Turbocharger components

Abstract

The turbocharger may include: a central housing; a compressor assembly operatively coupled to the central housing; and a turbine assembly operatively coupled to the central housing, wherein the central housing includes a bearing boss including a bore wall having opposite axial ends, the opposite axial ends defining an axial through-bore having opposite axial openings, an oil inlet, an oil outlet, an arcuate oil passage in fluid communication with the oil inlet, an oil passage in fluid communication with the arcuate oil passage and an opening in the bore wall, and an oil drainage passage in fluid communication with the opposite axial openings of the through-bore and in fluid communication with the oil outlet.

Description

Technical Field

[0001] The subject matter disclosed herein relates generally to turbocharger components for internal combustion engines. Background Art

[0002] A turbocharger may include a rotating group including a turbine wheel and a compressor wheel connected to each other by a shaft. For example, the turbine wheel may be welded or otherwise connected to the shaft to form a shaft and impeller assembly (SWA), and the compressor wheel may be adapted to the free end of the shaft. An electric compressor may include one or more compressor impellers connected to one or more shafts that may be driven by an electric motor. As an example, a shaft attached to one or more bladed impellers may be supported by one or more bearings disposed in a bearing housing, which may form a central housing rotating assembly (CHRA). During operation of a turbocharger or electric compressor, depending on factors such as the size of various components, it may be expected that the shaft may rotate at a speed exceeding 200,000 rpm. In order to ensure proper rotor dynamics, the rotating group should be well balanced, well supported, and well lubricated over a wide range of conditions (e.g., operability, temperature, pressure, etc.). Summary of the invention

[0003] A turbine is provided, comprising: a central housing (410); a compressor assembly operatively coupled to the central housing (410); and a turbine assembly operatively coupled to the central housing (410), wherein the central housing (410) comprises a bearing boss (430) comprising a bore wall (431) having opposite axial ends (434, 436), the opposite axial ends (434, 436) defining an axial through hole having opposite axial openings, an oil inlet (411), an oil outlet (419), and an oil inlet (411). 11) an arcuate oil passage (450) in fluid communication, wherein the arcuate oil passage (450) extends from a first region (452) proximate the oil inlet (411) to a second region (454), and wherein the arcuate oil passage includes an arc greater than 45 degrees about the axis of the axial through hole, an oil passage (455) in fluid communication with the arcuate oil passage (450) and an opening (433) in the hole wall (431), and an oil drainage passage (458) in fluid communication with an opposite axial opening of the through hole and in fluid communication with the oil outlet (419).

[0004] A method for setting up a turbine is provided, comprising: flowing oil to an oil inlet (411) in a central housing (410), the central housing (410) comprising: a bearing boss (430) comprising a bore wall (431) having opposite axial ends (434, 436), the opposite axial ends (434, 436) defining an axial through hole having opposite axial openings; an oil inlet (411); an oil outlet (419); an arcuate oil passage (450) in fluid communication with the oil inlet (411), wherein the arcuate oil passage (450) extends from a first portion proximate to the oil inlet (411) to a second portion proximate to the oil inlet (411); Zone (452) extends to a second zone (454), and wherein the arcuate oil passage includes an arc greater than 45 degrees about the axis of the axial through hole; an oil passage (455) fluidly connected to the arcuate oil passage (450) and the opening (433) in the hole wall (431); and an oil drainage passage (458) fluidly connected to the opposite axial opening of the through hole and to the oil outlet (419); receiving at least a portion of the oil flowing from the opposite axial opening of the axial through hole in the oil drainage passage (458); and causing the oil to flow from the oil drainage passage (458) to the oil outlet (419). BRIEF DESCRIPTION OF THE DRAWINGS

[0005] A more complete understanding of the various methods, apparatus, components, systems, arrangements, etc. described herein, and their equivalents, may be had by referring to the following detailed description when taken in conjunction with the examples illustrated in the accompanying drawings, in which:

[0006] Figure 1 is a diagram of a turbocharger and an internal combustion engine along a controller;

[0007] Figure 2 are cross-sectional views of examples of turbocharger components and end and cross-sectional views of examples of journal bearings;

[0008] Figure 3 is a diagram of an example of a system including an example of a water-cooled turbocharger;

[0009] Figure 4 is a cross-sectional view of an example of an oil-cooled turbocharger assembly and a view of an example of a bearing;

[0010] Figure 5A and 5B is a perspective view of an example of a housing;

[0011] Fig. 6A and 6B yes Figure 5A and 5B end view and side view of the housing;

[0012] Fig. 7A , 7B , 7C and 7D are Fig. 6A and6B A cross-sectional view of a housing;

[0013] Figure 8 Available in various sizes as shown Fig. 6A and 6B A cross-sectional view of a housing;

[0014] Fig. 9 yes Fig. 6A and 6B A front perspective view of the space of the shell;

[0015] Fig.10 yes Figure 4 A cross-sectional view of an oil-cooled turbocharger assembly and a cross-sectional view of a portion thereof having an example of a bearing, wherein arrows indicate the general direction of oil flow;

[0016] Fig.11 is an example of a graph of temperatures at various locations of an oil-cooled turbocharger assembly;

[0017] Fig.12 is a cross-sectional view of an example of a housing;

[0018] Fig.13 is a cross-sectional view of an example of a housing;

[0019] Fig.14A and 14B are perspective and cross-sectional views of examples of housings. DETAILED DESCRIPTION

[0020] Examples of turbocharged engine systems are described following examples of components, assemblies, methods, and the like.

[0021] Turbochargers are frequently used to increase the output of internal combustion engines. Figure 1 As an example, the system 100 may include an internal combustion engine 110 and a turbocharger 120. Figure 1 As shown in , the system 100 may be part of a vehicle 101, where the system 100 is disposed in an engine compartment and connected to an exhaust duct 103 that directs exhaust gases to an exhaust port 109 positioned, for example, behind a passenger compartment 105. Figure 1 In the example of FIG. 1 , a treatment unit 107 may be provided to treat the exhaust gas (eg, to reduce emissions via molecular catalytic conversion).

[0022] like Figure 1As shown in , the internal combustion engine 110 includes an engine block 118 that houses one or more combustion chambers that operatively drive a shaft 112 (e.g., via a piston) as well as an intake port 114 that provides a flow path for air to the engine block 118 and an outlet port 116 that provides a flow path for exhaust from the engine block 118.

[0023] The turbocharger 120 may function to extract energy from the exhaust gas and provide energy to the incoming air, which may be combined with fuel to form combustion gases. Figure 1 As shown in FIG. 1 , the turbocharger 120 includes an air inlet 134, a shaft 122, a compressor housing assembly 124 for a compressor wheel 125, a turbine housing assembly 126 for a turbine wheel 127, another housing assembly 128, and an exhaust 136. The housing assembly 128 may be referred to as a center housing assembly because it is disposed between the compressor housing assembly 124 and the turbine housing assembly 126.

