A turbocharger turbine housing

Abstract

A turbine housing can include a bearing housing end and a process unit end; a volute wall defining a volute; a wall defining at least a portion of a turbine wheel space defining a turbine wheel space axis and a turbine wheel space diameter, wherein the wall extends to an axial peak to define an extension space having an extension space outlet having an extension space outlet dimension; and an outlet wall defining an outlet space having a process unit end outlet having an outlet dimension, wherein the extension space is at least partially axially disposed between the turbine wheel space and the outlet space to increase axial velocity uniformity at the process unit end outlet.

Description

Technical Field

[0001] The topics disclosed in this article generally relate to turbocharger turbine housings for internal combustion engines. Background Technology

[0002] A turbocharger may include a rotating assembly comprising a turbine impeller and a compressor impeller connected to each other via a shaft. For example, the turbine impeller may be welded or otherwise attached to the shaft to form a shaft and impeller assembly (SWA), and the compressor impeller may be fitted to the free end of the shaft. As an example, the shaft attached to one or more bladed impellers may be supported by one or more bearings disposed in bearing housings, which may form a central housing rotating assembly (CHRA). During turbocharger operation, depending on factors such as the dimensions of various components, the SWA may be expected to rotate at speeds exceeding 200,000 rpm.

[0003] The turbine impeller can be positioned within a turbine housing, which may include one or more volutes shaped and sized to guide exhaust flow to the turbine impeller. For example, the turbine housing may include an inlet and an outlet, wherein exhaust is guided from the inlet to one or more volutes into the turbine impeller space, and then from the turbine impeller space to the outlet. Exhaust from the outlet may be directed to one or more components for exhaust treatment, which may include treatment regarding one or more of chemical composition, heat content, and noise. Attached Figure Description

[0004] When understood in conjunction with the examples shown in the accompanying drawings, a more complete understanding of the various methods, apparatuses, components, systems, arrangements, etc., and their equivalents described herein can be obtained by referring to the following detailed description, in which:

[0005] Figure 1 It is a diagram of a turbocharger and an internal combustion engine along with its controller;

[0006] Figure 2 This is a cross-sectional view of an example turbocharger;

[0007] Figure 3 This is a side view of an example turbocharger;

[0008] Figure 4A and Figure 4B These are, respectively, a perspective view of an example turbocharger turbine housing connected to a catalytic converter and an end view of the catalytic converter;

[0009] Figure 5 These are a series of diagrams illustrating examples of phenomena associated with catalytic converters;

[0010] Figure 6It is a series of diagrams related to the exhaust flow in the turbine housing;

[0011] Figure 7 These are a series of diagrams relating to the exhaust flow in an example of a turbine housing;

[0012] Figure 8 This is a perspective view of a portion of an example of a turbocharger;

[0013] Figure 9 yes Figure 8 A cross-sectional view of a portion of the turbocharger;

[0014] Figure 10 yes Figure 8 A cross-sectional view of an example turbine housing of a turbocharger;

[0015] Figure 11 This is a cross-sectional view of an example turbine casing; and

[0016] Figure 12 This is a cross-sectional view of an example turbine casing. Detailed Implementation

[0017] Below, we describe an example of a turbocharged engine system, followed by various examples of parts, components, methods, etc.

[0018] Turbochargers are frequently used to increase the output of internal combustion engines. (Reference) Figure 1 As an example, system 100 may include an internal combustion engine 110 and a turbocharger 120. Figure 1 As shown, system 100 may be part of vehicle 101, wherein system 100 is disposed in the engine compartment and connected to exhaust pipe 103, which directs exhaust gas to exhaust outlet 109, for example, located behind passenger compartment 105. Figure 1 In one example, a treatment unit 107 may be provided to treat exhaust gas (e.g., to reduce emissions via catalytic conversion of molecules). As an example, a muffler designed to reduce noise emissions may be included, such as a silencer. As an example, a combined treatment unit and a muffler may be utilized along one or more exhaust flow paths.

[0019] like Figure 1 As shown, 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); and an intake port 114 and an exhaust port 116, the intake port providing a flow path for air to the engine block 118 and the exhaust port providing a flow path for exhaust from the engine block 118.

[0020] The turbocharger 120 can function to extract energy from the exhaust and provide energy to the intake air, which can then be combined with fuel to form combustion gases. For example... Figure 1 As shown, the turbocharger 120 includes an air inlet 134, a shaft 122, a compressor housing assembly 124 for a compressor impeller 125, a turbine housing assembly 126 for a turbine impeller 127, another housing assembly 128, and an exhaust outlet 136. The housing assembly 128 may be referred to as the central housing assembly because it is disposed between the compressor housing assembly 124 and the turbine housing assembly 126.

[0021] exist Figure 1 In the turbocharger 120, the shaft 122 may be a shaft assembly comprising various components (e.g., consider a shaft and impeller assembly (SWA) in which the turbine impeller 127 is welded to the shaft 122). As an example, the shaft 122 may be rotatably supported by a bearing system (e.g., journal bearings, rolling element bearings, etc.) disposed in the housing assembly 128 (e.g., in a bore defined by one or more bore walls), such that rotation of the turbine impeller 127 causes rotation of the compressor impeller 125 (e.g., rotatably coupled via the shaft 122). As an example, the central housing rotating assembly (CHRA) may include the compressor impeller 125, the turbine impeller 127, the shaft 122, the housing assembly 128, and various other components (e.g., a compressor side plate disposed at an axial position between the compressor impeller 125 and the housing assembly 128).

[0022] exist Figure 1 In the example, the variable geometry component 129 is shown partially disposed between the housing assembly 128 and the housing assembly 126. This variable geometry component may include blades or other components to change the geometry of the passageway leading to the turbine impeller space in the turbine housing assembly 126. As an example, a variable geometry compressor assembly may be provided.

[0023] exist Figure 1 In the example, the exhaust valve (or simply, the exhaust valve) 135 is positioned close to the exhaust inlet of the turbine housing assembly 126. The exhaust valve 135 can be controlled to allow at least some of the exhaust gas from the exhaust port 116 to bypass the turbine impeller 127. Various exhaust valves, exhaust valve components, etc., can be applied to conventional fixed-nozzle turbines, fixed-blade nozzle turbines, variable-nozzle turbines, twin-scroll turbochargers, etc. As an example, the exhaust valve can be an internal exhaust valve (e.g., at least partially inside the turbine housing). As an example, the exhaust valve can be an external exhaust valve (e.g., operatively connected to a conduit in fluid communication with the turbine housing).

