System and method for a variable inlet device for a compressor

Abstract

The present application provides methods and systems for a variable inlet device for a compressor. In one example, the compressor may include an impeller rotatable about a central axis and an inlet duct, the inlet duct including a variable inlet device (VID) positioned upstream of the impeller and adjustable between an open position and a closed position for restricting and generating pre-swirl flow to the impeller. The VID may include a plurality of adjacent vanes arranged in a ring around the central axis, wherein inner surfaces of the vanes form a flow path through the VID, and each of the vanes may pivot about an axis arranged tangentially to the ring between an open position and a closed position.

Description

Technical Field

[0001] The present description generally relates to methods and systems for variable inlet devices for compressors, and controlling the variable inlet devices to regulate airflow into the compressor. Background Art

[0002] A turbocharger may be provided in an engine to increase engine torque or power output density. A turbocharger may include an exhaust-driven turbine coupled to a compressor via a drive shaft. The compressor may be fluidically coupled to an intake manifold in the engine, which is connected to a plurality of engine cylinders. Exhaust flow from one or more engine cylinders may be directed to a turbine wheel, causing the turbine to rotate about a fixed axis. The rotational motion of the turbine drives an impeller (e.g., an impeller) of the compressor, which compresses air into the intake manifold to increase boost pressure based on engine operating conditions.

[0003] Compressor efficiency impacts overall engine performance and fuel consumption. For example, lower compressor efficiency can lead to slower engine transient response and higher fuel consumption during both steady-state and transient engine operation. At lighter engine loads, when compressor efficiency decreases, this can result in increased turbocharger lag during a tip-in. Additionally, light-load operation can result in lower compressor efficiency, and the compressor surge limit can limit boost pressure rise at low engine speeds.

[0004] Other attempts to address low compressor efficiency include utilizing a variable inlet compressor, which utilizes guide vanes to guide and regulate the flow through the impeller of the compressor. An example method is shown in EP2024645 by Sconfietti et al. Therein, a variable inlet device is disclosed that is disposed adjacent to the compressor inlet and includes a plurality of vanes. Each of the vanes is movable between a first position and a second position to control the amount of fluid delivered to the impeller. Specifically, the vanes are positioned around the center of the impeller device and pivot around an axis parallel to the central axis of the compressor. In the closed position, flow is prevented from being delivered to the impeller, and in the open position, gas can flow between adjacent blades around the center of the impeller device.

[0005] However, the inventors herein have recognized potential issues with this type of system. As an example, even in the open position, flow through the variable inlet device and to the impeller is restricted (e.g., partially blocked) due to the orientation and pivoting direction of the vanes. As a result, this type of variable inlet has reduced high-end efficiency and constrains high-end flow due to flow restriction issues. Furthermore, this type of device does not generate pre-swirl flow in the compressor, which can increase low-end efficiency. Summary of the Invention

[0006] In one example, the aforementioned problem is addressed by a compressor comprising: an impeller rotatable about a central axis; and an inlet duct including a variable inlet device (VID) positioned therein upstream of the impeller and comprising a plurality of adjacent vanes arranged in a ring around the central axis, wherein the inner surfaces of the vanes define a flow path through the VID, and each vane is pivotable about an axis arranged tangentially to the ring between an open position and a closed position. In the open position, the vanes may have little overlap with each other, and the inner surfaces define a wider flow path with reduced flow restriction. In the closed position, the vanes may have increased overlap at the outlet end of the VID, thereby restricting flow as it passes through the flow path of the VID. Furthermore, the overlap of the vanes creates a smooth surface with spiral grooves that generate pre-swirl to the impeller as intake air flows through the flow path of the VID. As a result, compressor efficiency increases in the closed position due to the restricted pre-swirl generated by the VID. When the VID is in the open position, compressor efficiency further increases at higher loads due to reduced flow restriction through the inlet duct and the VID. In this way, compressor efficiency and overall engine performance and fuel economy may be increased over a wide range of engine operating speeds and loads.

[0007] It should be understood that the above summary is provided to introduce in a simplified form selected concepts that are further described in the detailed description. It is not meant to identify key or essential features of the claimed subject matter, the scope of which is defined solely by the appended claims. Furthermore, the claimed subject matter is not limited to implementations that solve any disadvantages noted above or in any part of this disclosure. BRIEF DESCRIPTION OF THE DRAWINGS

[0008] Figure 1 A schematic depiction of an example vehicle system is shown.

[0009] Figures 2A to 2C A first embodiment and a second embodiment of a turbocharger compressor are shown that include a variable inlet device positioned in an inlet duct of the compressor.

[0010] Figures 3A to 3D An embodiment of a variable inlet device for a turbocharger compressor is shown in an open position and a closed position.

[0011] Figures 4A to 4B A cross-sectional view of a third embodiment of a turbocharger compressor is shown including a case treatment and a variable inlet device positioned in the inlet duct of the compressor.

[0012] Figures 5A to 5B A cross-sectional view of a fourth embodiment of a turbocharger compressor is shown including active case treatment and a variable inlet device positioned in the inlet duct of the compressor.

[0013] Figure 6 A flow chart illustrating a method for controlling the position of a variable inlet device.

[0014] Figure 7 An engine load and engine speed map is shown for controlling the position of a variable inlet device.

[0015] Figure 8 A flow chart illustrating a method for coordinating position control of a variable inlet device and active case processing of a compressor.

[0016] Figure 9 A graph showing engine load and engine speed processed by an active case for controlling the position of a variable inlet device and a compressor is shown.

[0017] Figures 2A to 3B and Figures 4A to 5B Shown approximately to scale. DETAILED DESCRIPTION

[0018] The following description relates to systems and methods for variable inlet devices for turbocharger compressors. Figure 1 The compressor of the engine system shown in FIG) can be positioned in the intake passage of the engine. The compressor can include an outer casing having an inlet duct (e.g., the intake passage) and a pump wheel (e.g., a compressor impeller) disposed downstream in the inlet duct. The pump wheel can include one or more blades and can rotate about a central axis of the compressor. Figures 2A to 2C As shown, a variable inlet device (VID) may be provided in the inlet duct of the compressor upstream of the impeller. The VID may be in an open position (e.g. Figure 2A 、 Figure 2C 、 Figure 3A 、 Figure 3C 、 Figure 4B and Figure 5B shown) and closed position (as Figure 2B 、 Figure 3B 、 Figure 3D 、 Figure 4A and Figure 5A Adjustable between Figure 2C A passive method of activating a VID is shown in FIG. Figure 3A and Figure 3BAs shown, the VID includes a plurality of adjacent vanes arranged in a ring around the central axis of the compressor. The vanes are pivotable toward and away from the central axis between an open position and a closed position. When the VID is in the open position, the inner surfaces of the vanes of the VID restrict the flow through the VID and the inlet duct to a lesser extent than when the VID is in the closed position. For example, Figure 3C As shown, in the open position, reducing the VID limits the amount of flow from the inlet end to the outlet end. Figure 3D As shown, when the VID is in the closed position, the vanes pivot so that the flow path of the VID formed by the inner surface of the vanes narrows from the inlet end to the outlet end. In addition, in the closed position, the inner surface forms a smooth surface with spiral grooves, which generate swirl due to the overlap of the vanes at the outlet end. Figures 4A to 4B As shown, the VID can also be used in conjunction with a compressor having a case treatment that includes a resonant chamber for recirculating flow from the impeller to the inlet duct upstream of the VID. Figures 5A to 5B As shown, the VID may be used in conjunction with a compressor having active case processing adapted to regulate the recirculation flow between the recirculation port and one of the discharge port and the injection port provided in the wall of the inlet duct. Figures 6 and 7 As shown, the position of the VID can be controlled based on engine load and engine speed conditions relative to the surge threshold. In embodiments of the VID used in conjunction with active case processing, the position of the VID and the active case processing can be controlled in coordination with each other based on engine load and engine speed conditions relative to the surge threshold and the choke threshold, such as Figures 8 and 9 As depicted in . In this way, the VID of the compressor can be used to improve compressor efficiency under different operating conditions, such as lighter load conditions. The arrangement of the VID can reduce unwanted flow restriction in the open position and generate smooth pre-swirl flow to the compressor impeller in the closed position, thereby improving the low-end efficiency and flow rate of the compressor.