[0024] exist Figure 1 , shaft 122 may be a shaft assembly that includes various components (e.g., consider a shaft and wheel assembly (SWA) in which turbine wheel 127 is welded to shaft 122, etc.). As an example, shaft 122 may be rotatably supported by a bearing system (e.g., plain bearing(s), rolling bearing(s), etc.) disposed in housing assembly 128 (e.g., in a bore defined by one or more bore walls) such that rotation of turbine wheel 127 results in rotation of compressor wheel 125 (e.g., as rotatably coupled via shaft 122). As an example, a central housing rotating assembly (CHRA) may include compressor wheel 125, turbine wheel 127, shaft 122, housing assembly 128, and various other components (e.g., a compressor side plate disposed at an axial position between compressor wheel 125 and housing assembly 128).

[0025] exist Figure 1 In the example of FIG. 1 , a variable geometry assembly 129 is shown as being partially disposed between the housing assembly 128 and the housing assembly 126. Such a variable geometry assembly may include vanes or other components to change the geometry of the passage to the turbine wheel space in the turbine housing assembly 126. As an example, a variable geometry compressor assembly may be provided.

[0026] exist Figure 1In the example of , a wastegate valve (or simply, wastegate) 135 is positioned proximate to the exhaust port of the turbine housing assembly 126. The wastegate valve 135 can be controlled to allow at least some exhaust from the outlet 116 to bypass the turbine wheel 127. Various wastegates, wastegate components, etc. can be applied to conventional fixed nozzle turbines, fixed vane nozzle turbines, variable nozzle turbines, twin scroll turbochargers, etc. As an example, the wastegate can be an internal wastegate (e.g., at least partially inside the turbine housing). As an example, the wastegate can be an external wastegate (e.g., operatively coupled to a conduit in fluid communication with the turbine housing).

[0027] exist Figure 1 In the example of FIG. 1 , an exhaust gas recirculation (EGR) conduit 115 is also shown, which may optionally be provided with one or more valves 117 , for example to allow exhaust gas to flow to a position upstream of the compressor impeller 125 .

[0028] Figure 1 Also shown is an example arrangement 150 for exhaust gas flow to an exhaust gas turbine housing assembly 152, and another example arrangement 170 for exhaust gas flow to an exhaust gas turbine housing assembly 172. In arrangement 150, passages 156 are included in cylinder head 154 to direct exhaust gas from the cylinders to turbine housing assembly 152, while in arrangement 170, for example, manifold 176 provides for mounting of turbine housing assembly 172 without any separate, intermediate length exhaust pipe. In example arrangements 150 and 170, turbine housing assemblies 152 and 172 may be configured for use with wastegates, variable geometry assemblies, and the like.

[0029] exist Figure 1In the example of controller 190, an example is shown as including one or more processors 192, memory 194, and one or more interfaces 196. Such a controller may include circuits such as circuits of an engine control unit (ECU). As described herein, various methods or techniques may be optionally implemented in conjunction with a controller, such as by control logic. The control logic may depend on one or more engine operating conditions (e.g., turbine rpm, engine rpm, temperature, load, lubricant, cooling, etc.). For example, a sensor may transmit information to the controller 190 via one or more interfaces 196. The control logic may rely on such information, and then, the controller 190 may output a control signal to control the engine operation. The controller 190 may be configured to control lubricant flow, temperature, variable geometry components (e.g., variable geometry compressors or turbines), wastegates (e.g., via actuators), motors, or one or more components associated with an engine, a turbocharger (or multiple turbochargers), and the like. As an example, the turbocharger 120 may include one or more actuators and / or one or more sensors 198, which may be coupled to one or more interfaces 196 of the controller 190, for example. As an example, the wastegate valve 135 may be controlled by a controller that includes an actuator responsive to an electrical signal, a pressure signal, etc. As an example, the actuator for the wastegate may be, for example, a mechanical actuator that may operate without the need for electrical power (e.g., consider a mechanical actuator configured to respond to a pressure signal supplied via a conduit).

[0030] Figure 2 An example of a turbocharger assembly 200 is shown, which includes a shaft 220 supported by a journal bearing 230 disposed in a center housing 280 between a compressor wheel 240 and a turbine wheel 260; note that a thrust ring 270 is shown positioned between the compressor wheel 240 and a shoulder of the shaft 220 relative to a hole in a back plate 290. Figure 2 As shown in , the shoulder is formed by a step in the diameter of the shaft 220 from a smaller diameter to a larger diameter, thereby forming an annular axial surface (e.g., the compressor side). Figure 2 In the example of FIG. 2 , the thrust ring 270 is adjacent to the axial face of the shaft 220 on one side and adjacent to the annular axial face of the compressor impeller 240 on the opposite side. The sliding bearing 230 is at least partially positioned in the through hole of the central housing 280 via the locating pin 210. The locating pin 210 can be fixed by being screwed into the socket 285 of the housing 280 and can be received by the opening 235 of the sliding bearing 230, thereby positioning the sliding bearing 230 in the through hole of the central housing 280. As an example, the locating pin 210 can axially and azimuthally position the sliding bearing 230 in the through hole of the central housing 280. As shown in FIG. Figure 2As shown in the example of FIG. 2 , the sliding bearing 230 includes a lubricant opening 239 for lubricant to flow to the inner sliding surface of the sliding bearing 230, which supports the shaft 220, opposite to the opening 235. The lubricant can flow to the through hole of the central housing 280, through the lubricant opening 239 and to the inner sliding surface to form a lubricant film that lubricates the shaft 220 within the sliding bearing 230. The lubricant can also flow to the gap between the wall of the hole of the central housing 280 and the outer surface of the sliding bearing 230.

[0031] As an example, the sliding bearing 230 can move radially within the through hole of the central housing 280, for example, the sliding bearing 230 can move radially upward and downward relative to the locating pin 210 while being axially and positionally restricted by the locating pin 210 (for example, the sliding bearing 230 can be a semi-suspended sliding bearing).

[0032] Figure 2 An end view and a cross-sectional view of the sliding bearing 230 are also shown. Figure 2 In the example of FIG. 2 , the plain bearing 230 includes an axially oriented channel 232 extending across the internal sliding surface for lubricant flow. The channel 232 extends to the end of the plain bearing 230, and various features therein provide distribution of the lubricant across the thrust pad (e.g., thrust surface) of the plain bearing 230. The thrust pad 234 and lubricant of the plain bearing 230 can help manage thrust forces experienced during operation.

[0033] exist Figure 2 In the example of , the thrust surface forming the thrust pad 234 includes radial grooves to improve thrust capacity while also enhancing contamination control. As an example, eight radial grooves spaced 45° apart may be employed, with four grooves aligned with the axial grooves in the bearing bore. As an example, each axial groove may have a V shape (e.g., a 90° V shape). As shown, a relief on the inner periphery of each thrust surface may act to enhance lubricant delivery and distribution.

[0034] The thrust ring 270 may include an integrated lifting ring, or a separate lifting ring component may be provided. The lifting ring acts to direct lubricant outwardly away from the shaft, as indicated by the arrows. The lifting ring may include one or more passages extending from the inner diameter to the outer diameter to direct lubricant outwardly as the lifting ring rotates.