[0024] exist Figure 1The example also shows an exhaust gas recirculation (EGR) line 115, which may optionally be equipped with one or more valves 117, for example to allow exhaust gas to flow to a location upstream of the compressor impeller 125.

[0025] Figure 1 Example arrangement 150 for exhaust flow to exhaust turbine housing assembly 152 and another example arrangement 170 for exhaust flow to exhaust turbine housing assembly 172 are also shown. In arrangement 150, a passage 156 is included within the cylinder head 154 to guide exhaust from the cylinder to turbine housing assembly 152, while in arrangement 170, a manifold 176 provides mounting for turbine housing assembly 172, for example, without requiring any separate exhaust pipe of intermediate length. In example arrangements 150 and 170, turbine housing assemblies 152 and 172 can be configured for use with wastegates, variable geometry assemblies, etc.

[0026] exist Figure 1 In this document, an example of controller 190 is shown including one or more processors 192, memory 194, and one or more interfaces 196. Such a controller may include circuitry such as that of an engine control unit (ECU). As described herein, various methods or techniques may be optionally incorporated into the controller, for example, through control logic. The control logic may depend on one or more engine operating conditions (e.g., turbo rpm, engine rpm, temperature, load, lubricant, cooling, etc.). For example, sensors may transmit information to controller 190 via the one or more interfaces 196. The control logic may depend on this information, and consequently, controller 190 may output control signals to control engine operation. Controller 190 may be configured to control lubricant flow, temperature, variable geometry components (e.g., variable geometry compressors or turbines), exhaust valves (e.g., via actuators), electric motors, or one or more other components associated with the engine, a turbocharger (or multiple turbochargers), etc. As an example, turbocharger 120 may include one or more actuators and / or one or more sensors 198, which may be coupled, for example, to one or more interfaces 196 of controller 190. As an example, the exhaust 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 exhaust valve may be a mechanical actuator, for example, one that can operate without electricity (e.g., consider a mechanical actuator configured to respond to a pressure signal supplied via a pipe).

[0027] Figure 2An example of a turbocharger 200 is shown, which includes a turbine assembly 201, a compressor assembly 202, and a central housing 203. The turbine assembly 201 includes a turbine housing 204 shaped to receive a turbine impeller 205, and the compressor assembly 202 includes a compressor housing 206 shaped to receive a compressor impeller 207. As shown, a shaft 208 operatively connects the turbine impeller 205 and the compressor impeller 207, supported by one or more bearings 215 and 216 in a through-hole in the central housing 203.

[0028] like Figure 2 As shown, the turbine housing 204 may include an exhaust inlet 210 and an exhaust outlet 211, wherein the volute 212 is at least partially defined by the turbine housing 204. The volute 212 may be referred to as a vortex tube, and its cross-sectional diameter decreases as it extends inwardly in a spiral shape toward the turbine impeller space that houses the turbine impeller 205.

[0029] like Figure 2 As shown, the compressor housing 206 may include an air inlet 213 and an air outlet 211, wherein a volute 214 is at least partially defined by the compressor housing 206. The volute 214 may be referred to as a volute, and its cross-sectional diameter increases as it extends outwardly in a spiral shape from the compressor impeller space housing the compressor impeller 207.

[0030] A back plate 220 is disposed between the compressor housing 206 and the central housing 203. The back plate includes a hole 221 for receiving a thrust ring 222, which can be placed abutting against the base end 223 of the compressor impeller 207. As shown, the thrust ring 222 may include a radially outwardly extending lubricant slinger 225, which can help reduce unwanted lubricant flow (e.g., into the compressor impeller space, etc.).

[0031] The central housing 203 includes various lubricant features such as a lubricant inlet 217, a lubricant orifice 218, a lubricant nozzle 219, and a lubricant outlet 229. As shown, lubricant can be supplied at the lubricant inlet 217 to flow into the lubricant orifice 218 and into the lubricant nozzle 219, which includes a compressor-side nozzle for directing lubricant to bearing 215 and a turbine-side nozzle for directing lubricant to bearing 216. Since the turbine impeller 205 is driven by an exhaust flow through the turbine housing 204, the lubricant can carry away heat from these bearings as they rotatably support the shaft 208.

[0032] like Figure 2As shown in the example, compressor housing 206 can be clamped to back plate 220 via clip 231, back plate 220 can be bolted to center housing 203 via one or more bolts 232, and center housing 203 can be bolted to turbine housing 204 via one or more bolts 233; note that various other techniques can be used to connect components to form a turbocharger.

[0033] exist Figure 2 In the examples, one or more of the housings 203, 204, and 206 can be cast. For example, turbine housing 204 can be cast from iron, steel, nickel alloys, etc. As an example, consider a corrosion-resistant Ni cast iron alloy with a sufficient amount of nickel to produce an austenitic structure. For example, consider nickel present in amounts from about 12 wt% to about 40 wt%. As an example, an increased amount of nickel can provide a reduced coefficient of thermal expansion (e.g., consider a minimum of about 35 wt%). However, the increased nickel content increases the cost of the corrosion-resistant Ni material; note that the density tends to be relatively constant over a wide range of nickel contents (e.g., about 7.3 to 7.6 grams per cubic centimeter). The density of the corrosion-resistant Ni material tends to be about 5% higher than that of gray cast iron and about 15% lower than that of cast bronze alloys. Regarding machinability, the corrosion-resistant Ni material tends to be superior to cast steel; note that the increased chromium content tends to decrease machinability due to the increased amount of hard carbides. When compared to stainless steel (e.g., with a density of approximately 8 grams per cubic centimeter), corrosion-resistant Ni materials can be less expensive and lighter (e.g., with a lower density).

[0034] Corrosion-resistant Ni materials tend to exhibit suitable high-temperature properties, with rated temperatures exceeding 480 degrees Celsius (900 degrees Fahrenheit). Corrosion-resistant Ni materials are suitable for use in turbochargers for diesel and gasoline internal combustion engines. As an example, a diesel engine may have exhaust gases that can reach approximately 860 degrees Celsius, and a gasoline engine may have exhaust gases that can reach approximately 1050 degrees Celsius. This exhaust gas can be received by a turbine assembly comprising a turbine housing made of a suitable material.