[0019] Now turning to the accompanying drawings, Figure 1An example embodiment of cylinder 14 of internal combustion engine 10 is depicted, which may be included in vehicle 5. Engine 10 may be controlled at least partially by a control system including controller 12 and by input from a vehicle operator 130 via an input device 132. In this example, input device 132 includes an accelerator pedal and a pedal position sensor 134 for generating a proportional pedal position signal PP. Cylinder 14 of engine 10 (also referred to herein as a "combustion chamber") may include combustion chamber walls 136 with a piston 138 positioned therein. Piston 138 may be coupled to a crankshaft 140 such that reciprocating motion of the piston is translated into rotational motion of the crankshaft. Crankshaft 140 may be coupled to at least one drive wheel 55 of the passenger vehicle via a transmission 54, as described further below. Additionally, a starter motor (not shown) may be coupled to crankshaft 140 via a flywheel to enable a starting operation of engine 10.

[0020] In some examples, vehicle 5 may be a hybrid vehicle having multiple torque sources available for one or more wheels 55. In other examples, vehicle 5 is a conventional vehicle having only an engine or an electric vehicle having only one or more motors. In the example shown, vehicle 5 includes engine 10 and motor 52. Motor 52 may be a motor or a motor / generator. When one or more clutches 56 are engaged, crankshaft 140 of engine 10 and motor 52 are connected to wheels 55 via transmission 54. In the depicted example, a first clutch 56 is disposed between crankshaft 140 and motor 52, and a second clutch 56 is disposed between motor 52 and transmission 54. Controller 12 may send signals to the actuators of each clutch 56 to engage or disengage the clutches, thereby connecting or disconnecting crankshaft 140 from motor 52 and components connected thereto, and / or connecting or disconnecting motor 52 from transmission 54 and components connected thereto. Transmission 54 may be a gearbox, a planetary gear system, or another type of transmission. The powertrain can be configured in various ways, including parallel, series, or series-parallel hybrid vehicles.

[0021] The electric motor 52 receives power from the traction battery 58 to provide torque to the wheels 55. The electric motor 52 may also operate as a generator to provide power to the rechargeable battery 58, for example, during braking operations.

[0022] Cylinder 14 of engine 10 can receive intake air via a series of intake passages 142, 144, and 146. Intake passage 146 can also communicate with other cylinders of engine 10 in addition to cylinder 14. In some examples, one or more of the intake passages may include a boosting device, such as a turbocharger or a supercharger. For example, Figure 1Engine 10 is shown configured with a turbocharger including a compressor 174 arranged between intake passages 142 and 144, and an exhaust turbine 176 arranged along exhaust passage 148. When the boosting device is configured as a turbocharger, compressor 174 may be at least partially powered by exhaust turbine 176 via shaft 180. However, in other examples, such as when engine 10 is provided with a supercharger, compressor 174 may be powered by mechanical input from a motor or the engine, and exhaust turbine 176 may optionally be omitted.

[0023] A throttle 162 including a throttle plate 164 may be provided in the engine intake passage for varying the flow rate and / or pressure of intake air provided to the engine cylinders. Figure 1 As shown, throttle 162 may be positioned downstream of compressor 174 , or may alternatively be provided upstream of compressor 174 .

[0024] Exhaust passage 148 can also receive exhaust gas from other cylinders of engine 10 in addition to cylinder 14. Exhaust gas sensor 128 is shown coupled to exhaust passage 148 upstream of emission control device 178. Exhaust gas sensor 128 may be selected from various suitable sensors for providing an indication of exhaust air-fuel ratio (AFR), such as a linear oxygen sensor or UEGO (Universal or Wide Range Exhaust Gas Oxygen), a two-state oxygen sensor or EGO (as depicted), a HEGO (Heated EGO), a NOx, HC, or CO sensor, for example. Emission control device 178 may be a three-way catalyst (TWC), a NOx trap, various other emission control devices, or combinations thereof.

[0025] Each cylinder of engine 10 may include one or more intake valves and one or more exhaust valves. For example, cylinder 14 is shown including at least one intake poppet valve 150 and at least one exhaust poppet valve 156 located at an upper region of cylinder 14. In some embodiments, each cylinder of engine 10, including cylinder 14, may include at least two intake poppet valves and at least two exhaust poppet valves located at an upper region of the cylinder. Intake valve 150 may be controlled by controller 12 via actuator 152. Similarly, exhaust valve 156 may be controlled by controller 12 via actuator 154. The positions of intake valve 150 and exhaust valve 156 may be determined by respective valve position sensors (not shown).

[0026] In some cases, controller 12 may vary the signals provided to actuators 152 and 154 to control the opening and closing of the corresponding intake and exhaust valves. The valve actuators may be electric valve actuation, cam actuation, or a combination thereof. Intake and exhaust valve timing may be controlled simultaneously, or any of variable intake cam timing, variable exhaust cam timing, dual independent variable cam timing, or fixed cam timing may be used. Each cam actuation system may include one or more cams and may utilize one or more of a cam profile switching system (CPS), variable cam timing (VCT), variable valve timing (VVT), and / or variable valve lift (VVL) system operable by controller 12 to vary valve operation. For example, cylinder 14 may alternatively include an intake valve controlled via electric valve actuation and an exhaust valve controlled via cam actuation including CPS and / or VCT. In other embodiments, the intake and exhaust valves may be controlled by a common valve actuator (or actuation system) or a variable valve timing actuator (or actuation system).

[0027] Cylinder 14 can have a compression ratio, which is the ratio of volume when piston 138 is at bottom dead center (BDC) to volume when piston 138 is at top dead center (TDC). In one example, this compression ratio is in the range of 9:1 to 10:1. However, in some examples using different fuels, the compression ratio may be increased. This may occur, for example, when using a higher octane fuel or a fuel with a higher latent enthalpy of vaporization. If direct injection is used, the compression ratio may also be increased due to its effect on engine knock.

[0028] In some examples, each cylinder of engine 10 may include a spark plug 192 for initiating combustion. In select operating modes, ignition system 190 can provide an ignition spark to combustion chamber 14 via spark plug 192 in response to spark advance signal SA from controller 12. The timing of signal SA can be adjusted based on engine operating conditions and driver torque demand. For example, the spark can be provided at maximum brake torque (MBT) timing to maximize engine power and efficiency. Controller 12 can input engine operating conditions, including engine speed, engine load, and exhaust gas ignition frequency (AFR), into a lookup table and output a corresponding MBT timing for the input engine operating conditions.