[0035] exist Figure 2In the example of FIG. 2 , the thrust ring 270 is shown as including an integrated lifting ring and an annular surface facing the end of the sliding bearing 230. As an example, under the pressure of a lubricant feed system (e.g., an engine lubricant pump), lubricant can be supplied to the thrust pad 234 of the sliding bearing 230 to form a lubricant film between the annular surface of the thrust ring 270 and the thrust pad of the sliding bearing 230. Because the thrust ring 270 can rotate, the lubricant forming the lubricant film can also be slung radially outward (e.g., in addition to the lubricant in the passage of the lifting ring). Regardless of whether the lubricant is slung from the passage of the lifting ring or from the lubricant film, the lubricant may be discharged downward toward the lubricant drainage cavity of the center housing 280 under the influence of gravity (see the arrow marked as "G").

[0036] Figure 2 A small arrow is also shown near the compressor wheel 240 to indicate where lubricant may escape and potentially be transported with the gas compressed by the rotation of the compressor wheel 240 (e.g., in the compressor housing). The lifting ring may help reduce the escape of lubricant through the compressor. Figure 2 As shown in the example of FIG. 2 , the back plate 290 has a profile that allows the thrown lubricant to collect and flow along a larger radius located a distance away from the shaft 220. The slope at the bottom side of the profile of the back plate 290 can guide the lubricant to flow to the lubricant drainage cavity of the central housing 280 (see, for example, arrows).

[0037] With respect to pressure, the area formed between the back plate 290 and the central housing 280 may have approximately the same pressure as the lubricant drainage cavity of the central housing (see, for example, P L ). Thus, in such a scenario, the flow of lubricant to the lubricant drain of the center housing 280 occurs primarily under the influence of gravity. Such a path can be considered an expansion path that acts to minimize the pressure at which the lubricant exits the gap between the shaft 220 and the journal bearing 230, and thereby minimizes the driving force (e.g., pressure differential) for the lubricant to escape between the back plate 290 and the compressor impeller 240 (see, e.g., P C ) is minimized. Figure 2 As indicated in the example of , by having an enlarged area (e.g., a large volume) between the back plate 290 and the center housing 280, a large pressure drop is achieved for the lubricant exiting the gap between the shaft 220 and the journal bearing 230 (e.g., considering that the lubricant is fed to the center housing 280 via a pump such as an engine oil pump). Figure 2 In the example of FIG. 2 , the small arrow indicates the flow direction of the lubricant escaping to the space via the interface formed between the thrust ring 270 and the back plate 290 . Note that one or more sealing rings (eg, O-rings) may be positioned around the thrust ring 270 to resist such flow.

[0038] Figure 2 The turbocharger assembly 200 is oil-cooled and air-cooled, for example, by being in an environment with ambient air or vehicle engine compartment air. The turbocharger can be cooled via one or more mechanisms. For example, the turbocharger can be cooled via air, water, oil, or other fluids. There are some trade-offs regarding lubricant cooling (e.g., oil, whether natural or synthetic, etc.). For example, if a carbonaceous lubricant reaches too high a temperature for too long (e.g., considering time-temperature correlation), carbonization (e.g., also known as carbon deposition or "coking") may occur. Coking may exacerbate heat generation and heat retention through any of a variety of mechanisms, and over time, coke deposition may shorten the life of the lubricated bearing system. As an example, coke deposition may result in reduced heat transfer and increased heat generation, which may cause the bearing system to fail.

[0039] In order to overcome coking, the turbocharger can be configured to improve the lubricant flow. For example, the pump can pressurize the lubricant to increase the flow rate to reduce the residence time of the lubricant in the high temperature zone. However, the increase in lubricant pressure may exacerbate various types of lubricant leakage problems. For example, the increase in lubricant pressure in the bearing system may cause the lubricant to leak to the exhaust turbine, to the air compressor, or to both. Escape via the exhaust turbine may cause observable levels of smoke, while escape via the air compressor may cause the lubricant to enter the intercooler, the combustion chamber (e.g., the combustion cylinder), etc.

[0040] To reduce the risk of coking and / or other lubricant issues, the system may employ water cooling, where "water" is the engine coolant circulated to the turbocharger, which may include a cast center housing having water passages and / or a water cooling jacket having water passages adapted to or otherwise operatively coupled to an oil-cooled turbocharger core (e.g., an oil-cooled center housing).

[0041] Figure 3 An example of a system 300 is shown that includes a turbocharger 320 that includes an oil passage and a water passage, such that the system 300 includes separate water supply lines and oil supply lines. Figure 3, arrows with open heads indicate a general direction of oil flow, and arrows with filled heads indicate a general direction of water flow; note that "water" may be a coolant fluid that may include one or more chemicals other than water. System 300 includes an internal combustion engine 302 having a mechanical water pump 304 and an oil pump and filter assembly 306. A water radiator 310 includes a water tank 311, and another heat exchanger 314 also provides heat exchange with water via a water line that is operatively coupled to an electric water pump 316 (e.g., an auxiliary water pump). System 300 may include an automatic transmission fluid cooler 318 that may handle automatic transmission fluid of an automatic transmission operatively coupled to the internal combustion engine 302.

[0042] The internal combustion engine 302 can be cooled by circulating water as an engine coolant through the engine block, where it is heated by internal combustion, friction, etc. The water can then be circulated to the radiator 310, where its heat is lost to the atmosphere, and the water is then returned to the internal combustion engine 302. The mechanical water pump 304 can be mechanically driven during operation of the internal combustion engine 302 to force the water to circulate. As an example, the radiator 310 can be in the airflow path of one or more fans, which can be driven mechanically and / or electrically.

[0043] Figure 3 A cross-sectional view of a turbocharger 320 is shown, the turbocharger 320 including a cast center housing 322, a compressor assembly 324 having a compressor housing and a compressor impeller operatively coupled to the cast center housing 322, a turbine assembly 326 having a turbine housing and a turbine impeller operatively coupled to the cast center housing 322, an oil passage accessible in the cast center housing 322 via an oil inlet 321 and an oil outlet 323 (e.g., an oil drain), and a water passage accessible in the cast center housing 322 via a water inlet 327 and a water outlet 329 (e.g., a water drain).

[0044] exist Figure 3 In the system 300 of FIG. 302, when the internal combustion engine 302 is running, water flows from the engine block, enters the lower end of the turbocharger 320, then comes out of the top and is routed through a tube behind the timing belt cover, which then connects to the coolant flange on the cylinder head. The water can flow through the top radiator hose and return to the radiator 310 for cooling.

[0045] When the internal combustion engine 302 is off and the water coolant temperature at the outlet of the cylinder head is above about 110 degrees C, the auxiliary electric water pump 316 can be turned on, which can provide water circulation through the top coolant line down into the turbocharger 320 and then into the engine block (e.g., to help ensure that bubbles from boiling water (e.g., coolant) are cleared). For example, the direction of water flow through the cast center housing 322 can be reversed so that the water inlet 327 becomes the outlet and the outlet 329 becomes the inlet.

[0046] Circulating the water can help maintain the center housing 322 at a reasonable temperature level, for example, helping to reduce coking of the oil in the center housing 322. The electric water pump 316 can be controlled by a post-operation temperature sensor (e.g., as part of a post-operation control unit). When the electric water pump 316 is turned on, a low-speed radiator fan can be turned on by the post-operation control unit.

[0047] The various components of system 300 add to vehicle complexity and weight. Further, electric water pump 316 and connecting hoses may be overlooked and may fail at an inopportune time.