[0035] As shown in the figure, the turbine housing 204 can be a relatively large component compared to the compressor housing 206 and the central housing 203, so that the mass of the turbine housing 204 makes a significant contribution to the mass of the turbocharger 200.

[0036] exist Figure 2In the example, various components of the turbocharger 200 can be defined relative to a cylindrical coordinate system including a z-axis centered on a through-hole in the central housing 203, which can coincide with the axis of rotation of a rotating assembly including a turbine impeller 205, a compressor impeller 207, and a shaft 208. As mentioned, the turbine impeller can be welded to the shaft to form a shaft and impeller assembly (SWA), and the compressor impeller can be threaded onto an end of the shaft (e.g., a "holeless" compressor impeller) or have a through-hole receiving a free end of the shaft, where a nut or other suitable component is used to secure the compressor impeller to the shaft. Figure 2 In the example, turbine impeller 205 is welded to shaft 208, and nut 235 is used to secure compressor impeller 207 to shaft 208 and thus to turbine impeller 205.

[0037] exist Figure 2 In the example, a gap exists between the blades 254 extending from the hub 252 of the turbine impeller 205 and the shroud portion 240 of the turbine housing 204. As shown, the shroud portion 240 (J-shaped in cross-sectional view) may define a rotating body having an annular ridge portion 242 and a cylindrical portion 244. As shown, the annular ridge portion 242 may define a nozzle for exhaust gas flowing from the volute 212 into the turbine impeller space at the inlet section of the turbine impeller 205, which may be defined by a leading edge, where each of the blades 254 includes a leading edge (LE). As shown, the turbine impeller 205 also includes an outlet section, where each of the blades 254 includes a trailing edge (TE). During operation, exhaust gas flows from the volute 212 to the leading edge of the blade 254 via a nozzle partially defined by the annular ridge 242 of the shroud portion 240, along a channel defined by the adjacent blades 254 of the turbine impeller 205, as confined between the hub 252 and the cylindrical portion 244 of the shroud portion 240, and then to the trailing edge of the blade 254, where the exhaust gas is confined by a larger diameter cylindrical wall 272, a slightly conical wall 274, and an even larger diameter cylindrical wall 276. Figure 2 As shown, the cylindrical wall 276 may be defined by a portion of the turbine housing 204, which includes fittings such as an annular ridge 282, which can be used to secure an exhaust duct to the turbine housing 204. This exhaust duct may be in fluid communication with one or more other components, such as an exhaust treatment unit, a muffler, another turbocharger, etc. Regarding the exhaust inlet 210 of the turbine housing 204, it may also be shaped to connect to one or more exhaust ducts, such as, for example, an exhaust manifold, an exhaust crosspipe, another turbine housing (e.g., for a multi-stage turbocharger arrangement), etc.

[0038] like Figure 2 As shown, the turbine housing 204 separates various functions by its structural features and its shape; however, these structural features can contribute to the quality of the turbocharger.

[0039] As an example, the weight of a turbocharger can range from about 4 kg (e.g., 8.8 lbs) to about 40 kg (e.g., 88 lbs) or more.

[0040] As mentioned, the turbocharger can be defined relative to a cylindrical coordinate system, in which the z-axis can be along its length. Figure 2 In the example, the length of the turbine housing 204 exceeds 50% of the total length. The total length or size of the turbocharger can be a factor when it is installed in the engine compartment of a vehicle, as it exhibits design constraints.

[0041] Figure 2 The turbocharger 200 can be cooled by one or more media, such as lubricant (e.g., oil), water (e.g., radiator fluid), and air (e.g., via an environment with ambient air or vehicle engine compartment air).

[0042] There are some trade-offs regarding lubricant cooling (e.g., oils, whether natural, synthetic, etc.). For example, carbonaceous lubricants may carbonize (e.g., also known as coking or “coking”) if they reach excessively high temperatures for too long (e.g., considering time-temperature correlation). Coking exacerbates heat generation and retention through any of a variety of mechanisms, and over time, coke deposits shorten the life of the lubricated bearing system. As an example, coke deposits can cause reduced heat transfer and increased heat generation, which can lead to bearing system failure. To overcome coking, turbochargers can be configured to improve lubricant flow. For example, pumps can pressurize the lubricant to increase flow rate, thereby reducing the lubricant's residence time in high-temperature regions. However, increased lubricant pressure can exacerbate various types of lubricant leakage problems. For example, increased lubricant pressure in a bearing system can cause lubricant to leak into the exhaust turbine, air compressor, or both. Leaks via the exhaust turbine result in observable smoke levels, while leaks via the air compressor can cause lubricant to enter the intercooler, combustion chamber (e.g., combustion cylinder), etc.

[0043] Regarding the temperatures experienced during operation, these can depend on the temperature of the exhaust gas flowing to the exhaust turbine of the turbocharger, which can depend on whether the internal combustion engine is gasoline or diesel fuel (for example, as mentioned, a diesel engine may have exhaust gas at approximately 860 degrees Celsius, and a gasoline engine may have exhaust gas at approximately 1050 degrees Celsius). Furthermore, regarding temperature, consider... Figure 1Example arrangements 150 and 170, in which turbine housing assemblies 152 and 172 are very close to the combustion cylinder, which may cause turbine housing assemblies 152 and 172 to experience higher exhaust temperatures and / or higher ambient temperatures.

[0044] Figure 3 An example of a turbocharger 300 is shown, which includes: a compressor assembly 340 having a compressor housing for a compressor impeller; a turbine assembly 360 having a turbine housing for a turbine impeller; a central housing 380 for one or more bearings or bearing assemblies to rotatably support a shaft and impeller assembly (SWA); and an actuator 350 having a link 354 to a control arm assembly 358 for a wastegate of the turbine assembly 360. The turbocharger 300 may include... Figure 2 One or more of the components shown. In Figure 3 In the view, the exhaust inlet of the turbine assembly 360 is not visible because it is on the opposite side. The overall direction of air or exhaust flow is indicated by arrows. The actuator 350 is shown mounted to the compressor assembly 340, which helps to reduce the temperature experienced by the actuator 350 (e.g., compared to mounting the actuator on the turbine housing). The turbocharger 300 can be a vehicle (such as, for example, Figure 1 Part of vehicle 101. As an example, the turbine assembly 360 may optionally be such as Figure 1 The example arrangement is one of 150 or 170.