[0029] In some examples, each cylinder of engine 10 may be configured with one or more fuel injectors for providing fuel to the cylinder. As a non-limiting example, cylinder 14 is shown including fuel injector 166. Fuel injector 166 may be configured to deliver fuel received from fuel system 8. Fuel system 8 may include one or more fuel tanks, fuel pumps, and a fuel rail. Fuel injector 166 is shown directly coupled to cylinder 14 for injecting fuel directly into the cylinder in proportion to the pulse width of signal FPW received from controller 12 via electronic driver 168. In this manner, fuel injector 166 provides what is known as direct injection (hereinafter also referred to as "DI") of fuel into cylinder 14. Although Figure 1 Fuel injector 166 is shown positioned to the side of cylinder 14, but may alternatively be located on the piston crown, such as near spark plug 192. Due to the lower volatility of some alcohol-based fuels, such a location may improve mixing and combustion when the engine is operated on alcohol-based fuels. Alternatively, the injector may be located on top of and near the intake valve to improve mixing. Fuel may be delivered to fuel injector 166 from a fuel tank of fuel system 8 via a high-pressure fuel pump and a fuel rail. The fuel tank may also have a pressure sensor that provides a signal to controller 12.

[0030] In an alternative example, fuel injector 166 may be arranged in intake passage 146 rather than being directly coupled to cylinder 14 in a configuration that provides so-called port injection (hereinafter also referred to as "PFI") of fuel into the intake port upstream of cylinder 14. In other examples, cylinder 14 may include multiple injectors that may be configured as direct fuel injectors, port fuel injectors, or a combination thereof. Thus, it should be understood that the fuel system described herein should not be limited to the specific fuel injector configurations described herein by way of example.

[0031] Fuel injector 166 can be configured to receive different fuels from fuel system 8 in varying relative amounts as a fuel mixture, and further configured to inject this fuel mixture directly into the cylinder. Furthermore, fuel can be delivered to cylinder 14 during different strokes of a single cylinder cycle. For example, directly injected fuel can be at least partially delivered during the preceding exhaust stroke, during the intake stroke, and / or during the compression stroke. Thus, for a single combustion event, one or more injections of fuel can be performed per cycle. Multiple injections can be performed during the compression stroke, the intake stroke, or any suitable combination thereof, in what is known as split fuel injection.

[0032] The fuel tank in the fuel system 8 can accommodate the fuel of different fuel types, such as the fuel with different fuel qualities and different fuel compositions.Difference can comprise different alcohol contents, different water contents, different octane numbers, different heats of vaporization, different fuel blends and / or their combination etc.An example of fuel with different heats of vaporization comprises gasoline as the first fuel type with lower heat of vaporization and alcohol as the second fuel type with larger heat of vaporization.In another example, the engine can use gasoline as the first fuel type, and the fuel blend containing alcohol such as E85 (E85 is about 85% ethanol and 15% gasoline) or M85 (M85 is about 85% methanol and 15% gasoline) as the second fuel type.Other feasible materials comprise the mixture of water, methanol, alcohol and water, the mixture of water and methanol, the mixture of alcohols etc. In yet another example, both fuels may be alcohol blends having different alcohol components, where the first fuel type may be a gasoline alcohol blend with a lower alcohol concentration, such as E10 (which is approximately 10% ethanol), while the second fuel type may be a gasoline alcohol blend with a higher alcohol concentration, such as E85 (which is approximately 85% ethanol). Furthermore, the first and second fuels may differ in other fuel quality aspects, such as temperature, viscosity, octane rating, etc. Furthermore, the fuel characteristics of one or both fuel tanks may vary frequently, for example, due to daily variations in fuel tank refilling.

[0033] The controller 12 Figure 11 is a microcomputer that includes a microprocessor unit (CPU) 106, input / output ports (I / O) 108, an electronic storage medium for executable programs (e.g., executable instructions) and calibration values, shown in this particular example as a non-transitory read-only memory chip (ROM) 110, a random access memory (RAM) 112, a keep alive memory (KAM) 114, and a data bus. Controller 12 may receive various signals from sensors coupled to engine 10, including, in addition to those previously discussed, a measurement of intake mass airflow (MAF) from mass airflow sensor 122; engine coolant temperature (ECT) from temperature sensor 116 coupled to cooling sleeve 118; exhaust temperature from temperature sensor 158 coupled to exhaust passage 148; a surface ignition probe (PIP) signal from Hall effect sensor 120 (or other type) coupled to crankshaft 140; throttle position (TP) from a throttle position sensor; a signal EGO from exhaust gas sensor 128, which may be used by controller 12 to determine exhaust gas AFR; and a manifold pressure absolute (MAP) signal from MAP sensor 124. Engine speed signal RPM may be generated by controller 12 from signal PIP. Manifold pressure signal MAP from MAP sensor 124 may be used to provide an indication of vacuum or pressure in the intake manifold. Controller 12 may infer engine temperature based on the engine coolant temperature and infer catalyst 178 temperature based on signals received from temperature sensor 158.

[0034] The controller 12 receives the Figure 1 The signals of various sensors are used Figure 1 The engine controller may control various actuators to adjust engine operation based on received signals and instructions stored in the controller's memory. For example, upon receiving signals from various sensors, the engine controller may send control signals to actuators to change the position of a variable inlet device (VID) of the compressor 174 and / or send control signals to actuators of active casing treatments (such as slidable sleeves) disposed along the inlet duct of the compressor 174 (as described below with reference to FIG. Figure 6 and Figure 8 For example, the controller may send an electronic signal to an actuator of the VID to adjust the VID from an open position to a closed position or vice versa in response to the current engine speed and engine load relative to a surge threshold and / or a choke threshold of the compressor.

[0035] As mentioned above, Figure 1Only one cylinder of a multi-cylinder engine is shown. Thus, each cylinder may similarly include its own set of intake / exhaust valves, (one or more) fuel injectors, spark plugs, etc. It should be appreciated that engine 10 may include any suitable number of cylinders, including 2, 3, 4, 5, 6, 8, 10, 12, or more cylinders. Furthermore, each of these cylinders may include a reference cylinder 14 represented by Figure 1 Some or all of the various components described and depicted.

[0036] Figures 2A to 2B A cutaway view (eg, a cross-sectional view) of a first embodiment of a turbocharger compressor 202 is shown that includes a variable inlet device (VID) 204 positioned in an inlet duct 206 of the compressor 202. In one embodiment, the compressor 202 may be Figure 1 Compressor 174 in. Figure 2C A second embodiment of a VID 204 positioned in the inlet duct 206 of a compressor 202 is shown, wherein the compressor 202 includes an additional passage 226 disposed in the inlet duct 206 upstream of the impeller 208 and downstream of the inlet end of the VID 204, as further explained below. The compressor 202 includes the inlet duct 206, the impeller 208, a volute 216, a diffuser 218, and a casing 220. The elements of the compressor 202 can be described in terms of the direction of airflow 203 through the compressor 202, with any element in the airflow path relative to a reference point being considered downstream of the reference point. Conversely, any element positioned in the opposite direction of airflow relative to the reference point is considered upstream of the reference point. Additionally, the compressor 202 includes a central axis 205, which is the central axis of the inlet duct 206 and the central rotational axis of the impeller 208 (e.g., the impeller can rotate about the central axis 205).

