-side housing 110 and the turbine-side housing 120 configured as described above, as shown in FIGS. 2 and 3 and FIGS. 13 to 16, the front surface of the compressor-side housing 110 and the rear surface of the turbine-side housing 120, The bearing housing 100 is formed by fastening (fixing) with a fastener such as a bolt, diffusion bonding, or the like in a state where the contact is made.

  At this time, a metal gasket 150, which is a metal gasket, is interposed between the compressor side housing 110 and the turbine side housing 120, and liquid tightness between the compressor side housing 110 and the turbine side housing 120 is ensured. Kept.

  Further, the slide bearing 80 is inserted into the bearing portion 111 b formed in the compressor side housing 110 of the bearing housing 100, and the shaft 20 is further inserted into the slide bearing 80. In this way, the plain bearing 80 is interposed between the shaft 20 and the bearing housing 100 (more specifically, the bearing portion 111b).

  In the turbocharger 10 including the bearing housing 100 configured as described above, when the turbine 40 is rotated by exhaust of the engine, the temperature of the bearing housing 100 becomes high due to high-temperature exhaust. At this time, a portion of the bearing housing 100 close to the turbine 40 rotated by exhaust, that is, the temperature of the turbine-side housing 120 becomes particularly high. The turbine-side housing 120 of this embodiment is made of stainless steel, so it is resistant to heat and can withstand high temperatures caused by engine exhaust.

  Further, a portion of the bearing housing 100 close to the turbine 40 is configured by a turbine side housing 120 formed of stainless steel, so that heat from the exhaust in the turbine side housing 120 is blocked (heat shielding), and the compressor side housing 110 is cut off. It is possible to make it difficult to transmit heat. Further, by interposing the metal gasket 150 between the compressor-side housing 110 and the turbine-side housing 120 as in this embodiment, heat can also be shielded in the metal gasket 150, and more heat can be applied to the compressor-side housing 110. It can be difficult to communicate.

  Further, in the bearing housing 100, a portion far from the turbine 40, that is, the compressor-side housing 110 has a heat shielding action by the turbine-side housing 120, and therefore is less likely to be hotter than the turbine-side housing 120. Therefore, as in this embodiment, the compressor-side housing 110 can be formed using an aluminum-based material that is relatively weaker to heat than stainless steel. Thereby, the weight reduction and workability improvement of the bearing housing 100 can be achieved.

  Furthermore, since the heat sink portion 111c for facilitating heat release is formed in the compressor side housing 110, the rise in the temperature of the compressor side housing 110 (and hence the bearing housing 100) is more effectively suppressed. be able to.

  Further, generally, a portion that rotates at high speed using a slide bearing (in this embodiment, the shaft 20 is rotatably supported by the bearing portion 111b of the compressor-side housing 110 via the slide bearing 80. Part) may cause whirl vibrations. When the whirl vibration is generated, noise (abnormal noise) may be generated due to the whirl vibration, and it is important to reduce the whirl vibration.

  In the present embodiment, the shaft 20 rotates at a high speed or the heat of exhaust gas is transmitted from the turbine 40 side, so that it is supported by the bearing portion 111b (more specifically, the bearing portion 111b and the bearing portion 111b. When the temperature of the slide bearing 80 and the shaft 20) rises, the bearing portion 111b, the slide bearing 80, and the shaft 20 expand (thermally expand).

  Here, the thermal expansion coefficient of the slide bearing 80 (copper material) is larger than the thermal expansion coefficient of the shaft 20 (steel material), and the thermal expansion coefficient of the bearing portion 111b (aluminum material) is the slide bearing 80 (copper material). ) Greater than the coefficient of thermal expansion. For this reason, the inner diameter of the slide bearing 80 expands larger than the outer diameter of the shaft 20, and the inner diameter of the bearing portion 111 b expands larger than the outer diameter of the slide bearing 80. Therefore, the amount of lubricating oil interposed between the sliding bearing 80 and the shaft 20 and the amount of lubricating oil interposed between the bearing portion 111b and the sliding bearing 80 are increased, and the whirl vibration can be reduced.