[0045] Figure 4A and Figure 4B The diagram shows an example view of a portion of a system including a manifold 176, a turbine housing 460, and a treatment unit 1000. As shown, the turbine housing 460 may be integral with the manifold 176 and may include a flange 498 for connection to the treatment unit 1000, for example, via a flange 1020. The treatment unit 1000 may include a flared pipe 1030 that increases in diameter from the flange 1020 to a catalyst housing 1040, at which the flared pipe 1030 may include one or more fittings 1035 for device connection (e.g., one or more sensors, one or more pipes, etc.). As shown, the treatment unit 1000 may include a flange 1020 as a proximal flange and another flange 1080 as a distal flange, wherein exhaust gas flows generally in a direction from flange 1020 to flange 1080. The flange 1020 may include a feature 1021 for coupling to the turbine housing 460 via bolts or the like. As an example, belts, threads, bayonets, etc., may be used to couple the turbine housing to the processing unit.

[0046] like Figure 4B As shown, flange 1020 may include an opening 1022 leading to flared tube 1030, which in turn leads to an opening 1042 leading to catalyst housing 1040. As shown, catalyst assembly 1050 may be disposed in catalyst housing 1040, in which, for example, catalyst assembly 1050 may include support material supporting one or more catalysts.

[0047] Emissions from internal combustion engines can include components such as carbon monoxide, unburned hydrocarbons, and nitrogen oxides. Catalytic converters (e.g., treatment units) can reduce emissions; however, they introduce some losses, such as increased engine back pressure. As an example, a catalytic converter can include one or more types of catalyst assemblies. For example, consider concentric methods, spiral methods, etc., that provide relatively straight pathways along the length of the catalytic converter. As an example, consider a monolithic cordierite ceramic, which can be formed into a honeycomb structure with straight channels. In various cases, straight channels help reduce pressure loss and provide higher pollutant conversion efficiency due to better flow distribution.

[0048] While the configuration of the treatment unit affects flow distribution, as explained in this article, so do turbine assemblies. For example, if the exhaust flow is unevenly distributed as it leaves the turbine housing, it may be unevenly distributed as it enters the treatment unit. In this example, features of the treatment unit designed to provide better flow distribution help to maintain the uneven distribution of the incoming exhaust.

[0049] The paper “Understanding Flow through Catalytic Converters” by Ibrahim et al. (Proceedings of the 4th International Conference on Fluid Flow, Heat and Mass Transfer, Canada, August 21-23, 2017, Paper No. 135 (DOI: 10.11159 / ffhmt17.135) is incorporated herein by reference. Ibrahim et al.’s paper presents computational fluid dynamics (CFD) modeling results of the flow behavior through a catalytic converter using a model with a straight vertical inlet pipe (5 cm inlet diameter and 53 cm length) connected to a bulk container with a 7.6 cm diameter and 7.6 cm length, which is connected to an outlet pipe 18 cm long and 5 cm diameter. Both the inlet and outlet diffusers have a 45˚ cone angle and a length of 2.5 cm. As indicated, the inlet flow profile to the bulk container benefits from an axial length exceeding ten diameters (i.e., 5 cm diameter and 53 cm length). A straight tube (cm in length) along with an inlet diffuser (flared tube). Ibrahim et al.'s article does not mention a turbocharger.

[0050] Figure 5 Various graphs illustrating the general results of the CFD modeling in Ibrahim et al.'s article are shown, including a graph of a catalytic converter 1040 with inlet 1020, inlet diffuser 1030, outlet diffuser 1060, and outlet 1080, wherein a catalyst assembly 1050 is contained within the catalytic converter. As shown, the exhaust velocity is relatively uniform as it enters the inlet diffuser 1030, where the velocity decreases. As indicated, the pressure contour lines represent the pressure decrease as the exhaust flows through the catalytic converter 1040.

[0051] The article by Ibrahim et al. points out that flow uniformity can be increased by utilizing a bulk material with a higher unit density and smaller hydraulic diameter, and by dividing the bulk material into two parts separated by gaps. They also observe lower flow uniformity in 3D steady-state and transient numerical simulations of systems with a high bulk-to-inlet diameter ratio. Furthermore, the article notes that the bulk material acts as a flow resistance zone, creating a high-pressure region at the center of the catalytic converter that forces flow redistribution to the sides, and that "the design of the inlet diffuser plays a crucial role in converter design."

[0052] Refer again Figure 4A For example, space for a 10-diameter axially long pipe may not be available in the engine compartment, and the turbine housing may, for instance, be integrally cast with the exhaust manifold. In various applications, heat conservation can improve turbine performance and can also improve catalytic converter performance. Heat conservation can be achieved by reducing the flow path length, which also reduces wall losses in the exhaust flow.

[0053] exist Figure 4A In the example, the outlet of turbine housing 460 directs exhaust gas into processing unit 1000, where the relatively short distance from the turbine impeller space to the outlet helps reduce diffusion (e.g., helps align the gas into the catalyst and ensure stable function). A measure of the exhaust gas exiting the turbine housing can be a uniformity index, or it can be a specification of the processing unit. For example, a higher uniformity index of the turbine housing can help provide a specified catalyst inflow uniformity index and pressure gradient, both of which tend to define and ensure proper catalyst function. Proper function of the catalyst assembly tends to depend on appropriate heat distribution at the inlet of the catalyst assembly. The flow uniformity index can specify the catalyst reaction efficiency.

[0054] Another potential design factor that can affect functionality is, such as Figure 4AAs shown in the example, the axis of the turbine housing 460 (e.g., the turbine impeller rotation axis) is displaced relative to the axis of the catalyst assembly 1050 of the processing unit 1000. This displacement results in uneven heat distribution at the catalyst inlet region, where, for example, flow may not be perpendicular to the front surface of the catalyst assembly 1050. This factor affects the catalyst reaction efficiency and, in combination with the catalyst reaction efficiency, affects the stability of the gas conversion.

[0055] Figure 6 Example drawings 601 and 603 show the exhaust flow of a turbine housing 660, illustrated in cross-sectional views. As shown, the turbine housing 660 includes opposing ends 662 and 664, a volute wall 670, a nozzle space 672, a turbine impeller space 674, and an outlet space 678, wherein the turbine space 674 and the outlet space 678 are defined by a wall 690. Dimensions may include the shroud diameter D of the turbine impeller space 674. s And the exit diameter D of the exit space 678 out The axial dimension Δz of the wall 690, together with the wall 690, can be utilized, as explained, by taking advantage of the relatively short axial distance between the turbine impeller space 674 and the end 664.