[0048] Figure 4 A cross-sectional view of an example of a turbocharger assembly 400 is shown including a center housing 410, which may be, for example, a cast center housing that is cast from a metallic material including at least one metal (e.g., to form a metal housing, an alloy housing, or a composite metal housing) and machined to provide various surfaces, features, etc.

[0049] like Figure 4 As shown in , the central housing 410 includes an oil inlet 411 and an oil outlet 419. The central housing 410 also includes a bearing boss 430 that can be defined by a diameter around the longitudinal axis of the central housing 410, which can be an axis defined by a through hole of the central housing 410 at least partially formed by a hole surface 431.

[0050] like Figure 4 As shown in , the bearing boss 430 can receive a bearing 480, which includes a through hole that receives the shaft 402 and which includes cross-hole portions 483 and 485, wherein the cross-hole portion 483 can receive oil, and wherein the cross-hole portion 485 can receive a pin 471 as at least partially disposed in the pin hole 437 of the bearing boss 430 of the center housing 410. As an example, the sizes of the cross-hole portions 483 and 485 can be the same or can be different. As an example, the bearing 480 can be positioned in one of two orientations in which the cross-hole portions 483 and 485 can receive the pin 471. The bearing 480 can include an axial length Δz and an inner bore diameter D bThe cross-hole portions 483 and 485 may have a substantially uniform diameter, and / or one or more of the cross-hole portions 483 and 485 may be elliptical in one direction (eg, the dimension along the z-axis may be longer or shorter than the diameter in a direction orthogonal to the z-axis).

[0051] like Figure 4 As shown in , the central housing 410 includes an oil passage that is in fluid communication with the oil inlet 411 and the oil outlet 419. The oil passage includes an arcuate oil passage 450 that extends from a zone 452 proximate the oil inlet 411 to a zone 454 proximate the plug hole 415 of the central housing 410. The plug hole 415 can receive a plug 465 that can be adapted with one or more sealing elements 465 so that oil does not pass outwardly from the zone 454 through the plug hole 415. As an example, oil can flow in the arcuate oil passage in a vertical direction (e.g., clockwise or counterclockwise). In Figure 4 In the view of FIG. 4 , oil can flow in the arcuate oil passage 450 in a counterclockwise direction; note that the housing can include a different arrangement about the inlet whereby the oil can flow in a clockwise direction in such a view. For example, a cylindrical coordinate system is shown having a z-axis for z-coordinates, a radial axis for r-coordinates, and an azimuthal coordinate that starts at 0 degrees at the oil inlet 411 and spans 360 degrees in an increasing counterclockwise direction. Figure 4 Various dimensions are also shown, including the inlet diameter D of the oil inlet 411. i Plug diameter D p and the outlet diameter D of the oil outlet 419 o , inlet diameter D i Spanning the distance from zone 452 (eg, radially from z), the plug diameter D p The span is configured to be received by the plug hole 415 and has a length that extends a distance toward the zone 454 (e.g., optionally a short portion of the zone 454, even with the wall of the zone 454, or into the zone 454). Figure 4 In the example shown in FIG. 4 , the bore wall 431 has a diameter that exceeds the outer diameter of the bearing 480 , and the passage 450 has a semi-diameter (eg, inner wall radius) that exceeds the diameter of the bore wall 431 . Figure 4 In the example of the present invention, the oil inlet 411 and the plug hole 415 extend radially inwardly toward the passage 450. In the absence of the plug 465 and the pin 471, there may be a direct line of sight between the oil inlet 411 and the plug hole 415 diameter. As an example, the manufacturing method may include drilling one or more of the cross-hole portions 483 and 485 through the oil inlet 411 and / or the plug hole 415. As an example, the manufacturing method may include drilling the passage 457 through the oil outlet 419, wherein the passage 457 may extend to the hole wall 431.

[0052] like Figure 4As shown in the example of, the central housing 410 includes a passage 455 and a passage 457 in the bearing boss 430, wherein the passage 455 is in fluid communication with the zone 454 via an opening 432 in the bearing boss 430, and is also in fluid communication with the cross hole portion 483 of the bearing 480 via an opening 433 in the hole wall 431 of the bearing boss 430, and wherein the passage 457 is in fluid communication with the through hole of the bearing boss 430 via an opening 435 in the hole wall 431 of the bearing boss 430, and is also in fluid communication with the drainage zone 458 via an opening 439 in the bearing boss 430, wherein the drainage zone 458 can guide oil to the oil outlet 419. The oil drainage zone 458 can be referred to as a drainage passage and / or as a cavity (e.g., an oil cavity or an oil drainage cavity). Figure 4 As shown in the cross-sectional view of FIG. 1 , the bearing boss 430 may include a through hole and an arcuate oil passage 450 and a drainage area 458, which may be at least partially defined by an arc, and the drainage area 458 may optionally have a greater diameter than the arcuate oil passage 450 (e.g., see FIG. 1 ). Figure 8 ). As an example, the arcuate oil passage 450 can be separated from the drainage area 458 so that oil (e.g., as a lubricant and heat transfer fluid) flows from the arcuate oil passage 450 to the bore wall 431 via the opening in the bearing boss 430, and then flows from the area defined at least in part by the bore wall 431 to the drainage area 458. As an example, the bearing received by the bearing boss 430 can rotatably support the shaft of the rotating group (e.g., compressor impeller, shaft and turbine impeller) of the turbocharger, wherein the oil flows to the bearing and shaft surfaces via the arcuate oil passage 450 and then flows from such surfaces to the drainage area 458. As an example, in the absence of one or more "short circuit" passages, oil flowing to the oil inlet 411 can be exclusively passed through the bearing boss 430 to the various bearings, bore walls and shaft surfaces and then to the drainage area 458 (e.g., to the oil outlet 419). In such an example, the bearing system can present a resistance to the flow of oil and thereby, at least partially control the flow of oil through the center housing (e.g., based on the pressure provided by the oil pump to the oil inlet 411, where the pressure at the oil outlet 419 is at a lower pressure to provide a pressure drop across the center housing). As an example, to control the flow of oil, one or more short-circuit passages (e.g., see Fig.14A and 14B ) can be utilized, where such one or more passages can be sized, fitted with regulators, etc., to control how much oil (e.g., volume percentage, flow rate fraction, etc.) flows to the bearing system and how much flows to the drainage area 458 in a manner that bypasses the bearing system (e.g., a portion of the oil can flow through the bearing system and a portion of the oil can bypass the bearing system, where there are one or more bypass passages between the arcuate oil passages and the drainage area). Figure 4As shown in the example of FIG. 4 , oil entering the oil inlet 411 flows in the arcuate oil passage 450 over a span of approximately 180 degrees before being directed to the bearing system (eg, the shaft 402 , the bearing 480 , and the bore wall 431 ).

[0053] As an example, the plug hole 415 can optionally be utilized as an oil inlet and / or an oil outlet. For example, in the case where the plug hole 415 is utilized as an oil outlet, a portion of the oil flowing in through the oil inlet 411 can leave the central housing 410 before flowing through the passage 455. In such an example, the oil flow rate to the passage 455 can be appropriately adjusted or selected by using a plug 465 having one or more orifices therein. As an example, a pressure balance can be performed to determine the resistance to flow through one or more bearing paths and through one or more bypass paths. In such an example, the inlet pressure can correspond to the oil pump deliverable pressure, and the one or more outlet pressures can correspond to one or more pressures in one or more oil pipelines that are fluidly coupled to one or more corresponding openings of the central housing.