  Further, by forming the bearing portion 111b with an aluminum-based material having a high thermal conductivity as in this embodiment, the heat generated in the bearing portion 111b is effectively absorbed and conducted (for example, dissipated from the heat sink portion 111c). The temperature rise of the bearing 111b can be suppressed. As a result, it is possible to effectively prevent deformation or damage of the bearing 111b due to heat.

  The lubricating oil passage 140 for supplying lubricating oil to the bearing portion 111b will be described later.

  Next, the cooling water passage 130 and the lubricating oil passage 140 formed in the bearing housing 100 will be described with reference to FIGS. 2 to 8 and FIGS. 11 to 16.

  The cooling water channel 130 is for supplying cooling water for cooling the bearing housing 100 into the bearing housing 100. The cooling water channel 130 mainly includes a compressor-side arc-shaped cooling water channel 131, a turbine-side arc-shaped cooling water channel 132, a supply water channel 133, and a discharge water channel 134.

  The compressor-side arc-shaped cooling water channel 131 shown in FIGS. 4 to 8 is a groove formed on the front surface of the main body 111 of the compressor-side housing 110. The compressor-side arc-shaped cooling water channel 131 is formed so as to have a shape (arc shape) in which a circular lower portion centering on the bearing portion 111b is cut out in a front view (see FIG. 5). The compressor-side arc-shaped cooling water channel 131 is formed by performing machining such as cutting or grinding on the front surface of the main body 111 of the compressor-side housing 110.

  The turbine-side arc-shaped cooling water channel 132 shown in FIGS. 11 and 12 is a groove formed on the rear surface of the thick portion of the turbine-side housing 120. The turbine-side arc-shaped cooling water channel 132 is formed so as to have a shape (arc-shaped) in which a circular lower portion centering on the through-hole 122a is notched in a rear view (see FIG. 11). The turbine-side arc-shaped cooling water channel 132 is formed so as to overlap with the compressor-side arc-shaped cooling water channel 131 (see FIG. 5) formed in the compressor-side housing 110. The turbine-side arc-shaped cooling water channel 132 is formed by subjecting the rear surface of the thick portion 122 of the turbine-side housing 120 to machining such as cutting or grinding, or pressing.

  5 and 8 is formed in the compressor-side housing 110, and communicates the compressor-side arc-shaped cooling water channel 131 with the bottom surface of the main body 111 of the compressor-side housing 110. More specifically, the supply water channel 133 is formed to communicate the vicinity of the right end of the bottom surface of the main body 111 of the compressor side housing 110 and the right end of the compressor side arc-shaped cooling water channel 131. The supply water channel 133 is formed on the front surface of the main body 111 of the compressor-side housing 110 (more specifically, in the compressor-side arc-shaped cooling water channel 131) and the bottom surface of the main body 111 of the compressor-side housing 110 such as cutting or grinding. It is formed by machining.

  The discharge water channel 134 shown in FIG. 5 is formed in the compressor-side housing 110 and communicates the compressor-side arc-shaped cooling water channel 131 and the bottom surface of the main body 111 of the compressor-side housing 110. More specifically, the discharge water channel 134 is formed so as to communicate the vicinity of the left end of the bottom surface of the main body 111 of the compressor side housing 110 and the left end of the compressor side arc-shaped cooling water channel 131. The discharge water channel 134 is formed on the front surface of the main body 111 of the compressor-side housing 110 (more specifically, in the compressor-side arc-shaped cooling water channel 131) and on the bottom surface of the main body 111 of the compressor-side housing 110 by cutting or grinding. It is formed by machining.

  As shown in FIGS. 3 and 13 to 16, when the compressor-side housing 110 and the turbine-side housing 120 are fastened (fixed), the supply water channel 133, the compressor-side arc-shaped cooling water channel 131, and the turbine-side arc-shaped cooling water channel 132 and the discharge water channel 134 are connected to each other to form a cooling water channel 130.