[0056] exist Figure 6 In the turbine housing 660, there is a continuous wall 690, the cross-sectional area of ​​which is from the area corresponding to D. s The axial position corresponding to D out The axial position increases, and except for a relatively small portion near the end 664, this portion can have a constant cross-sectional area (e.g., the cylindrical portion of wall 690).

[0057] exist Figure 6 In the example, the uniformity index of the axial velocity is 0.8, where D out D s It is approximately 230% of Δz and approximately 122% of Δz. As shown in Figures 601 and 603, the axial velocity tends to be higher near the wall 690 and lower near the center (see, for example, the contour lines 90 near the wall and 10 near the center). The differences in the contour line values ​​and positions result in a homogeneity index that is substantially less than one (e.g., 0.2 less than one).

[0058] Figure 7Example drawings 701 and 703 show the exhaust flow of a turbine housing 760, illustrated in cross-sectional view. As shown, the turbine housing 760 includes opposing ends 762 and 764, a volute wall 770, a nozzle space 772, a turbine impeller space 774, an extension space 776, and an outlet space 778, wherein the extension space 776 is disposed between the turbine impeller space 774 and the outlet space 778. As shown, a wall 780 defines the turbine impeller space 774 and the extension space 776, wherein the wall 780 transitions to a wall 790 defining the outlet space 778. As shown, the wall 780 reaches an annular axial peak 784, at which it descends axially along a substantially cylindrical portion 786 to an annular axial valley 788. The wall 790 then extends from the annular axial valley 788 to the end 764.

[0059] exist Figure 7 In the example, turbine housing 760 includes a transition region where wall 780 transitions to wall 790. As shown, there is no single wall that increases the cross-sectional area; instead, wall 780 can be set within wall 790, with the transition region connecting wall 780 and wall 790. Figure 7 In the example, the turbine housing 760 includes double walls for various axial positions. For instance, consider an axial position where the cut plane is exactly above the annular axial valley 788, where wall 780 forms a passage defined by wall 790. As an example, the annular axial peak 784 of wall 780 may extend axially beyond... Figure 7 The example shows a higher one. For example, consider an annular axial peak 784 extending toward and / or beyond end 764 (e.g., to define the total axial length of turbine housing 760).

[0060] like Figure 7 As shown, the dimensions may include the shroud diameter D of the turbine impeller space 774. s And the export size D of the export space 778 out Including the axial dimension Δz. Exit dimension D out This can be the diameter of a circular outlet or the size of a non-circular outlet (e.g., an oval outlet, an elliptical outlet, etc.). As explained, the relatively short axial distance between the turbine impeller space 774 and the end portion 764 can be utilized. Additionally, the size may include an extended axial dimension Δz. e and the size D of the intermediate outlet as the outlet of the extended space 776 e The size D e It can be the diameter of a circular outlet or the size of a non-circular outlet (e.g., an oval outlet, an elliptical outlet, etc.).

[0061] exist Figure 7 In the example, the uniformity index of the axial velocity is 0.9, where D out Ds Approximately 230% of and approximately 122% of Δz, where D e D out Approximately 60% and of D s 138%, along with Δz e It is approximately 78% of Δz; it should be noted that, as mentioned above, Δz e Δz can be defined, where peak 784 extends beyond end 764. As shown in figures 701 and 703, as the difference between the lower and higher contour lines decreases, the axial velocity tends to become more uniform, making it more consistent with... Figure 6 Compared to the example, the higher velocity near wall 790 decreases.

[0062] Figure 8 A perspective view of an example portion of a turbocharger 700 is shown, the turbocharger having a turbine housing 760 including one or more inlet passages 761 and a wall 780 that may define at least a portion of an outlet passage 763. As shown, the axis of the turbine impeller 722 is offset (e.g., displaced) from the axis of the opening 765. In this example, these axes may be parallel, or, for example, the axis of the opening 765 may be slightly inclined (e.g., less than approximately 45 degrees) relative to the axis of the turbine impeller 722. Figure 8 In one example, the one or more inlet passages 761 extend outward, wherein the axis of the opening 765 is offset from the axis of the turbine impeller 722 along the general direction of the one or more inlet passages 761. In this example, the opening 765 may be large enough to be coupled to the processing unit without increasing the overall footprint of the turbine housing 760; note that in various other examples, the turbine housing may be shaped differently, constructed differently, etc., relative to the one or more inlet passages (see, for example, [link to relevant documentation]). Figure 4A The turbine housing 460 can be integrated with the manifold 176.

[0063] Figure 8 An example of a cylindrical coordinate system is also shown, which has a z-coordinate along the z-axis, an r-coordinate along the r-direction, and an azimuth angle θ. Figure 8 In the example, dimensions in a cylindrical coordinate system can be used to define the turbine housing 760 and / or the wall 780 of the turbocharger 700 and one or more other features. As an example, the surface of the wall 780 can be a surface of revolution along an azimuth direction (represented by angle θ), where rotation can occur about the z-axis. As an example, the wall 780 can extend approximately 360 degrees equally to an edge (e.g., peak 784), or, for example, the wall 780 can extend to an edge at varying heights from the base, which can be uniform or non-uniform. As an example, the edge (e.g., peak 784) can lie in a plane perpendicular to the z-axis or inclined at an angle relative to the z-axis.

[0064] exist Figure 8 In this example, the angle θ may be zero degrees along a direction that could be the direction of the one or more inlet passages 761 and / or the volute inlet. In this example, peak 784 (e.g., edge) may be closest to wall 790 at or approximately at an angle θ equal to zero (e.g., positive or negative 15 degrees). As an example, wall 780 may transition to wall 790 without valleys, where it is closest to wall 790 (e.g., valley 788 may be less than 360 degrees around wall 780).