[0037] Airflow (e.g., intake air from an intake passage, such as Figure 1 The intake passage 142) 203 shown in FIG enters the inlet duct 206 and flows through the VID 204 located upstream of the impeller 208. The VID 204 includes a plurality of blades 207 arranged adjacent to each other in a ring configuration around a central axis 205. Figures 3A to 3DThe configuration of VID 204 is further described. VID 204 is positioned so that the central axis of the ring of blades 207 is perpendicular to the wall of the inlet duct 206 and co-linear with the central axis 205 of the compressor 202. The impeller 208 includes a plurality of impeller blades 210 attached to a hub 212. Hub 212 is connected to a rotatable shaft 214, which is aligned parallel to the direction of airflow and the central axis 205 and is connected to the turbine wheel (which drives the shaft and the rotation of the impeller 208). The rotation of the impeller 208 draws gas through the inlet duct 206 of the casing 220 and then into the compressor 202 through VID 204. From VID 204, the gas travels to the impeller 208 and enters the diffuser 218. The gas is accelerated through the diffuser 218 and enters the volute 216, causing the airflow to decelerate and the pressure in the volute 216 to increase. The high pressure in the volute 216 can cause the gas to flow to the intake manifold.

[0038] like Figures 2A to 2C As shown, the VID 204 spans the entire inlet duct 206. Specifically, the ends of the blades 207 of the VID 204 are positioned proximate to the inner wall 219 of the casing 220. In addition, the entire VID 204 is positioned upstream of the entire impeller 208, including upstream of the leading edges of the impeller blades 210. Figures 2A to 2B As shown, with the controller 211 (which can be Figure 1 2. An actuator 209 is mechanically coupled to the VID 204 in electronic communication with a controller 12 (same or similar to that shown in FIG. 1 ). The actuator 209 is adapted to pivot the vanes 207 of the VID 204 between an open position and a closed position based on one or more electronic signals received from the controller 211. In one example, the actuator can be a motor coupled to the inlet end of the VID 204. Figure 2A A first schematic diagram 200 shows a compressor 202 with a VID 204 in an open position, wherein the outlet vane end 222 of the vane 207 is positioned proximate to the inner wall 219 of the inlet duct 206, with the outlet vane end 222 of the vane 207 positioned furthest downstream in the inlet duct 206 relative to the inlet vane end 224 of the vane 207. In one example, the outlet vane end 222 may contact the inner wall 219 (e.g., in coplanar contact with the inner wall 219). In the open position, the diameter of the annulus formed by the outlet vane end 222 may be equal to or greater than the diameter of the annulus formed by the inlet vane end 224. In the open position, the inner wall of the vane 207 creates little flow restriction through the VID 204, and therefore, creates little flow restriction through the inlet duct 206. Figure 2BA second schematic diagram 201 of a compressor 202 is shown with a VID 204 in a closed position, wherein the inlet vane end 224 is disposed proximate to the inner wall 219 of the inlet duct 206. In one example, the inlet vane end 224 may contact the inner wall 219 (e.g., in coplanar contact with the inner wall 219). In the closed position, the diameter of the ring formed by the outlet vane end 222 is narrower than the diameter of the ring formed by the inlet vane end 224. Thus, when the VID is in Figure 2B In the closed position shown, airflow through the VID 204 and inlet duct 206 (and to the impeller 208 ) is restricted by the inner surfaces of the vanes 207 .

[0039] Figure 2C A third schematic diagram 221 of the compressor 202 is shown illustrating a passive actuation mechanism for adjusting the VID 204 between an open position and a closed position. Specifically, the casing 220 includes an additional passage 226 formed in the inlet duct 206 upstream of the impeller 208 and downstream of the inlet end of the VID 204. Figure 2C As shown, the passage 226 may extend outward from the central axis 205 such that the inner wall 219 in the region of the passage 226 is positioned further away from the central axis 205 than the inner wall 219 in the region of the inlet duct 206 disposed upstream of the inlet end of the VID 204. During certain operating conditions, airflow is recirculated from the impeller 208 to the VID 204 via the passage 226 in a direction opposite to the airflow 203 into the inlet duct 206, as indicated at arrow 213. This recirculated airflow via the passage 226 causes the outer faces of the vanes 207 at the outlet end of the VID 204 (e.g., the surface facing the inner wall 219 of the inlet duct 206) to experience a higher pressure than the inner faces of the vanes 207 due to the airflow 203. As a result, the VID 204 is passively actuated from the open position to the closed position (e.g., via the pressure differential). Figure 2C 204 ). One example of such a pressure differential may occur during a surge condition, where the pressure at the outlet end of compressor 202 increases and initiates a reversal of airflow 203 via passage 226. The increased pressure on the outer face of vane 207 at the outlet end of VID 204 enables vane 207 to pivot toward the central axis of rotation 205 at the outlet end of VID 204, thereby moving VID 204 to the closed position. Under conditions where the pressure on the outer face of vane 207 is equal to or less than the pressure on the inner face of vane 207, VID 204 is adjusted to (or maintained in) the open position.

[0040] Figures 3A to 3D Details of a variable entry device (VID) 300 are shown, which can be used as Figures 2A to 2B 、 Figures 4A to 4B as well as Figures 5A to 5BIn one of the variable inlet devices 204, 404 and 540 shown in FIG. Figure 3A A side view of the VID 300 is shown in the open position, Figure 3B A side view of the VID 300 is shown in the closed position, Figure 3C A front view of the VID 300 is shown in the open position, and Figure 3D A front view of the VID 300 is shown in the closed position.

[0041] like Figures 3A to 3D As shown, the VID 300 includes a plurality of blades 306 arranged adjacently to form a ring around a central axis 301 of the VID 300, which may be collinear with a central axis of the compressor, as shown. Figures 2A to 2B 、 Figures 4A to 4B as well as Figures 5A to 5B As shown. VID 300 has an inlet end formed by inlet ends (e.g., inlet blade edges) 304 of blades 306, which form a first ring having a first diameter 303. VID 300 also has an outlet end formed by outlet ends (e.g., outlet blade edges) 302 of blades 306, which form a second ring having a second diameter 305. When VID 300 is positioned in a flow path, such as Figures 2A to 2B 、 Figures 4A to 4B as well as Figures 5A to 5B , the inlet end 304 is arranged upstream of the outlet end 302. Each vane 306 has an outer surface 307 and an inner surface 309, wherein the inner surfaces 309 of all vanes 306 form a flow passage 311 through the VID 300. In this manner, flow through a passage (such as a passage) in which the VID 300 is located is Figures 2A to 2B 、 Figures 4A to 4B as well as Figures 5A to 5B Gas (e.g., intake air) entering the VID 300 via an inlet duct or intake passage shown in FIG. 3 contacts the inner surface 309 and passes through the VID 300 via flow passage 311. The direction of airflow through the VID 300 is shown by arrows 313. Figures 3C to 3D , the direction of airflow through the VID 300 is shown. The open and closed positions of the VID 300 are achieved by pivoting the vanes 306 toward and away from the central axis 301 at pivot axes 329 arranged tangentially to the inlet ring and perpendicular to the central axis 301, as further explained below.