  In the cooling water passage 130 formed in this way, the cooling water is supplied into the bearing housing 100 through the supply water passage 133. The cooling water flows from the supply water channel 133 to one end of the compressor-side arc-shaped cooling water channel 131 (the lower right end in FIG. 5A) and one end of the turbine-side arc-shaped cooling water channel 132 (the lower right end in FIG. 11). Supplied with.

  The cooling water flows through the compressor-side arc-shaped cooling water channel 131 and the turbine-side arc-shaped cooling water channel 132, and the other end of the compressor-side arc-shaped cooling water channel 131 (the lower left end in FIG. 5A) and It is supplied to the other end portion (the lower left end portion in FIG. 11) of the turbine-side arc-shaped cooling water channel 132. At this time, the compressor-side arc-shaped cooling water channel 131 and the turbine-side arc-shaped cooling water channel 132 are formed to have an arc shape centering on the bearing portion 111b and the through hole 122a (that is, the shaft 20). Therefore, the heat transmitted from the turbine 40 side via the shaft 20 and the heat generated by the rotation of the shaft 20 can be effectively cooled.

  The cooling water is supplied from the other end of the compressor-side arc-shaped cooling water channel 131 and the other end of the turbine-side arc-shaped cooling water channel 132 to the discharge water channel 134. The cooling water is discharged from the discharge water passage 134 to the outside of the bearing housing 100.

  Thus, by circulating the cooling water in the cooling water channel 130, it is possible to effectively suppress the temperature of the bearing housing 100 from rising.

  The lubricating oil passage 140 is for supplying lubricating oil for lubricating the sliding portion between the bearing housing 100 and the shaft 20 into the bearing housing 100. The lubricating oil path 140 mainly includes a bearing portion 111b, a first lubricating oil path 142, and a second lubricating oil path 143.

  The bearing 111b shown in FIGS. 4 to 8 is a through-hole formed so as to penetrate the main body 111 of the compressor-side housing 110 in the front-rear direction as described above. The bearing portion 111b is a portion that rotatably supports the shaft 20, and is also a portion that constitutes a part of the lubricating oil passage 140. The bearing portion 111b is formed by performing machining such as cutting or grinding from the front surface or the rear surface of the compressor-side housing 110 (more specifically, in a thrust bearing oil passage 143a described later).

  The first lubricating oil passage 142 shown in FIGS. 4, 7 and 8 communicates the upper surface of the bearing housing 100 and the bearing portion 111b. More specifically, the first lubricating oil passage 142 is formed so as to communicate the substantially central portion of the upper surface (upper portion) of the main body 111 of the compressor-side housing 110 and the substantially central portion of the front and rear of the bearing portion 111b. . The first lubricating oil passage 142 is formed by subjecting the upper surface (upper part) of the main body 111 of the compressor-side housing 110 to machining such as cutting or grinding.

  A compressor-side branch oil passage 142 a is formed so as to branch from the middle portion of the first lubricating oil passage 142. The compressor-side branch oil passage 142a communicates with a vertically middle portion of the first lubricating oil passage 142 and a thrust bearing oil passage 143a described later. The compressor side branch oil passage 142a is formed by subjecting a thrust bearing oil passage 143a, which will be described later, to machining such as cutting or grinding.

  The second lubricating oil passage 143 shown in FIGS. 4 to 7 and FIGS. 11 and 12 communicates the lower surface of the bearing housing 100 and the bearing portion 111b. The second lubricating oil passage 143 mainly includes a thrust bearing oil passage 143a, a compressor side lateral oil passage 143b, a turbine side longitudinal oil passage 143c, and a discharge oil passage 143d.

  The thrust bearing oil passage 143a shown in FIGS. 6 and 7 is a groove formed by vertically cutting the inside (rear part of the main body 111) of the O-ring groove 111a formed in the main body 111 of the compressor side housing 110. It is. More specifically, the thrust bearing oil passage 143a extends forward from the substantially central portion (the rear end portion (end portion on the compressor 30 side) of the bearing portion 111b) of the rear portion of the main body portion 111 to the lower portion. It is formed so as to be deeply cut out. The thrust bearing oil passage 143a is formed by performing machining such as cutting or grinding on the rear surface of the compressor-side housing 110 (more specifically, inside the O-ring groove 111a).