[0065] Figure 9 A cross-sectional view of a portion of a turbocharger 700 is shown, the turbocharger including: a shaft and impeller assembly 720 including a turbine impeller 722, an insert 730 for a variable nozzle tube (e.g., VNT, etc.), and a turbine housing 760. Figure 9 Also, the size Δz f This is shown as the axial distance from the peak 784 of the turbine housing 760 to the end 764. Figure 9 The diagram shows an angle γ that can, for example, at least partially define a valley 788 relative to a plane, wherein the axis of rotation (e.g., the axis of the turbine impeller space) is perpendicular (or orthogonal) to that plane. Figure 9 In the example, the angle γ is approximately 10 degrees, as defined by the line passing through the two marked valley points 788-1 and 788-2. Figure 9 In the example, angle γ can be the maximum angle, where valley point 788-1 is the highest and valley point 788-2 is the lowest. As an example, for a portion of the turbine housing, the valley points may approximately coincide with the peak points. As an example, the valley can be a continuous annular valley, or, for example, part of an annulus (e.g., less than 360 degrees around the peak). When wall 780 is surrounded by valleys 788 smaller than a complete annulus (e.g., less than 360 degrees), wall 780 may include a region that transitions to wall 790 without descending to valley 788. For example, in Figure 8 In the turbine housing 780, the valley 788 can be less than 360 degrees around the wall 780, such that for a portion of the 360 ​​degrees, the wall transitions to the wall 790 without descending to the valley 788.

[0066] like Figure 9 As shown in the example, wall 780 may include an inner axial height and an outer axial height, wherein the outer axial height may be partially defined via valley 788, where the outer axial height may vary azimuthally about the axis of the turbine impeller space. As an example, wall 780 may define a volume relative to wall 790, wherein this volume may be asymmetrical. For example, the volume may be larger where valley 788 is deeper.

[0067] As explained, the function of the catalyst in the processing unit can depend on the heat distribution at the inlet of the processing unit. The uniformity of the flow at the inlet can be defined using a flow uniformity index, or, for example, computational fluid dynamics (CFD), where flow and flow patterns (e.g., contour lines, streamlines, etc.) can be analyzed. As explained, increased flow uniformity can improve catalyst reaction efficiency. Because the position of the turbocharger turbine impeller axis can be shifted relative to the catalyst processing unit axis in the absence of walls (e.g., wall 780), the heat distribution at the catalyst inlet region will be less uniform and, for example, may differ from the direction perpendicular to the catalyst inlet region. Lack of uniformity affects catalyst reaction efficiency and the stability of gas conversion (e.g., emissions).

[0068] like Figure 9 As shown in the example, wall 780 can be a housing duct portion that directs the exhaust flow to a desired area at the outlet, where, for example, the distance can be relatively short (e.g., measured as turbine impeller axial length, turbine leading edge blade axial height, etc.). Such a housing duct portion (e.g., an inner duct or passage portion) can guide the exhaust flow, where it can be more uniform at the catalyst inlet region of the treatment unit. Wall 780 can help align the exhaust flow to the catalytic region, which can also help ensure stable function. Wall 780 can be referred to as an inner housing stack tube, which can be at least partially inside the outer wall (e.g., wall 790), such that the turbine housing can be referred to as “double-walled” at least in the azimuth-defined portion. Such an inner housing stack tube can help achieve the desired catalyst inflow uniformity index value (e.g., flow profile, etc.) and, for example, the desired pressure gradient (e.g., pressure profile, etc.) for proper treatment unit catalyst function.

[0069] As an example, wall 780 can be shaped such that, for instance, more uniform flow is achieved in a manner that avoids the risk of overheating the catalyst in the region of the processing unit when the turbocharger can operate at peak power. For example, uniform flow can reduce the risk of hot spot formation. In the case of non-uniform flow, it may have a significantly greater velocity along the centerline, where the impact of this higher-velocity flow can cause hot spots in the catalyst region of the processing unit.

[0070] exist Figure 9 In the example, the "double-wall" method can provide a certain amount of heat conservation because wall 780 is at least partially defined by wall 790, where wall 790 is the outer wall (e.g., consider heat exchange with the cooler surrounding environment around the outer wall). Figure 9 In this process, wall 780 serves as a conduit or tube that helps separate the flow from wall 790 at specific axial locations, which can promote flow uniformity in front of the catalyst region of the processing unit.

[0071] exist Figure 9 In the example, wall 790 may be suitably sized and / or shaped to accommodate one or more standardized attachment diameters of one or more processing units. Figure 9 In the example, wall 780 performs a flow homogenization function, while wall 790 performs a turbine housing shaping function for operatively attaching the turbine housing to the processing unit. Figure 9 In the example, the "double-wall" method allows each wall to be individually customized to perform one or more of its specific functions, while providing, for example, a certain amount of heat retention (e.g., reducing heat loss), wherein space (e.g., volume) exists between at least a portion of wall 780 and wall 790. As explained, wall 780 may be at least partially an inner wall, and wall 790 may be an outer wall, wherein flow and heat can be appropriately directed to the catalyst inlet region of the processing unit.

[0072] In various examples, the inner duct may be cast as part of the turbine housing and / or provided as a separate part that can be fitted to the turbine housing. As an example, the turbine housing may include attachment features, such as threads or bayonets, wherein the walls may include corresponding attachment features. In this example, depending on the application, processing unit, space, etc., an appropriate wall may be selected and then coupled to the turbine housing to provide flow uniformity to the processing unit.

[0073] Figure 10 A cross-sectional view of the turbine housing 760 is shown, along with the angular dimension α (which is the angle of the wall 780) and the overall length dimension Δz. TH Connection dimension D with the central housing CH .

[0074] Figure 11 A cross-sectional view of an example turbine housing 860 is shown, where angle α is shown as approximately 6.2 degrees, and where the cone's angle can be twice α, for example, approximately 12.4 degrees. Figure 11 The dimension b, representing the height of the turbine impeller leading-edge blade, and the dimension Δz, representing the distance from the tip of the leading-edge blade to the wall at 880°, are also shown. bc (It can be defined by angle α), and size Δz c (It can be the cone size that can characterize the wall 880), note that the size h can be the cone size measured from the apex or origin of the cone.

[0075] As an example, wall 880 can be characterized by an angle α ranging from about 0 degrees to about 15 degrees, or for example, from greater than 5 degrees to about 15 degrees. As for the cone angle (e.g., 2α), consider greater than 10 degrees to about 30 degrees.

[0076] A circular cone or a portion thereof may be defined by a dimension along an axis (such as the z-axis in a cylindrical coordinate system), wherein the circular cone or a portion thereof increases in its radial dimension, as can be measured via the r-axis. The surface may be a surface of revolution along an azimuth direction, represented by an angle θ. As an example, the cone may extend approximately 360 degrees equally to its edge, or, for example, the cone may extend to edges at varying heights from its base, these heights may be uniform or non-uniform.

[0077] As an example, a right circular cone can be partially defined by its opening angle. For instance, consider a right circular cone of height h and radius r, where the opening angle (or aperture angle) θ (e.g., consider 2α) can be defined by the following equation:

[0078] .