[0054] exist Figure 4 In the example of FIG. 4 , various features of the central housing 410 may be formed via casting or casting and machining. For example, the plug hole 415 may be cast and then machined to include threads, etc. Figure 4 As shown in the cross-sectional view of , the plug hole 415 of the center housing 410 can be aligned with the passage 455 of the bearing boss 430 of the center housing 410. In such an example, the passage 455 can be machined through the plug hole 415 (e.g., by inserting a tool into the plug hole 415 to contact the bearing boss 430). As another example, the pin hole 437 can be machined by inserting a tool through the oil inlet 411 and the area 452. Once properly formed, the bearing 480 can be inserted into the through hole at least partially defined by the bearing boss 430 and the pin 471, which is inserted through the oil inlet 411 and the area 452 to at least partially seat in the pin hole 437 and at least partially in the cross-hole portion 485 of the bearing 480 to axially position the bearing 480 and position it in the through hole of the bearing boss 430. As an example, in the event that pin 471 is to be moved or removed, if shaft 402 is not present, a tool can be inserted through plug hole 415 and through cross-hole portion 483 of bearing 480 (e.g., where there is some transverse axis alignment of cross-hole portion 483 with 485) so that pin 471 can be forced radially outward in pin hole 437 and pin 471 can be optionally removed through oil inlet 411.

[0055] As an example, passage 457 can be machined to a desired specification by inserting a tool through oil outlet 419 and drainage area 458. As an example, passage 457 can be machined to have a diameter and / or shape that can adjust the flow of oil. As an example, a component 490 with an orifice can be inserted into passage 457. For example, consider a threaded component that may include an external thread that can cooperate with the internal thread of passage 457. In such an example, the component can be selected and / or formed to provide a desired amount of resistance to the flow of oil from the through-hole area to the drainage area 458. Such a component can be selected and / or formed according to one or more operating conditions of the turbocharger and / or internal combustion engine system. For example, consider one or more of the oil pump operating conditions, the turbocharger shaft speed operating conditions, the temperature operating conditions, etc.

[0056] Figure 4 An end view and a cross-sectional view of a bearing 480 are shown, noting that one or more other types of bearings may be utilized in the turbocharger assembly 400. As shown, the bearing 480 includes opposite ends 482 and 484, a cross-bore portion 483, and an axial passage 486. In such an example, oil may flow from the cross-bore portion 483 as fed via the passage 455 of the bearing boss 430 and into the space between the outer surface of the shaft 402 and the inner surface of the through-bore of the bearing 480, which may include the surface of the axial passage 486.

[0057] exist Figure 4 In the example, oil can flow from passage 455 to the through hole defined by hole wall 431 and to passage 457 and / or to the ends of the through hole of bearing boss 430, which ends can correspond to opposite ends 482 and 484 of bearing 480 as at least partially disposed in the through hole of bearing boss 430.

[0058] As shown and explained, the center housing 410 can include features that allow for machining and / or assembly. Further, the center housing 410 can include an oil flow adjustment mechanism (e.g., see component 490) that can help determine how much oil flows to the oil outlet 419 via the end of the through hole of the bearing boss 430 and how much oil can flow to the oil outlet 419 via the passage 457.

[0059] exist Figure 4 In the example of , the housing 410 includes holes 422-1 and 422-2 that may be threaded to receive bolts. In such an example, the housing 410 may be attached to another component that may include, for example, a passage or conduit for receiving oil flowing through the oil outlet 419. Figure 3As shown in FIG. 4 , the turbocharger 320 includes an oil outlet 323 as indicated by an arrow and a water inlet 327 as indicated by an arrow. The housing 410 includes an oil outlet 419 and does not include a water outlet.

[0060] As an example, the oil outlet 419 and the holes 422-1 and 422-2 can be formed in a common boss, which can be a mounting boss. In such an example, the housing 410 can be mounted to a component that can be, for example, an engine block or a component attached to the engine block. As an example, the engine block can include an oil inlet for receiving oil from a housing such as the housing 410. In such an example, an oil pump associated with the engine block can be utilized to provide oil pressure to drive the flow of oil to the oil inlet 411 of the housing 410.

[0061] Figure 5A and 5B A perspective view of an example of a housing 410 is shown. As shown, the housing 410 includes a turbine end feature including an annular surface 426, a bore wall 427 defining a bore, and a flange surface 429 (e.g., for coupling to a turbine housing), and includes a compressor end feature including a flange surface 423 (e.g., for coupling to a compressor housing), an annular surface 424, and a bore wall 425 defining a bore. As shown, the bore defined by bore walls 425 and 427 is coaxial with the bore defined by bore wall 431. As such, the housing 410 includes a through-hole formed by a plurality of holes that are substantially coaxially aligned along a rotational axis of a rotating group that may include a compressor impeller, a turbine impeller, and a shaft, wherein the shaft and turbine impeller may be joined as a shaft and wheel assembly (SWA), and wherein the compressor impeller may be attached via a free end of the shaft, wherein the compressor impeller may include a partial bore or through-hole. With respect to the partial bore, sometimes referred to as a non-hole compressor impeller, it may include threads and the shaft may include machining for the threads to couple the non-hole compressor impeller to the shaft. With respect to the through bore, a nut or other component may be utilized to secure the compressor impeller to the shaft, wherein the shaft extends axially through the through bore of the compressor impeller.

[0062] Fig. 6A and 6B yes Figure 5A and 5B 4 and 5. End and side views of housing 410. Various cross-sectional views are indicated via arrows and letters. Fig. 7A A cross-sectional view taken along line AA is shown, Figure 7B A cross-sectional view taken along line BB is shown, Figure 7C shows a cross-sectional view taken along line CC, and Fig.7D A cross-sectional view taken along line DD is shown.

[0063] like Fig. 7AAs shown in the example of , the arcuate oil passage 450 has relatively symmetrical cross-sectional areas. These areas are elongated in axial length and radial width. As shown, these areas can be substantially axially disposed between the compressor side bore wall 425 and the turbine side bore wall 427, while radially offset from the central axis of the bore defined by the bore wall 431. As shown, the compressor side recess 444 is disposed between the bore wall 431 and the bore wall 425, and the turbine side recess 446 is disposed between the bore wall 431 and the bore wall 427. The recesses 444 and 446 can receive oil, for example, oil flowing axially outward from each end of the bore wall 431. The oil flowing into the recesses 444 and 446 can then be discharged radially downward toward the oil diversion area 458, as shown. Figure 7B , where it can exit via the oil outlet 419 .

[0064] As mentioned, Figure 7C and 7D Cross-sectional views taken along lines CC and DD are shown. Figure 7C and 7D An example of an arcuate shape of the arcuate oil passage 450 is shown.