  The compressor side lateral oil passage 143b shown in FIGS. 4 to 7 is a through hole formed so as to penetrate the main body 111 of the compressor side housing 110 in the front-rear direction. More specifically, the compressor side lateral oil passage 143b is formed below the bearing portion 111b so as to communicate the front surface of the main body portion 111 with the thrust bearing oil passage 143a and to be parallel to the bearing portion 111b. The The compressor side lateral oil passage 143b is cast by machining such as cutting or grinding from the front or rear surface (more specifically, in the thrust bearing oil passage 143a) of the compressor side housing 110, or by a die. Formed by.

  The turbine-side vertical oil passage 143c shown in FIGS. 11 and 12 is a groove formed by cutting out the rear surface of the thick portion 122 of the turbine-side housing 120 in the vertical direction. More specifically, the turbine-side vertical oil passage 143c is formed from the substantially central portion (through hole 122a) on the rear surface of the thick portion 122 to the lower portion. The turbine-side vertical oil passage 143c is formed by subjecting the rear surface of the turbine-side housing 120 to machining such as cutting or grinding, or pressing.

  5 and 7 is formed in the compressor-side housing 110, and communicates the compressor-side lateral oil passage 143b with the bottom surface of the main body 111 of the compressor-side housing 110. More specifically, the discharge oil passage 143d is formed so as to communicate the left and right center portion of the bottom surface of the main body 111 of the compressor side housing 110 with the substantially front and rear center portion of the compressor side lateral oil passage 143b. The discharged oil passage 143d is formed by performing machining such as cutting or grinding on the bottom surface of the main body 111 of the compressor-side housing 110.

  As shown in FIGS. 3 and 13 to 16, when the compressor-side housing 110 and the turbine-side housing 120 are fastened (fixed), a thrust bearing oil passage 143 a, a compressor-side lateral oil passage 143 b, and a turbine-side vertical oil passage are provided. 143c and the discharge oil passage 143d are connected to each other to form a second lubricating oil passage 143. Further, the first lubricating oil path 142, the bearing portion 111b, and the second lubricating oil path 143 form a lubricating oil path 140.

  The lubricating oil passage 140 according to the present embodiment is subjected to processing (for example, precision grinding processing or coating processing) for reducing the surface roughness of the lubricating oil passage 140.

  In the lubricating oil passage 140 formed in this manner, the lubricating oil is supplied into the bearing housing 100 from the upper surface of the bearing housing 100 (compressor side housing 110) via the first lubricating oil passage 142. The lubricating oil flows downward in the first lubricating oil passage 142 and is supplied to the bearing portion 111b. A part of the lubricating oil flowing through the first lubricating oil passage 142 is supplied to the thrust bearing oil passage 143a of the compressor-side housing 110 via the compressor-side branch oil passage 142a.

  The lubricating oil supplied to the bearing portion 111b flows between the bearing portion 111b and the slide bearing 80, and attenuates the vibration of the slide bearing 80. Further, the lubricating oil circulates inside the sliding bearing 80 from a through hole appropriately formed on the outer peripheral surface of the sliding bearing 80. The lubricating oil flows between the sliding bearing 80 and the shaft 20, lubricates the relative rotation between the sliding bearing 80 and the shaft 20, and cools the bearing portion. .

  The lubricating oil that has lubricated the bearing portion 111b, the plain bearing 80, and the shaft 20 flows to the front end portion (turbine 40 side end portion) or the rear end portion (compressor 30 side end portion) of the bearing portion 111b, and the thrust bearing oil passage. 143a or the turbine side vertical oil path 143c is supplied to the compressor side horizontal oil path 143b. The lubricating oil supplied to the compressor side lateral oil passage 143b is discharged from the bottom surface of the main body 111 of the compressor side housing 110 to the outside of the bearing housing 100 via the discharge oil passage 143d.