[0042] Figure 3A A side view of the VID 300 is shown in an open position, wherein the second diameter 305 may be equal to (eg Figure 3A ) or greater than the first diameter 303. Thus, flow through the VID 300 is not restricted from the inlet end to the outlet end. Figure 3C , a front view of the VID 300 taken from the inlet end 304 of the blade 306 is shown in the open position. Figure 3C As shown, the first diameter 303 and the second diameter 305 are equal. Therefore, in the open position, the blades 306 are relatively straight from the inlet end 304 to the outlet end 302 and are arranged approximately parallel to the central axis. Each blade 306 has a pivot axis 329 about which the inlet end of each blade pivots between the open position and the closed position. Figure 3C As shown, the inlet end of each blade 306 includes a hinge element 331 disposed at the pivot axis 329. As such, the hinge element 331 can allow each blade 306 to pivot between an open position and a closed position. In one example, the hinge element 331 can be a torsion spring positioned approximately tangentially to the inlet ring of the VID 300 and centered within the thickness 333 of the blade 306. Figure 3C As shown, the cross-sectional area of the blade 306 is compared to the cross-sectional area in the closed position (as shown below in Figure 3B and Figure 3D 306 are small (as further discussed and shown in FIG. 306 ) and are small compared to the cross-sectional area of a device having blades or vanes oriented from a central axis of the device to an outer periphery of the device. Due to the positioning of vanes 306 in the open position, flow restriction through VID 300 and to the impeller in the open position can be reduced (e.g., minimized).

[0043] Likewise Figure 3A and Figure 3C , each vane 306 includes a side surface extending between the inlet end 304 and the outlet end 302. For example, a first vane 315 has a first side surface 317 that contacts a side surface 319 of an adjacent second vane 321. The first vane 315 has a second side surface 323 that contacts a side surface 325 of an adjacent third vane 327. In the open position, the side surfaces (e.g., inner surfaces) of the vanes 306 contact each other, but they may not overlap. Figure 3B A side view (eg, a profile view) of the VID 300 is shown in the closed position. Figure 3D A front view of the VID 300 is shown in the closed position (seen from the inlet end). To move from the open position to the closed position, the outlet end 302 of the vane 306 is pivoted toward the central axis 301 via a pivot axis 329 disposed at the inlet end of the vane 306. As a result, the second diameter 305 is reduced and the first diameter remains the same as when the VID 300 is in the open position. In the closed position, as shown Figure 3B and Figure 3DAs shown, the second diameter 305 is smaller than the first diameter 303. Specifically, the second diameter 305 is smaller than the first diameter 303 by a first amount (e.g., the difference between the first diameter 303 and the second diameter 305 is the first amount in the closed position). In the closed position, the vanes 306 are angled inwardly toward the central axis 301 from the inlet end 304 to the outlet end 302. In the closed configuration, because the diameter of the flow passage 311 of the VID 300 gradually decreases from the inlet end 304 to the outlet end 302 (e.g., as the flow through the flow passage 311 travels downstream), the inner surface 309 of the vanes 306 restricts the flow from the inlet end 304 to the outlet end 302. The inner surface 309 has a relatively smooth surface for directing the flow from the inlet end 304 to the outlet end 302. As shown in FIG. Figure 3B As shown in FIG, the outlet ends 302 of the blades 306 overlap one another (e.g., each blade overlaps an adjacent blade and is overlapped by another adjacent blade). However, the inlet ends 304 of the blades 306 may not overlap or may overlap less than the outlet ends 302 in the closed position. The overlapping arrangement of the blades at the outlet ends 302 in the closed position provides a smooth inner surface having a spiral groove 308, as shown in FIG. Figure 3D As shown in FIG, the airflow is caused to swirl when passing through the VID 300. Specifically, as Figure 3D As shown in FIG, each blade 306 is separated from an adjacent blade 306 by a spiral groove 308. The spiral groove 308 is curved relative to the central axis 301. In one example, the curvature of the spiral groove 308 is biased to direct flow in the same rotational direction as the rotation of the compressor's impeller. For example, Figure 3B and Figure 3D The blades 306 in the compressor overlap to produce a spiral groove, which, when installed upstream of the impeller in the compressor inlet duct (e.g. Figures 2A to 2B 、 Figures 4A to 4B as well as Figures 5A to 5B The spiral groove causes the gas to swirl counterclockwise relative to the central axis 301, which can be collinear with the central rotation axis of the compressor impeller. The swirled gas can then flow from the outlet end of the VID 300 to the impeller, which also rotates counterclockwise.

[0044] Figures 4A to 4B A cross-sectional view of a third embodiment of a turbocharger compressor 402 is shown, the compressor 402 including a case treatment 416 and a VID 404 (such as a compressor inlet) positioned in an inlet duct 406 of the compressor 402 (also described herein as a compressor inlet). Figures 3A to 3D In one embodiment, the compressor 402 may be Figure 1174 of compressor 402. Compressor 402 includes an inlet duct 406, an impeller 408, a diffuser 410, a volute 412, a casing 414, and a casing treatment 416. The elements of compressor 402 can be described in the direction of airflow, and any element in the airflow path relative to a reference point is considered to be downstream of the reference point. Conversely, any element positioned in the opposite direction of the airflow relative to the reference point is upstream of the reference point. The airflow direction is parallel to the central rotational axis 403 of the impeller 408 and is shown by arrow 405. The central rotational axis of the impeller 408 will be referred to herein as the central axis of the compressor. The central rotational axis of the compressor 402 may also be the central axis of the inlet duct 406 and the central axis of the VID 404, as further described above and below.

[0045] The compressor 402 is rotatably coupled to a shaft that is connected to a turbine (such as Figure 1 180 and 176 in FIG), which is arranged parallel to the central axis of rotation and transmits energy to the impeller 408. The impeller 408 may also be referred to herein as the compressor impeller. The rotation of the impeller 408 draws gas into the compressor 402 through the intake duct 406 of the casing 414. The gas flows through the VID 404 and flows to the impeller 408. The gas is then accelerated by the impeller 408 through the diffuser 410 and into the volute 412. The flow through the diffuser 410 and into the volute 412 is decelerated, resulting in an increase in pressure. The pressurized gas can then flow from the volute 412 to the intake manifold.

[0046] The impeller 408 includes a plurality of blades 418, a hub 420, and has a central rotational axis 403 arranged parallel to the direction of flow through the inlet duct 406. The casing treatment 416 includes a recirculation passage (also referred to as a resonance chamber) 424, an exhaust port 422, an actuation port 423, and a recirculation port 430. The actuation port 423 is formed in the inner wall 425 of the inlet duct 406 and fluidically couples the recirculation passage to the inlet duct 406 at a location directly adjacent to the plurality of blades 407 of the VID 404. More specifically, the actuation port 423 is positioned between the inlet (e.g., upstream) end and the outlet (e.g., downstream) end of the VID 404. Furthermore, the actuation port 423 is positioned in the recirculation passage 424 between the exhaust port 422 and the recirculation port 430.

[0047] The recirculation passage 424 is formed by the casing (e.g., outer casing) 414 of the compressor 402 and surrounds the inlet duct 406. Therefore, the recirculation passage 424 can be an annular passage surrounding the inlet duct 406 and arranged parallel to the inlet duct 406. The recirculation passage 424 is separated from the inlet duct 406 by the inner wall 425 of the casing 414, which is the wall forming the inlet duct 406. In addition, the recirculation passage 424 is fluidically coupled to the inlet duct 406 via the discharge port 422 and the recirculation port 430. The discharge port 422 is formed in the inner wall 425 downstream of the leading edge of the impeller 408 and upstream of the diffuser 410. In one example, the discharge port 422 is a narrow slot located in and through the inner wall 425. The inlet of the discharge port 422 can be arranged directly adjacent to the impeller blades 418. The discharge port 422 is the entrance to the recirculation passage 424. The recirculation passage 424 is adjacent to a recirculation port 430 formed in a wall 425 upstream of the inlet end of the VID 404. The recirculation port 430 is configured to enable gas to flow between the inlet duct 406 and the recirculation passage 424. The discharge port 422, the actuation port 423, the recirculation passage 424, and the recirculation port 430 relieve pressure buildup downstream of the impeller 408. This can reduce surge conditions and extend the surge margin of the compressor 402 by circulating air back to the compressor inlet 406.