[0079] As an example, a region can be defined by volume, one or more areas, one or more tilt heights, etc. For example, consider the volume of a cone (e.g., A b It refers to the base area or the top area.

[0080] Figure 12 A cross-sectional view of an example turbine housing 960 is shown, wherein a wall 980 may be integrally formed with the turbine housing 960 and / or formed via a separate wall member 981 that can be fitted to the turbine housing 960. For example, consider that the turbine housing 960 includes features 969 such as threads, and the wall member 981 has features such as mating threads 989. As shown, the wall member 981 may include an axial height Δz. w The axial height can be selected by choosing a specific compatible wall component (e.g., having a desired size, shape, etc.). As an example, wall component 981 can be threaded into a socket of turbine housing 960, such that the threaded engagement secures wall component 981 to turbine housing 960. With wall component 981, wall 980 can be defined partly via wall 968 of turbine housing 960 and partly via wall component 981. In this example, the dimension Δz... c It can be the sum of two axial heights. Although in Figure 12 The example mentions threads, but one or more other techniques, skills, etc. (e.g., bayonet, interference fit, welding, etc.) can be used.

[0081] As an example, when using a separate wall component 981, one or more gaps 967 (e.g., radial gaps) may exist, which can help reduce heat transfer from the wall component 981 to the turbine housing 960. If heat transfer is reduced, more exhaust heat can be retained for use by the catalyst region of the treatment unit.

[0082] exist Figure 12 In the example, angle α is shown as approximately 13.1 degrees, where the angle of the cone can be twice α, for example, approximately 26.2 degrees. Figure 12 The dimension b, representing the axial height of the turbine impeller leading-edge blade, and the dimension Δz, representing the distance from the tip of the leading-edge blade to the wall at 980°, are also shown. bc (It can be defined by angle α), and size Δz c (It can be the cone size that can characterize the wall 980), note that the size h can be the cone size measured from the apex or origin of the cone.

[0083] As an example, wall 980 can be characterized by an angle α ranging from about 0 degrees to about 15 degrees, or for example, from greater than 5 degrees to about 15 degrees. As for the cone angle or opening angle (e.g., 2α), consider greater than 10 degrees to about 30 degrees.

[0084] As shown in various examples (see, for example) Figure 7 , Figure 8 , Figure 9 , Figure 10 , Figure 11 and Figure 12 The turbine housing 760 (or turbine housing 860 or 960) may include: a bearing housing end 762 and a processing unit end 764; a volute wall 770 defining a volute; and a wall 780 (e.g., wall 880 or wall 980) defining at least a portion of the turbine impeller space, which defines the turbine impeller space axis and the turbine impeller space diameter D. s The wall 780 extends to the axial peak to define an extension space with an extension space outlet having an extension space outlet size D. e ; and an outlet wall 790, which defines an outlet space having an outlet at the end of a processing unit, the outlet having an outlet size D. out The extension space is axially positioned between the turbine impeller space and the outlet space to increase the uniformity of axial velocity at the end outlet of the processing unit.

[0085] As an example, wall 780, wall 880, or wall 980 may be symmetrical about an axis and represented, for example, by a rotation according to an angle α or, for example, a cone angle 2α, or, for example, wall 780, wall 880, or wall 980 may be characterized by an angle α, while being partially different from a surface of rotation about an axis. For example, consider using an angle α to characterize the average diameter of wall 780, wall 880, or wall 980 between a smaller upstream diameter and a larger downstream diameter.

[0086] As an example, the turbine housing may include: a bearing housing end (e.g., see end 762) and a processing unit end (e.g., see end 764); a volute wall (e.g., see volute wall 770) defining a volute; and walls (e.g., see walls 780, 880, and 980) defining at least a portion of the turbine impeller space, which defines the turbine impeller space axis and the turbine impeller space diameter (D). s The wall extends to the axial peak to define an extended space with an extended space outlet having an extended space outlet size (D). e ); and an outlet wall (see, for example, outlet wall 790), which defines an outlet space having an outlet at the end of the processing unit having an outlet size (D). out The extension space is at least partially axially positioned between the turbine impeller space and the outlet space to increase the uniformity of the axial velocity at the end outlet of the processing unit. In this example, a portion of the wall defining the extension space may be positioned at an angle relative to the axis of the turbine impeller space, wherein the angle is greater than 0 degrees and less than 15 degrees, for example, consider an angle greater than 5 degrees and less than 15 degrees. As an example, such an angle may be in the range of greater than 6 degrees and less than 15 degrees.

[0087] As an example, the turbine housing may include the turbine impeller space diameter (D). s ), extended space exit dimensions (D e ); and having an export size (D) out The processing unit end outlet of ) where D s < D e < D out As an example, the axial distance from the axial peak of the wall to the end outlet of the processing unit can be less than D. s As an example, D e It can be greater than D s 110% and less than D s 200%.

[0088] As an example, the turbine housing may include walls descending from an axial peak to an axial valley (e.g., see walls 780, 880, and 980). In this example, the turbine housing may include a transition from one wall to another (e.g., see wall 790), where this transition is located at an axial valley. As an example, the depth of the axial valley may vary relative to the axial peak or axial edge. For example, in Figure 8 In this context, the axial valley 788 can vary with angle θ, making it deeper on one side compared to the opposite side. For example, the depth of the axial valley can vary along the azimuth angle around the turbine impeller's spatial axis. Figure 8 As shown in the example, the axial valley 788 is deeper on the side corresponding to the inlet side of the volute, which is at least partially defined by the turbine housing 760 (see, for example). Figure 8 One or more inlet passages 761). As an example, the axial valley may define a plane that can be tilted relative to the spatial axis of the turbine impeller (e.g., along such a plane). Figure 8 , Figure 9 , Figure 10 , Figure 11 or Figure 12 (The tilt direction shown).

[0089] As an example, the turbine housing may include a processing unit end outlet that defines an outlet axis offset from the turbine impeller spatial axis. In this example, the axial peak may be an annular axial peak centered on the turbine impeller spatial axis.

[0090] As an example, the turbine housing can be part of an assembly that includes an insert that partially defines the turbine impeller space. For example, consider an insert as a variable nozzle barrel insert (e.g., part of a variable nozzle barrel, etc.).

[0091] As an example, the turbine housing may include a multi-cylinder exhaust manifold. For instance, consider a multi-cylinder exhaust manifold integrally cast with the turbine housing.