  In this way, the lubricating oil is allowed to flow smoothly according to gravity by flowing the lubricating oil from the upper surface of the bearing housing 100 to the lower surface of the bearing housing 100 (the bottom surface of the main body 111) via the bearing portion 111b. Can do. Further, by discharging the lubricating oil from the front end and the rear end of the bearing portion 111b, the lubricating oil can be smoothly circulated and the lubricating oil can be reliably guided from the front end to the rear end of the bearing portion 111b.

As described above, the bearing housing 100 of the turbocharger 10 according to the present embodiment includes the shaft 20 connecting the turbine 40 and the compressor 30 and supports the shaft 20 so as to be rotatable. The bearing housing 100 of the turbocharger 10 is divided into a turbine side housing 120 disposed on the turbine 40 side and a compressor side housing 110 disposed on the compressor 30 side for supplying cooling water. The cooling water passage 130 and the lubricating oil passage 140 for supplying lubricating oil are formed by machining the turbine side housing 120 and the compressor side housing 110.
With this configuration, the cooling water passage 130 and the lubricating oil passage 140 formed in the bearing housing 100 are formed by machining, so that it is not necessary to use a core when the bearing housing 100 is formed by casting. Cost reduction can be achieved. Further, since it is not necessary to form the cooling water passage 130 and the lubricating oil passage 140 by the sand core at the casting stage, whether or not the sand sand of the sand core remains in the cooling water passage 130 and the lubricating oil passage 140. There is no need to inspect. Further, by dividing the bearing housing 100 into two members, it is possible to improve the workability of the cooling water passage 130 and the lubricating oil passage 140 (make it easy to perform machining).

The lubricating oil passage 140 is a first through which the shaft 20 is inserted and the bearing portion 111b that is a through hole that rotatably supports the shaft 20, and the upper surface of the bearing housing 100 and the bearing portion 111b communicate with each other. It includes a lubricating oil passage 142 and a second lubricating oil passage 143 that communicates the lower surface of the bearing housing 100 and the bearing portion 111b.
By configuring in this way, the shape of the lubricating oil passage 140 can be simplified, and as a result, the workability of the lubricating oil passage 140 can be improved. Further, by supplying the lubricating oil into the bearing housing 100 via the first lubricating oil path 142, the lubricating oil flows in the order of the first lubricating oil path 142, the bearing portion 111b, and the second lubricating oil path 143 according to gravity. Therefore, the lubricating oil can be circulated smoothly.

The second lubricating oil passage 143 is formed so as to communicate the end portion on the compressor 30 side and the end portion on the turbine 40 side of the bearing portion 111b with the lower surface of the bearing housing 100.
By comprising in this way, lubricating oil can be discharged | emitted from the both ends of the bearing part 111b to the downward direction of the bearing housing 100, and the said lubricating oil can be circulated smoothly. Further, the lubricating oil can be reliably guided to both ends of the bearing portion 111b, and the bearing portion 111b can be effectively lubricated and cooled.

In addition, at least one of the surface of the turbine side housing 120 that contacts the compressor side housing 110 and the surface of the compressor side housing 110 that contacts the turbine side housing 120 has an arcuate shape centering on the shaft 20 as the cooling water passage 130. Arc-shaped cooling water channels (the compressor-side arc-shaped cooling water channel 131 and the turbine-side arc-shaped cooling water channel 132) are formed.
By configuring in this way, the cooling water passage is formed so as to surround the periphery of the shaft 20, so that heat transmitted from the turbine 40 side through the shaft 20 and heat generated by the rotation of the shaft 20 are generated. An increase in the temperature of the bearing housing 100 can be effectively suppressed.

Further, the lubricating oil passage 140 is subjected to processing for reducing the surface roughness.
With this configuration, the flow resistance of the lubricating oil passage 140 can be reduced, and consequently the mechanical efficiency of the turbocharger 10 can be improved. In addition, since the lubricating oil is less likely to stay, the rate of oil coking can be reduced.