[0065] Figure 8 4 is a cross-sectional view of the housing 410 with various dimensions as shown. Specifically, the bearing aperture r that partially defines the outer surface of the bearing boss 430 is shown. b , showing the radius r of the drainage cavity partially defining the inner surface of the housing 410 p , and shows the radius r of the drainage cavity partially defining the inner surface of the housing 410 d . Figure 8 Also shown is the arc Θ p and θ d , which are the curvature of the passage and the curvature of the drainage cavity, respectively. As an example, the housing and features of the housing can be described with respect to coordinates of one or more cylindrical coordinate systems, where such coordinates include axial coordinates (e.g., z), radial coordinates (e.g., r), and azimuthal coordinates (e.g., θ). As an example, individual holes or openings can be described with respect to a cylindrical coordinate system, and references can be made to them with respect to a cylindrical coordinate system, where the axial coordinate is aligned along the central axis of a through hole of the housing, which can receive a shaft supported by one or more bearings.

[0066] Fig. 9 Shows Figure 4 The various spaces of the central housing 410 are illustrated along the front of the arrows, which indicate the general direction of oil flow during operation of the central housing 410 as part of a turbocharger of an internal combustion engine system. In such an example, Figure 3The various components of the system 300 need not be included, as the center housing 410 may be an oil-only center housing (ie, a center housing without water cooling passage(s)).

[0067] Fig.10 Show Figure 4 4 is a cross-sectional view with arrows indicating the general direction of oil flow during operation of a center housing 410 as part of a turbocharger of an internal combustion engine system.

[0068] Fig.10 Also shown is a cross-sectional view of an example of a bearing 680 disposed in the center housing 410 along arrows indicating the general direction of oil flow toward the axial end of the bearing 680 and the opposite axial ends 434 and 436 of the bore wall 431 that define the through-hole of the bearing boss 430 of the center housing 410. As shown, the through-hole has opposite axial openings.

[0069] As an example, a turbocharger may include: a center housing 410; a compressor assembly operatively coupled to the center housing 410; and a turbine assembly operatively coupled to the center housing 410, wherein the center housing 410 includes a bearing boss 430 (the bearing boss 430 includes a bore wall 431 with opposite axial ends 434, 436, which define an axial through-hole with opposite axial openings), an oil inlet 411, an oil outlet 419, an arcuate oil passage 450 in fluid communication with the oil inlet 411, an oil passage 455 in fluid communication with the arcuate oil passage 450 and an opening 433 in the bore wall 431, and an oil drainage area 458 in fluid communication with the opposite axial opening of the through-hole and in fluid communication with the oil outlet 419. In such an example, the oil drainage area 458 may be a cavity that collects oil from various areas and may direct the collected oil to the oil outlet 419, which may be a drain pipe (e.g., an oil drain pipe). Such an oil outlet may be in fluid communication with a conduit or passage of another component in which oil may flow, for example, for purposes of filtering and recirculation back to the center housing via the oil inlet 411. In such an example, the turbocharger may be an oil-cooled turbocharger which does not require a turbocharger such as Figure 3 The water coolant lines and / or water coolant passages as in the system 300 may be configured to provide a plurality of coolant paths and / or channels.

[0070] Various features of the central housing 410 may be derived from Figures 4 to 10. As an example, the central housing can be defined in a cylindrical coordinate system and can include an axial through hole and can include three radial openings in fluid communication with the internal oil passage. In such an example, one of these radial openings can be an oil inlet, one of these radial openings can be an oil outlet, and another of these radial openings can be an access port that can be blocked. In such an example, the central housing can include an internal oil passage that is accessible via the oil outlet opening. In such an example, the internal oil passage can be an oil flow regulating passage that can optionally receive a regulating component, such as an annular component having one or more openings (e.g., orifices, etc.). As an example, the internal oil passage can be an oil flow bypass passage that can cause at least a portion of the flowing oil to bypass one or more oil flow paths that will direct the oil to the end of the through hole, and the through hole can receive a bearing that rotatably supports the turbocharger shaft.

[0071] As an example, a turbocharger center housing may include a cooling core oil flow rate that is defined by the amount of oil considered as carrying oil flow and the amount of oil considered as carrying oil bypass flow. In such an example, one or more diameters of an oil bypass passage (e.g., or multiple passages) may define how much or what percentage of the flowing oil is carrying oil flow and how much or what percentage of the flowing oil is carrying oil bypass flow. As an example, the diameter or other shape parameters of the passage and / or regulating component may be selected at least in part based on the capacity of an oil pump, which may be a mechanical oil pump, an electrical oil pump, or both a mechanical and electrical oil pump.

[0072] Figure 4 The central housing 410 and Figure 2The central housing 280 of the turbocharger assembly 200 is further different in that the oil flowing to the central housing 280 is through a passage directly from the oil inlet to the opening of the through hole of the central housing 280. In the central housing 280, for a given oil flow rate, the flowing oil has a low residence time between the oil inlet and the opening of the through hole. In contrast, in the central housing 410, for the given oil flow rate, the residence time of the flowing oil increases before reaching the opening 433 of the variable 431. In such an example, the increased residence time allows, for example, heat transfer from exhaust heat absorbed from the turbine assembly to the flowing oil back to the central housing 410. Such an approach can help cool the central housing 410, and, for example, allow the turbocharger to operate under various conditions without central housing water cooling features (e.g., conduits, passages, etc.). As an example, a turbocharger using the central housing 410 as an oil-only central housing can be properly operated in a scenario in which a water-cooled turbocharger is utilized. As an example, the housing may be an oil-cooled housing that includes internal passages for the flow of oil and does not include one or more passages for the flow of water. In such an example, the oil may be a lubricant and a heat transfer fluid. As a lubricant, it may form one or more lubricant films for lubrication of one or more rotating or rotatable components (e.g., a rotatable shaft, etc.).

[0073] Fig.11 An example of a radar plot 1100 is shown for temperature at a location in a turbocharger center housing, such as Figure 4 The center housing 410 at 980 degrees C (see oil cooling) and various other types of turbocharger center housings, including an air-cooled type at 800 degrees C, an air-cooled type extrapolated to 980 degrees C, and a water-cooled type at 980 degrees C. In addition, the prescribed limit (PS) is shown as a solid line.

[0074] like Fig.11 As shown in the figure, the oil cooling housing can maintain the temperature at various locations within the specified limits. As standard, the highest temperature is at the piston ring, which is shown as Figure 7B The hole groove of the hole wall 427 of the housing 410 shown in FIG. 4 provides a seating location, wherein an annular groove is shown in the hole wall 427 adjacent to the recess 446. Figure 7B As shown in , the notch 446 creates a gap between the opening of the hole wall 427 and the opening of the hole wall 431. As an example, the hole wall can be stepped (e.g., stepped hole wall) and / or can have an increasing and / or decreasing radius (e.g., or diameter). Figure 7B As shown in , the hole wall 431 has two smaller diameter parts and a larger diameter part, and the chamfered annular surface between these parts forms the transition between these parts. The hole wall 427 may include a smaller diameter part and a flared diameter part.

[0075] Fig.12 Shown does not include Figure 4 An example of a housing 1210 having an opening 439 is shown in FIG. Fig.12 As shown in FIG. 1 , the housing includes an oil outlet 1219, a bearing boss 1230 having a bore wall 1231, an arcuate oil passage 1250, and an oil drainage chamber 1258. As shown, the bore wall 1231 does not include an oil passage that is directly fluidly connected to the oil drainage chamber 1258. In such an example, oil can flow to the oil drainage chamber 1258 via the end of the bore wall 1231, such as via the notches 1244 and 1246.