[0048] like Figures 4A to 4B As shown, the VID 404 is arranged in the inlet duct 406 upstream of the leading edge of the impeller 408 and downstream of the location where the recirculation port 430 is coupled to the inlet duct 406. The VID 404 includes a plurality of blades 407 arranged adjacent to each other in a ring configuration around the central axis 403. The configuration of the VID 404 is shown in FIG. Figures 3A to 3D As described in detail above. Figures 4A to 4B As shown, VID 404 spans the entire inlet duct 406. Specifically, the ends of blades 407 of VID 404 are positioned proximate to the inner wall 425 of casing 414. Additionally, the entire VID 404 is positioned upstream of the entire impeller 408, including the leading edges of impeller blades 418.

[0049] Figure 4A Shown with the Figure 3B and Figure 3D300 (shown in the closed position of VID 300), wherein the outlet vane end 426 of the vane 407 (which is arranged most downstream in the inlet duct 406 relative to the inlet vane end 428 of the vane 407) is pivoted inwardly toward the central axis 403, and the inlet vane end 428 is arranged adjacent to the inner wall 425 of the inlet duct 406. In one example, the actuation port 423 can allow recirculated gas to pass through the recirculation passage 424 to utilize the same method as described above. Figure 2C A similar approach is described for VID 404. Under conditions where the pressure at impeller blades 418 and in recirculation passage 424 is higher than the pressure in inlet duct 406 upstream of VID 404, recirculation flow increases through recirculation passage 424 (as indicated by arrow 431) in a direction opposite to airflow 405. The airflow also follows the path indicated by arrow 429, thereby exerting a greater pressure on the outer surfaces of vanes 407 of VID 404 (e.g., surfaces facing inner wall 425) than the pressure experienced by the inner surfaces of vanes 407 due to airflow 405. As a result, outlet vane ends 426 of VID 404 pivot inwardly toward central rotational axis 403, and VID 404 is actuated to a closed position.

[0050] like Figure 4A As shown, when the VID 404 is in the closed position, the inlet vane end 428 may touch or contact the inner wall 425. Figure 3B and Figure 3D As explained, the outlet blade ends 426 form a ring having a smaller diameter than the inlet blade ends 428. The overlapping arrangement of the outlet blade ends 426 creates a smooth inner surface that confines the flow through the compressor inlet 406, thereby improving compressor efficiency at light engine loads. The inner groove formed by the overlapping blade edges 426 generates a pre-vortex in the flow upstream of the impeller 408, thereby rotating the flow in the same direction as the rotation of the impeller blades 418.

[0051] Figure 4B Shown with the Figure 3A and Figure 3C FIG4 is a second schematic diagram 401 of VID 404 (shown in the open position of VID 300 shown in FIG4 ). In one example, the pressure at impeller blades 418 and upstream in recirculation passage 424 is equal to or less than the pressure in inlet duct 406 upstream of VID 404, and the pressure of the airflow through the recirculation passage, as indicated by arrow 431, may be equal to or less than the airflow 405. Consequently, vanes 407 of VID 404 experience a pressure on the outer face that is equal to or less than the pressure on the inner face, and VID 404 is actuated to the open position.

[0052] In the open position, the outlet vane ends 426 pivot outward toward the inner wall 425 and away from the central axis 403. In one example, both the inlet vane ends 428 and the outlet vane ends 426 can contact the inner wall 425 in the open position. When the VID 404 is in the open position, the diameter of the ring formed by the outlet vane ends 426 is equal to the diameter of the ring formed by the inlet vane ends 428. This minimizes the restriction of gas flow through the VID 404 and to the impeller 408 and can be the commanded configuration of the VID 404 at medium to high engine loads, as further described below.

[0053] Figures 5A to 5B A cross-sectional view of a fourth embodiment of a turbocharger compressor 502 is shown, the compressor including active case treatment (ACT) and a VID 540 (such as a VID 540) positioned in the inlet duct (eg, intake passage) of the compressor 502. Figures 3A to 3D In one embodiment, the compressor 502 may be Figure 1 The compressor 174 in the turbine (such as Figure 1 The turbine 176 shown in FIG5 may be rotationally coupled to the compressor 502 via a shaft 504. Specifically, the turbine converts the energy of the exhaust gas into rotational energy for rotating the drive shaft 504 connected to the impeller 506. The impeller 506 may also be referred to as a compressor impeller in this document. The compressor 502 includes an impeller 506, a diffuser 508, a volute (e.g., a compressor chamber) 510, an active case treatment 512, and a case 514. The rotation of the impeller 506 draws gas into the compressor 502 through the compressor inlet 516 of the case 514. As a non-limiting example, the gas may include air from the intake passage, exhaust gas (such as when long-loop EGR is used), gaseous fuel (such as when port injection of fuel is used), and combinations thereof. The gas flows from the compressor inlet 516 and is accelerated by the impeller 506 through the diffuser 508 into the volute 510. The diffuser 508 and the volute 510 decelerate the gas, thereby causing the pressure in the volute 510 to increase. Gas under pressure may flow from the volute 510 to the intake manifold.

[0054] Elements in the compressor 502 can be described relative to the direction of the gas flow path through the compressor 502. Elements that are substantially in the direction of the gas flow relative to a reference point are downstream of the reference point. Elements that are substantially opposite to the direction of the gas flow relative to the reference point are upstream of the reference point. For example, the compressor inlet 516 is upstream of the impeller 506, which is upstream of the diffuser 508. The diffuser 508 is downstream of the impeller 506, which is downstream of the compressor inlet 516.

[0055] The impeller 506 includes a hub 518 and a plurality of blades, including full blades 520 and splitters 522. The full blades 520 and the splitters 522 are attached to the hub 518. The edge of the full blade 520 that is most upstream in the compressor 502 is the leading edge of the full blade 520. Similarly, the splitter 522 includes a leading edge at the most upstream portion of the splitter 522. The leading edge of the full blade 520 is upstream of the splitter 522. The impeller 506 includes a rotation axis 524 that is aligned with the rotation axis of the drive shaft 504 and the turbine hub of the turbine. The rotation axis 524 is substantially parallel to the flow of gas at the compressor inlet 516 and substantially perpendicular to the flow of gas at the diffuser 508. The rotation axis 524 may also be referred to herein as the central axis of the compressor 502.

[0056] The casing 514 includes a compressor inlet 516, an intake passage (also referred to herein as an inlet duct) 526, a recirculation passage 528, a recirculation port 530, an actuation port 525, an exhaust port 532, and an injection port 534. The impeller 506 is housed in the intake passage 526. The exhaust port 532 is downstream of the leading edge of the full blades 520 and upstream of the leading edge of the flow splitter 522. The injection port 534 is downstream of the leading edge of the flow splitter 522. The actuation port 525 is upstream of the active casing 512, the exhaust port 532, and the injection port 534, and is directly adjacent to the VID 540 downstream of the recirculation port 530. The recirculation port 530 is downstream of the compressor inlet 516 and upstream of the impeller 506. The recirculation port 530 is configured to allow gas to flow between the intake passage 526 and the recirculation passage 528.