Further, the bearing housing 100 of the turbocharger 10 according to the present embodiment is a bearing housing 100 of the turbocharger 10 that includes the shaft 20 connecting the turbine 40 and the compressor 30 and supports the shaft 20 so as to be rotatable. The bearing housing 100 of the turbocharger 10 is divided into a turbine side housing 120 disposed on the turbine 40 side and a compressor side housing 110 disposed on the compressor 30 side. The compressor side housing 110 is made of an aluminum-based material. It is formed by.
By comprising in this way, weight reduction of the bearing housing 100 can be achieved by forming the compressor side housing 110 used as a comparatively low temperature with an aluminum-type material.

In addition, a heat sink portion 111 c for releasing the heat transmitted to the compressor side housing 110 is formed on the outer peripheral surface of the compressor side housing 110.
With this configuration, the temperature rise of the bearing housing 100 that is disposed in a high-temperature environment (specifically, the heat of engine exhaust or the heat generated by the rotation of the shaft 20 is transmitted) is suppressed. can do.

Moreover, the turbine side housing 120 is formed of stainless steel.
In this way, by forming the turbine-side housing 120 that is relatively high in temperature from stainless steel, deformation or damage due to high temperatures can be prevented. Further, since the heat is shielded by the turbine-side housing 120 formed of stainless steel, the compressor-side housing 110 formed of an aluminum-based material can be prevented from being deformed or damaged by heat. Further, since the surface roughness of stainless steel is lower than that of cast iron, lubricating oil does not easily stay in the turbine-side housing 120, and the rate of oil coking can be reduced.

Moreover, the turbocharger 10 according to the present embodiment includes a shaft 20 that connects the turbine 40 and the compressor 30, a bearing housing 100 that includes a bearing portion 111b that rotatably supports the shaft 20, and the shaft 20 and the bearing portion 111b. And a slide bearing 80 interposed therebetween, wherein the bearing portion 111b is made of an aluminum material, the shaft 20 is made of a steel material, and the slide bearing 80 is made of a copper material. Is formed.
With this configuration, when the temperature of the bearing portion 111b rises, the inner diameter of the bearing portion 111b formed of the aluminum-based material expands larger than the outer diameter of the slide bearing 80 formed of the copper-based material. The amount of lubricating oil interposed between the bearing portion 111b and the slide bearing 80 is increased, and the whirl vibration can be reduced. Similarly, when the temperature of the bearing portion 111b rises, the inner diameter of the slide bearing 80 made of a copper-based material expands larger than the outer diameter of the shaft 20 made of a steel material. The amount of lubricating oil interposed between the shaft 20 and the shaft 20 can be increased, and the whirl vibration can be reduced. Further, since the inner diameter of the bearing portion 111b formed of an aluminum-based material has high thermal conductivity, the heat generated in the bearing portion 111b is absorbed and conducted effectively, and the temperature of the bearing portion 111b is lowered to reduce deformation due to heat. Damage and the like can be prevented more effectively.

The bearing housing 100 is divided into a turbine side housing 120 disposed on the turbine 40 side and a compressor side housing 110 disposed on the compressor 30 side. The turbine side housing 120 is made of stainless steel, and has a bearing portion. 111 b is formed in the compressor-side housing 110.
In this way, by forming the turbine-side housing 120 that is relatively high in temperature from stainless steel, deformation or damage due to high temperatures can be prevented. Further, the turbine-side housing 120 formed of stainless steel shields heat, so that deformation or damage due to heat of the bearing portion 111b formed of an aluminum-based material can be prevented.

A metal gasket 150 is interposed between the turbine side housing 120 and the compressor side housing 110.
Thus, by interposing the metal gasket 150 between the turbine side housing 120 and the compressor side housing 110, heat from the turbine 40 side can be shielded, and the bearing portion 111b formed of an aluminum-based material. It is possible to more effectively prevent deformation and damage caused by heat.