[0076] Fig.13 Shown does not include Figure 4 An example of a housing 1310 having an opening 439. Fig.13 As shown in , the housing includes an oil outlet 1319, a bearing boss 1330 having a bore wall 1331, an arcuate oil passage 1350, and an oil drainage chamber 1358. As shown, the bore wall 1331 does not include an oil passage directly fluidly connected to the oil drainage chamber 1358. In such an example, the oil can flow to the oil drainage chamber 1358 via the end of the bore wall 1331, for example, via the recesses 1344 and 1346. In order to promote such flow, the bore wall 1331 may include grooves 1321-1 and 1321-2. As shown, the groove 1321-1 extends from the larger diameter portion of the bore wall 1331 toward the compressor side of the housing 1310, and the groove 1322-2 extends from the larger diameter portion of the bore wall 1331 toward the turbine side of the housing 1310. The number and size of the grooves can be selected based on flow requirements, cooling requirements, etc. As an example, the groove can be a channel extending axially with depth and width. Such a groove or channel can be defined with respect to a cylindrical coordinate system (e.g., via coordinates r, z, and θ), where z represents an axis that is the central axis of a bore of a housing that can receive one or more bearings (e.g., for rotatably supporting a shaft and a turbine wheel assembly).

[0077] Fig.14A and 14BPerspective and cross-sectional views of an example of a housing 1410 are shown, the housing 1410 including a bearing boss 1430, an arcuate oil passage 1450, an oil drainage chamber 1458, and a bypass passage 1497, the bypass passage 1497 including an opening 1496 to the arcuate oil passage 1450 and an opening 1498 to the oil drainage chamber 1458. As an example, the bypass passage 1497 can be formed by drilling a hole into the housing 1410. For example, from an external location, a drill can be used with a drill bit of a selected size and length to form the bypass passage 1497 by first drilling a hole into the housing 1410, thereby forming the opening 1492, the passage 1493, and the opening 1494. As an example, the passage 1493 can be sealed via a sealing element 1491, which can be seated into a recess at the opening 1492.

[0078] As an example, a temperature sensor and / or other type of sensor may be inserted into such a hole to a desired depth. For example, consider positioning a temperature sensor into the arcuate oil passage 1450 via opening 1492 and opening 1494. As an example, a flow sensor may be inserted to measure flow in the arcuate oil passage 1450. As an example, the sensor may be thin enough to form an annular region and other regions so that oil may flow past the sensor and through the bypass passage 1497 to the oil drainage chamber 1458.

[0079] As an example, the bypass passage can be formed via the oil outlet of the housing. For example, a drill can be inserted via the oil inlet and used to drill the bypass passage from the oil drainage cavity to the arcuate oil passage of the housing.

[0080] As an example, the arcuate oil passage can start at the bottom or top of the housing and be utilized to achieve a desired amount of heat removal capability. As an example, the arcuate oil passage can be at least partially defined by an arc. For example, the arc can be an angle in the range of about 45 degrees to about 360 degrees about the longitudinal axis of the bearing boss portion of the housing.

[0081] As an example, a turbocharger may include: a central housing; a compressor assembly operatively coupled to the central housing; and a turbine assembly operatively coupled to the central housing, wherein the central housing includes a bearing boss (the bearing boss includes a bore wall having opposite axial ends, the opposite axial ends defining an axial through-hole having opposite axial openings), an oil inlet, an oil outlet, an arcuate oil passage in fluid communication with the oil inlet, an oil passage in fluid communication with the arcuate oil passage and an opening in the bore wall, and an oil drainage passage in fluid communication with the opposite axial opening of the through-hole and in fluid communication with the oil outlet. As an example, the oil drainage passage may be an oil cavity, which may be oriented, for example, with its opening having an axis that is substantially aligned with gravity when installed in a vehicle. For example, such an opening may be a drain of an oil cavity, which may receive oil (e.g., as a lubricant and heat transfer fluid), which may be circulated in a vehicle system, filtered (e.g., by one or more filters), and returned to the central housing (e.g., via one or more pumps). As an example, the exhaust tube axis may be aligned with respect to gravity at an angle of approximately 0 degrees to approximately plus or minus 25 degrees.

[0082] As an example, a bearing boss of the housing can include a pin hole that can receive a pin such as, for example, a locating pin, which can be an anti-rotation pin that limits rotation of a bearing (e.g., or a bearing system component) at least partially disposed in a hole in the bearing boss and / or limits axial movement of such a bearing (e.g., or a bearing system component).

[0083] As an example, the bearing boss may include an oil bypass passage that is in fluid communication with an opening in the bore wall of the bearing boss and in fluid communication with an oil drainage passage (e.g., an oil cavity for drainage of oil). In such an example, a component that regulates the flow of oil from the oil bypass passage to the oil drainage passage may be included.

[0084] As an example, a turbocharger may include an oil-cooled center housing that does not include one or more water passages and corresponding water inlet and outlet openings.

[0085] As an example, the bearing boss may include a pin hole including a pin hole axis that passes through the oil inlet after the pin hole axis extends.

[0086] As an example, the bearing boss may include an oil bypass passage that is fluidly connected to an opening in a bore wall of the bearing boss and to an oil drainage passage (e.g., an oil cavity that serves as a drainage cavity that can collect oil from various zones within the housing), wherein the oil bypass passage includes a passage shaft that passes through the oil outlet after it extends.

[0087] As an example, a center housing of a turbocharger may include an arcuate oil passage that spans an arc of approximately 180 degrees around the axis of a through hole of the center housing that may receive one or more bearings that rotatably support a shaft of the turbocharger, such as a shaft of a turbine wheel and shaft assembly (SWA). As an example, the arcuate oil passage may span an arc that may be in the range of approximately 130 degrees to approximately 360 degrees.

[0088] As an example, the arcuate oil passage can be at least partially defined by a first wall of the center housing and a second wall of the center housing, the first wall including a first radius and the second wall including a second, larger radius. In such an example, along a radius line extending from a central axis of the through hole of the center housing, the difference between the first and second radii can define a size of the arcuate oil passage. As an example, such a size can vary with respect to the wheelbase or can be relatively constant. As an example, the arcuate oil passage can have a volume defined by the radius and the axis size (e.g., see Figure 8 of example housing 410).

[0089] As an example, the arcuate oil passages of the center housing may have a maximum axial length that is approximately 50 percent to approximately 150 percent of the axial length of the through-holes of the bearing bosses of the center housing (see, e.g., Fig. 7A of example housing 410).