[0092] As an example, a turbocharger may include: a bearing housing assembly; and a turbine housing assembly, wherein the turbine housing assembly includes: a bearing housing end and a processing unit end; a volute wall (e.g., one or more volute walls) defining a volute (e.g., one or more volutes); and a wall defining at least a portion of a turbine impeller space, the turbine impeller space defining a turbine impeller space axis and a turbine impeller space diameter (D). s The wall extends to the axial peak to define an extended space with an extended space outlet having an extended space outlet size (D). e ); and an outlet wall that defines an outlet space having an outlet at the end of the processing unit, the outlet having an outlet size (D). out The extended space is at least partially axially positioned between the turbine impeller space and the outlet space to increase the uniformity of axial velocity at the end outlet of the treatment unit. In this example, the turbocharger may include a treatment unit. For example, consider a treatment unit coupled to the turbine housing to receive exhaust gas via the end outlet of the treatment unit at the turbine housing. As an example, the treatment unit may include at least one catalyst. As an example, the turbine housing of the turbocharger may be integrally cast with a multi-cylinder exhaust manifold.

[0093] Although some examples of methods, apparatuses, systems, arrangements, etc. have been illustrated in the accompanying drawings and described in the foregoing detailed description, it will be understood that the disclosed exemplary embodiments are not limiting, but are capable of numerous rearrangements, modifications, and substitutions.

Claims

1. A turbine housing comprising: The bearing housing end (762) and the processing unit end (764). volute wall (770), which defines the volute; Walls (780, 880, 980) define at least a portion of the turbine impeller space, which defines the turbine impeller space axis and the turbine impeller space diameter D. s The wall (780) extends to the axial peak to define an extension space having an extension space outlet having an extension space outlet size D. e ;as well as An outlet wall (790) defines an outlet space having an end outlet of a processing unit having an outlet size D. out The extension space is at least partially axially disposed between the turbine impeller space and the outlet space to increase the uniformity of axial velocity at the end outlet of the processing unit. The wall (780) extends toward the end of the processing unit (764) to an axial peak (786), at which the wall extends axially away from the end of the processing unit (764) to an axial valley (788). Wherein, the wall (780) and the outlet wall (790) form a double wall at least in the axial position defined by the azimuth angle of the turbine housing; and Wherein, the extended space outlet size D e Larger than the turbine impeller spatial diameter D s 110% and less than the turbine impeller space diameter D s 200%, Wherein, the first axial distance (Δz) from the bottommost axial point of the wall to the axial peak e The second axial distance (Δz) is greater than the axial distance from the axial peak to the axial position at the end of the processing unit. f ),and Wherein, the outlet size D out Greater than the first axial distance (Δz) e ) and the second axial distance (Δz) f ) and.

2. The turbine housing according to claim 1, wherein, A portion of the wall (780, 880, 980) defining the extended space is arranged at an angle relative to the turbine impeller space axis, wherein the angle is greater than 0 degrees and less than 15 degrees.

3. The turbine housing according to claim 1, wherein, A portion of the wall (780, 880, 980) defining the extended space is arranged at an angle relative to the turbine impeller space axis, wherein the angle is greater than 5 degrees and less than 15 degrees.

4. The turbine housing according to claim 1, wherein, The turbine impeller space diameter D s The extended space outlet size D e <The outlet size D out .

5. The turbine housing according to claim 1, wherein, The axial distance from the axial peak to the end outlet of the processing unit is less than the turbine impeller space diameter D. s .

6. The turbine housing according to claim 1, wherein, The walls (780, 880, 980) descend from the axial peak to the axial valley.

7. The turbine housing according to claim 6, wherein, The walls (780, 880, 980) transition to the outlet wall (790) at the axial valley.

8. The turbine housing according to claim 6, wherein, The depth of the axial valley varies along the azimuth angle around the spatial axis of the turbine impeller.

9. The turbine housing according to claim 1, wherein, The end outlet of the processing unit defines an outlet axis offset from the spatial axis of the turbine impeller.

10. The turbine housing according to claim 9, wherein, The axial peak is a ring-shaped axial peak centered on the spatial axis of the turbine impeller.

11. The turbine housing of claim 1, comprising an insert that partially defines the turbine impeller space.

12. The turbine housing according to claim 11, wherein, The insert is a variable nozzle cylinder insert.

13. The turbine housing according to claim 1, comprising a multi-cylinder exhaust manifold.

14. The turbine housing according to claim 13, wherein, The multi-cylinder exhaust manifold is integrally cast with the turbine housing.

15. A turbocharger comprising: Bearing housing assembly; as well as A turbine housing assembly, wherein the turbine housing assembly includes: The bearing housing end (762) and the processing unit end (764). volute wall (770), which defines the volute; Walls (780, 880, 980) define at least a portion of the turbine impeller space, which defines the turbine impeller space axis and the turbine impeller space diameter D. s The wall (780) extends to the axial peak to define an extension space having an extension space outlet having an extension space outlet size D. e ,as well as An outlet wall (790) defines an outlet space having an end outlet of a processing unit having an outlet size D. out The extension space is at least partially axially disposed between the turbine impeller space and the outlet space to increase the uniformity of axial velocity at the end outlet of the processing unit. The wall (780) extends toward the end of the processing unit (764) to an axial peak (786), at which point the wall extends axially away from the end of the processing unit (764) to an axial valley (788), wherein the wall (780) and the outlet wall (790) form a double wall at least in the axial position defined by the azimuth angle of the turbine housing; and Wherein, the extended space outlet size D e Larger than the turbine impeller spatial diameter D s 110% and less than the turbine impeller space diameter D s 200%, Wherein, the first axial distance (Δz) from the bottommost axial point of the wall to the axial peak e The second axial distance (Δz) is greater than the axial distance from the axial peak to the axial position at the end of the processing unit. f ),and Wherein, the outlet size D out Greater than the first axial distance (Δz) e ) and the second axial distance (Δz) f ) and.

16. The turbocharger of claim 15, further comprising a processing unit.

17. The turbocharger according to claim 16, wherein, The processing unit is connected to the turbine housing to receive exhaust gas via the processing unit end outlet of the turbine housing.

18. The turbocharger according to claim 16, wherein, The processing unit includes at least one catalyst.

19. The turbocharger according to claim 15, wherein, The turbine housing is integrally cast with the multi-cylinder exhaust manifold.

Images