In the present embodiment, the heat sink portion 111c formed in the main body portion 111 of the compressor side housing 110 has a plurality of flat plate shapes (fin shapes), but the present invention is not limited to this. That is, the heat sink part 111c may be formed so as to increase the surface area of the main body part 111. For example, the heat sink part 111c may be formed in a lobe shape, a spiral shape, a sword mountain shape, a bellows shape, or the like.
In the present embodiment, the turbine housing 120 is formed by sheet metal processing using stainless steel. However, the present invention is not limited to this, and can be formed by casting using, for example, cast iron. It is.
In the present embodiment, the lubricating oil passage 140 is processed to reduce the surface roughness. However, the present invention is not limited to this, and the cooling water passage 130 is provided to reduce the surface roughness. Processing can also be performed. Thereby, the flow resistance of the cooling water flowing through the cooling water channel 130 can be reduced.

  As another embodiment, as shown in FIG. 17, a recess 121 a can be formed in the turbine-side housing 120.

  The recess 121a is formed by applying machining or pressing such as cutting or grinding to the rear surface of the turbine-side housing 120. The recess 121a is formed over the widest possible range on the rear surface of the turbine-side housing 120.

  When the rear surface of the turbine side housing 120 configured in this way and the front surface of the compressor side housing 110 (see FIGS. 4 to 8) are fixed to each other in contact with each other, the rear surface of the turbine side housing 120 is fixed. Since the recess 121a is formed, the contact area between the turbine housing 120 and the compressor housing 110 is reduced. As a result, even when the turbine-side housing 120 reaches a high temperature, it is possible to make it difficult for the heat to be transmitted to the compressor-side housing 110, thereby preventing the compressor-side housing 110 from being deformed or damaged due to the high temperature. Furthermore, since a space in which air is interposed is formed in the recess 121a, heat can be more difficult to be transmitted to the compressor-side housing 110 by the space (layer of air).

As described above, in the bearing housing 100 of the turbocharger 10 according to the present embodiment, the concave portion 121a is formed on the surface (rear surface) of the turbine side housing 120 that contacts the compressor side housing 110.
With this configuration, it is possible to make it difficult for the heat of the turbine-side housing 120 to be transmitted to the compressor-side housing 110.

  In the present embodiment, the recess 121a is formed in the turbine-side housing 120, but the present invention is not limited to this. That is, a configuration in which a recess is formed on a surface (front surface) of the compressor side housing 110 that contacts the turbine side housing 120, or a configuration in which a recess is formed on both the rear surface of the turbine side housing 120 and the front surface of the compressor side housing 110. Is also possible.

20 Shaft 30 Compressor 40 Turbine 80 Slide bearing 100 Bearing housing 110 Compressor side housing 111b Bearing portion 111c Heat sink portion 120 Turbine side housing 130 Cooling water passage 131 Compressor side arc cooling water passage 132 Turbine side arcuate cooling water passage 140 Lubricating oil passage 142 First Lubricating oil passage 143 Second lubricating oil passage 150 Metal gasket

Claims (3)

A turbocharger bearing housing that includes a shaft connecting a turbine and a compressor and supports the shaft rotatably.
The turbocharger bearing housing is
A turbine-side housing disposed on the turbine side;
A compressor-side housing disposed on the compressor side;
Divided into
The compressor side housing is formed of an aluminum-based material,
The bearing housing has a cooling water channel;
The cooling water channel is
An arc-shaped cooling water channel having an arc shape in which a lower part is cut out around the shaft;
A water supply channel that communicates a water supply port formed on the lower surface of the compressor side housing and one side end of the arc-shaped cooling water channel;
A discharge water passage communicating the water discharge port formed on the lower surface of the compressor side housing and the other end of the arcuate cooling water passage;
including,
Turbocharger bearing housing. The arc-shaped cooling water channel is
Formed on at least one of a surface of the turbine side housing that contacts the compressor side housing and a surface of the compressor side housing that contacts the turbine side housing;
The bearing housing of the turbocharger according to claim 1. The arc-shaped cooling water channel is
The shaft is formed along the outer peripheral surface of the compressor side housing inside the compressor side housing in the longitudinal direction view,
On the outer peripheral surface of the compressor-side housing, a heat sink portion for releasing the heat transmitted to the compressor-side housing is formed.
The bearing housing of the turbocharger according to claim 1 or 2.

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