[0057] The actuation port 525 is adapted to passively actuate the VID 540 between an open condition and a closed condition, depending on the pressure differential experienced between the outer surface of the outlet end 503 of the vanes of the VID 540 (e.g., the surface facing the intake passage wall 507) and the inner surface of the outlet end 503 of the vanes of the VID 540. In the event that the pressure at the downstream end of the outlet of the compressor 502 (proximate the impeller 506, the discharge port 532, and / or the injection port 534) is higher than the pressure upstream of the inlet duct 516 (e.g., upstream of the VID 540), the air flow restriction of the recirculation passage 528 in the direction opposite to the flow through the intake passage 526 is increased. Gas can flow from the recirculation passage 528 and through the actuation port 525 via the path depicted by arrows 542, and the pressure generated on the outer surface of the outlet end 503 of the VID 540 is higher than the pressure experienced by the inner surface of the outlet end 503 due to the air flow through 526. Thus, the position of the outlet end 503 of the VID 540 can be adjusted to a closed position, such as Figure 5AWhen the pressure experienced by the outer surface of the outlet end 503 of the VID 540 is less than or equal to the pressure exerted on the inner surface, the VID 540 is actuated to the open position, as shown. Figure 5B As shown, the restriction to air flow through the intake passage 526 is minimized.

[0058] Active case processing 512 is configured to control airflow through compressor 502. Specifically, active ... Figure 1 Active case processing 512, controlled by a controller 12 (shown), can selectively control the flow of gas through exhaust port 532 and injection port 534. During low mass flow conditions, active case processing 512 can enable gas to flow from intake passage 526 through exhaust port 532 into recirculation passage 528. Gas further continues from recirculation passage 528 into intake passage 526 through recirculation port 530. As a result, the gas flow striking the leading edge of full blade 520 can be greater than the gas flow without exhaust port 532. The additional gas flow can enable the turbocharger compressor to operate with less gas flow through the compressor before surge occurs.

[0059] During high-mass flow conditions, active case treatment 512 can enable gas to flow through injection port 534. During high-mass flow conditions, a low-pressure region can exist in intake passage 526 downstream of the leading edge of flow splitter 522 adjacent to injection port 534. The low-pressure region can direct gas from intake passage 526 through recirculation port 530 to recirculation passage 528, and back into intake passage 526 through injection port 534. The short-circuited path through recirculation passage 526 can increase gas flow through the compressor during high-mass flow conditions when compared to a compressor without injection port 534. In this way, the short-circuited gas flow can enable more gas to flow before the turbocharger enters a choked condition.

[0060] The intake passage 526 may be substantially cylindrical. The recirculation passage 528 may be substantially annular because it is outside the intake passage 526. The ports connecting the intake passage 526 and the recirculation passage 528, such as the recirculation port 530, the injection port 534, and the exhaust port 532, may each be implemented using various devices. For example, the ports may be configured as one or more holes formed in the wall 525 of the intake passage 526 (e.g., the wall forming the intake passage 526). In one example, the wall 525 may be part of the casing 514. As another example, the ports may be configured as one or more slots that extend around the circumference of the intake passage and extend through the wall of the casing forming the intake passage. The ports may have uniform or uneven widths along the length of the ports from the intake passage 526 to the recirculation passage 528. Each port may have a centerline extending along the length of the port from the intake passage 526 to the recirculation passage 528. The centerline may be normal to the rotational axis 524 of the impeller 506 , or the centerline may have a non-zero slope when compared to being normal to the rotational axis 524 of the impeller 506 .

[0061] Active casing treatment 512 can be implemented in many ways. For example, a slidable casing sleeve can be mounted in the recirculation passage to selectively block the flow of gas through the injection port 534 and / or the exhaust port 532. The casing sleeve can include one or more holes and / or one or more slots 536, such as Figures 5A to 5B As shown, depending on the position of the receiver sleeve, the one or more holes and / or one or more slots 536 are aligned with the injection port 534 and / or the exhaust port 532. For example, when a controller (such as the controller 12) detects a low mass flow condition, the receiver sleeve can be adjusted so that the slot 536 in the receiver sleeve is aligned with the exhaust port 532 and the slot 536 in the receiver sleeve is not aligned with the injection port 534. In this way, the receiver sleeve can be adjusted so that during a low mass flow condition, the exhaust port 532 is opened and the injection port 534 is blocked.

[0062] As another example, when the controller detects a high mass flow condition, the case sleeve may be adjusted so that the slot 536 in the case sleeve is aligned with the injection port 534, but the slot 536 in the case sleeve is not aligned with the exhaust port 532. In this manner, the case sleeve may be adjusted so that during high mass flow conditions, the injection port 534 is open and the exhaust port 532 is blocked. In an alternative embodiment, the active case treatment 512 may be adjusted based on the pressure difference between the compressor inlet 516 and the intake manifold. In yet another alternative embodiment, the active case treatment 512 may be adjusted based on the pressure difference between the intake manifold and the turbine inlet. In yet another alternative embodiment, the active case treatment 512 may be adjusted based on the engine load and engine speed conditions of the engine relative to surge and choke thresholds (e.g., the current operating speed and load of the engine). It should be understood that these specific embodiments are provided by way of example and are not intended to be limiting in any way.

[0063] like Figures 5A to 5B As shown, a variable inlet device (VID) 540 is positioned within the intake passage 526 upstream of the impeller 506. As described above, the VID 540 may be Figures 3A to 3D VID 300 is shown. Figure 5A A first schematic diagram 500 is shown in which the VID is adjusted (eg, actuated) to the off position, as described above with reference to FIG. Figure 3A and Figure 3C As stated, Figure 5B A second schematic diagram 550 is shown in which the VID is adjusted (eg, actuated) to the open position, as described above with reference to FIG. Figure 3B and Figure 3D As stated.

[0064] Specifically, the outlet end 503 of the VID 540 is disposed upstream of the exhaust port 532, and the inlet end 505 is disposed downstream of the recirculation port 530. The VID 540 spans the entire intake passage 526 and is disposed adjacent to a wall 507 of the intake passage 526. Under lighter load conditions, the VID 540 can be passively actuated to a closed position by flow through the actuation port, as shown. Figure 5A As shown, the active case 512 can be adjusted to a position that allows the exhaust port 532 to be opened. The spiral internal grooves created by the overlapping arrangement of the blades of the VID 540 at the outlet end generate a pre-swirl flow in the air passing through the VID 540 before contacting the downstream impeller 506. The intake passage 526 downstream of the VID 540 enters the recirculation passage 528 through the exhaust port 532, and the recirculated air returned to the intake passage 526 via the recirculation port 530 and the pre-swirl flow generated by the closed VID 540 can increase the compressor surge margin.

[0065] For medium engine loads, the VID 540 is actuated to the open position by the above-described actuation method, such as Figure 5A As shown, the active case 512 is adjusted so that the exhaust port 532 and the injection port 534 are closed. Flow restriction through the VID 540 is minimized, and circulation through the exhaust port 532 and the injection port 534 is prohibited. For higher mass flow and higher engine load conditions, the VID 540 remains open and the active case 512 is adjusted to allow the injection port 534 to pass into the intake passage 526. The flow of air through the recirculation port 530 can continue into the recirculation passage and enter the intake passage 526 through the injection port 534. This short-circuit flow improves the choke margin at high engine loads.

[0066] exist Figures 4A to 4B and Figures 5A to 5B In an alternative embodiment, the VID may be actively controlled via an actuator in electronic communication with the controller (e.g. Figures 2A to 2B In these embodiments, the recirculation path may not include the actuation channel described above.