[0090] As an example, the arcuate oil passage of the center housing can include a substantially semi-annular cross-sectional shape. For example, such an arcuate oil passage can span approximately 180 degrees about an azimuth arc of a central axis about a through hole of the center housing, the through hole receiving one or more bearings that rotatably support a shaft (e.g., a shaft and a turbine wheel assembly (SWA)), and such an arcuate oil passage can be defined by a plurality of walls, one of which can be an inner wall and another can be an outer wall, wherein both walls are walls of a cast center housing (e.g., a cast metal or alloy center housing). As an example, during manufacture of the center housing, the arcuate oil passage can be cast into the center housing. For example, a core can be provided in a mold, wherein the core is a positive volume of a suitable material (e.g., such as compacted sand, optionally with a binder (which can be polymeric, etc.), and the mold can be removed after the molten material introduced into the mold solidifies, so that the core forms a negative volume within the center housing, wherein such negative volume corresponds to the arcuate oil passage.

[0091] As an example, the central housing can be oriented with respect to gravity according to a predetermined orientation or orientation range. In such an example, the orientation range can be about the axis of the oil outlet (e.g., the discharge pipe or discharge opening) and the direction of gravity acceleration from about plus 25 degrees to about minus 25 degrees.

[0092] As an example, the arcuate oil passage of the center housing may have an arc greater than approximately 45 degrees about the axis of the axial throughbore, and / or an arc less than or equal to approximately 360 degrees about the axis of the axial throughbore.

[0093] As an example, the center housing may include a bypass passage including an opening in fluid communication with the arcuate oil passage of the center housing and an opening in fluid communication with an oil drainage passage (e.g., an oil cavity that may collect oil and direct the collected oil to a drain pipe as an oil outlet).

[0094] As an example, the central housing may include a bore wall having a through hole that may receive one or more bearings. As an example, the bearing may be a sliding bearing. As an example, the bore wall may include one or more grooves. As an example, the groove may be an axial groove or the groove may be curved along the bore wall.

[0095] As an example, a method may include: flowing oil to an oil inlet in a central housing including a bearing boss including a bore wall having opposite axial ends, the opposite axial ends defining an axial throughbore having opposite axial openings, an oil inlet, an oil outlet, an arcuate oil passage in fluid communication with the oil inlet, an oil passage in fluid communication with the arcuate oil passage and an opening in the bore wall, and an oil drainage passage in fluid communication with the opposite axial opening of the throughbore and in fluid communication with the oil outlet; receiving at least a portion of the flowing oil from the opposite axial opening of the axial throughbore in the oil drainage passage; and flowing oil from the oil drainage passage to the oil outlet. In such an example, the method may include receiving another portion of the flowing oil in the oil drainage passage via an oil bypass passage disposed in the bearing boss. As an example, the method may include flowing oil to the central housing of the turbocharger without flowing water to the central housing of the turbocharger.

[0096] Although some examples of methods, devices, systems, arrangements, etc. have been illustrated in the drawings and described in the foregoing detailed description, it will be understood that the disclosed example embodiments are not limiting but are capable of many rearrangements, modifications, and substitutions.

Claims

1. A turbine, comprising: a central housing (410); a compressor assembly operatively coupled to the central housing (410); as well as a turbine assembly operatively coupled to the central housing (410), The central housing (410) includes A bearing boss (430) comprising a bore wall (431) having opposite axial ends (434, 436) defining an axial through-bore having opposite axial openings, Oil inlet (411), Oil outlet (419), an arcuate oil passage (450) in fluid communication with the oil inlet (411), wherein the arcuate oil passage (450) extends from a first region (452) proximate the oil inlet (411) to a second region (454), and wherein the arcuate oil passage includes an arc greater than 45 degrees about the axis of the axial throughbore, An oil passage (455) in fluid communication with the arcuate oil passage (450) and the opening (433) in the bore wall (431), and an oil drainage passage (458) in fluid communication with the opposite axial opening of the throughbore and in fluid communication with the oil outlet (419).

2. The turbine of claim 1, wherein the bearing boss (430) includes a pin hole (437).

3. The turbine of claim 1, wherein the bearing boss (430) includes an oil bypass passage (457) in fluid communication with the further opening (435) of the bore wall (431) and in fluid communication with the oil drainage passage (458).

4. The turbine of claim 3, comprising means (490) for regulating the flow of oil from the oil bypass passage (457) to the oil drainage passage (458).

5. The turbine of claim 1, comprising an oil-cooled center housing, the oil-cooled center housing not including one or more water passages and corresponding water inlet and outlet openings.

6. The turbine according to claim 1, wherein the bearing boss (430) includes a pin hole (437), the pin hole (437) including a pin hole axis, and the pin hole axis passes through the oil inlet (411) after the pin hole axis extends.

7. The turbine of claim 1, wherein the bearing boss (430) includes an oil bypass passage (457) which is fluidically connected to a further opening (435) of the bore wall (431) and to the oil drainage passage (458), wherein the oil bypass passage (457) includes a passage shaft which passes through the oil outlet port (419) after the passage shaft extends.

8. The turbine of claim 1, wherein the arcuate oil passage (450) spans an arc of 180 degrees about the axis of the through hole.

9. The turbine of claim 1, wherein the arcuate oil passage (450) is at least partially defined by a first wall of the center housing (410) and a second wall of the center housing (410), the first wall comprising a first radius and the second wall comprising a second radius greater than the first radius.

10. The turbine of claim 1, wherein the arcuate oil passage (450) comprises a maximum axial length that is 50 percent to 150 percent of an axial length of the throughbore of the bearing boss (430).

11. The turbine of claim 1, wherein the arcuate oil passage (450) comprises a substantially semi-annular cross-sectional shape.

12. The turbine of claim 1, wherein the central housing (410) is oriented with respect to gravity according to a predetermined orientation or range of orientations.

13. The turbine of claim 12, wherein the range of orientation includes plus 25 degrees to minus 25 degrees about the axis of the oil outlet (419) and the direction of gravity acceleration.

14. The turbine of claim 1, wherein the arcuate oil passage comprises an arc less than or equal to 360 degrees about the axis of the axial throughbore.

15. The turbine of claim 1, comprising a bypass passage (1497) including an opening (1496) in fluid communication with the arcuate oil passage (450) and an opening (1498) in fluid communication with the oil drainage chamber (1458).

16. The turbine of claim 1, wherein the hole wall (431) includes grooves (1321-1, 1321-2).

17. A method for setting up a turbine, comprising: Oil is caused to flow to an oil inlet (411) in a central housing (410), the central housing (410) comprising: a bearing boss (430) comprising a bore wall (431) having opposite axial ends (434, 436), the opposite axial ends (434, 436) defining an axial through hole having opposite axial openings; an oil inlet (411); an oil outlet (419); an arcuate oil passage (450) in fluid communication with the oil inlet (411), wherein the arcuate oil passage (450) is an arcuate oil passage (450) extending from a first region (452) proximate the oil inlet (411) to a second region (454), and wherein the arcuate oil passage includes an arc greater than 45 degrees about the axis of the axial through hole; an oil passage (455) in fluid communication with the arcuate oil passage (450) and an opening (433) in the bore wall (431); and an oil drainage passage (458) in fluid communication with an opposite axial opening of the through hole and in fluid communication with the oil outlet (419); receiving at least a portion of the flowing oil from the opposite axial opening of the axial throughbore in an oil drainage passage (458); and The oil is caused to flow from the oil drainage passage (458) to the oil outlet (419).

18. The method of claim 17, comprising receiving another portion of the flowing oil in the oil drainage passage (458) via an oil bypass passage (457) disposed in the bearing boss (430).

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