[0067] Figures 2A to 5B Example configurations with relative positioning of various components are shown. If shown as being in direct contact or directly coupled to each other, then, in at least one example, such elements may be referred to as being in direct contact or directly coupled, respectively. Similarly, elements shown as being adjacent or proximate to each other may be referred to as being adjacent or proximate to each other, respectively, in at least one example. As an example, components placed in coplanar contact with each other may be referred to as being in coplanar contact. As another example, components positioned separately from each other with only space between them and no other components may be referred to as being in coplanar contact, at least in one example. As yet another example, elements shown above / below each other, on opposite sides of each other, or to the left / right of each other may be referred to as such relative to each other. Furthermore, as shown in the figure, in at least one example, the topmost element or the topmost point of an element may be referred to as the "top" of a component, and the bottommost element or the bottommost point of an element may be referred to as the "bottom" of a component. As used herein, top / bottom, upper / lower, above / below may be relative to the vertical axis of a figure and used to describe the positioning of elements of a figure relative to each other. Thus, in one example, an element shown above other elements is positioned vertically above the other elements. As yet another example, shapes of elements shown within a figure may be referred to as having those shapes (e.g., such as circular, straight, flat, curved, rounded, chamfered, angled, etc.). Furthermore, in at least one example, elements that intersect one another may be referred to as intersecting elements or intersecting one another. Furthermore, in one example, an element shown within another element or shown outside another element may be referred to as such.

[0068] Go to Figure 6, a flow chart illustrating a method 600 for controlling the operation (eg, controlling the position) of a variable inlet device positioned in an inlet duct of a compressor. Specifically, a variable inlet device (VID) may be Figures 3A to 3D The VID 300 is shown in FIG. The VID may be located in the inlet duct of the compressor upstream of the impeller, such as Figures 2A to 2C In some embodiments, the VID may be located in the inlet duct of the compressor upstream of the impeller, where the compressor additionally includes a case treatment including a recirculation path such as Figures 4A to 4B Instructions for implementing method 600 and the remaining methods included herein may be provided by a controller (e.g., Figure 1 The controller 12 shown in FIG. 1 is executed based on instructions stored in the controller's memory and in conjunction with signals received from sensors of the engine system, such as those described above with reference to FIG. Figure 1 According to the method described below, the controller may use the engine actuator of the engine system to adjust the engine operation. For example, the controller may use the actuator of the VID to adjust the open position (such as Figure 2A 、 Figure 3A 、 Figure 3C and Figure 4B shown) and closed position (as Figure 2B 、 Figure 3B 、 Figure 3D and Figure 4A As mentioned above, Figures 2A to 2B An example of such an actuator coupled to a VID is shown. In an alternative embodiment, the VID may be passively actuated via a pressure difference between the outer and inner surfaces of the outlet end of the vanes of the VID, such as Figure 2C and Figures 4A to 4B In these embodiments, method 600 may not be executed by a controller, but rather may be performed passively via the various passages and actuation paths described above based on varying pressure differentials occurring at certain thresholds, such as a surge threshold. Thus, in the methods described below, the opening and closing of the VID may occur passively based on varying pressure differentials above and below the surge threshold.

[0069] At 602, the method includes estimating and / or measuring engine operating conditions. The engine operating conditions may include engine speed, engine load, engine temperature (such as engine coolant temperature), mass air flow to the engine, intake manifold pressure, pressure difference across the compressor, mass air flow rate through the compressor, position of the VID, etc. At 604, the method includes determining whether the current engine operation is below a surge threshold. The current engine operation below the surge threshold may include a current (e.g., currently determined) engine load and engine speed below a surge line or surge threshold. For example, a map of engine load versus engine speed (such as Figure 7 The map 700 shown in FIG may be stored in the memory of the controller. Figure 7 , map 700 includes an operating boundary line 702. All possible engine speed and engine load operating points of the engine may be contained within the axis and operating boundary line 702. Map 700 also includes a surge threshold line 704. When the engine is operated at an engine speed and engine load point that fall below or to the left of surge threshold line 704, the likelihood of compressor surge may increase relative to when the engine is operated at an engine speed and engine load point that fall above or to the right of surge threshold line 704. Map 700 includes two regions: a first region 706 below or to the left of surge threshold line 704, and a second region 708 above or to the right of surge threshold line 704. As further explained below, when the engine is operated at an engine speed and engine load point that fall within first region 706, the engine may be operating under lighter load conditions, and the controller may actuate the VID to the closed position. Conversely, when the engine is operating at an engine speed and engine load point that falls within the second region 708, the engine may be operating at a higher load condition, and the controller may actuate the VID to an open position. In an alternative embodiment, instead of a map of engine speed and engine load, the controller may utilize a map of compressor conditions, such as the pressure difference across the compressor relative to the surge line and the mass air flow through the compressor, to determine which position to adjust the VID to.

[0070] Return to Figure 6 At 604, the controller may use a method similar to Figure 7700 , and the method continues to 606 to open the VID. Opening the VID may include the controller sending an electronic signal to an actuator (such as an actuator) of the VID. Figures 2A to 2B ) to adjust the VID from the closed position to the open position or to maintain the VID in the open position. As described above, the open position of the VID is Figure 2A 、 Figure 3A 、 Figure 3C and Figure 4B As explained above with reference to these figures, in the open position, the inner surface of the VID does not restrict flow through the VID from the inlet end to the outlet end of the VID. Adjusting the VID from the closed position to the open position may include pivoting a plurality of adjacently arranged vanes of the VID in a direction relative to a central axis of the compressor (about which the impeller rotates) via an actuator coupled to a pivot axis of the vanes to reduce overlap of the plurality of adjacently arranged vanes at the outlet end of the VID and increase the diameter of the outlet end of the VID.

[0071] In an alternative embodiment, when the VID is passively actuated via a pressure differential across the VID via a passage or actuation port in the wall of the inlet duct (rather than actively actuated via a controller), the method may include flowing gas through a recirculation chamber or passage (e.g., a chamber) in the opposite direction of flow through the intake passage. Figures 4A to 4B This may occur during conditions where the engine is operating below the surge threshold, i.e. Figure 6 608 in FIG, and results in a higher pressure at the outlet end of the compressor (defined as downstream of the leading edge of the compressor impeller) relative to the pressure at the inlet end of the compressor (defined as upstream of the impeller and VID). The pressure difference across the compressor results in a reverse flow through the recirculation chamber or passage, which generates airflow through a passage or actuation port immediately adjacent to the VID, which is disposed in the recirculation passage downstream of the impeller and upstream of the recirculation port, as shown in FIG. Figures 4A to 4B As shown. The airflow through the passage or actuation port exerts a pressure on the outer surface of the vane of the VID (e.g., the wall facing the inlet passage) that is greater than the pressure experienced by the inner surface of the vane due to the airflow through the inlet passage. The pressure difference across the vane of the VID actuates the VID to the closed position, thereby directing 604 forward to Figure 6 of 608.

[0072] During conditions where the engine is operating above a surge threshold and the pressure at the outlet end is less than or equal to the pressure at the inlet end of the compressor, the method may include airflow through the intake passage that is equal to or greater than the airflow through the recirculation chamber and passage or actuation port, resulting in a pressure experienced at the inner surface of the vanes of the VID that is greater than or equal to the pressure applied to the outer surface of the vanes, thereby actuating or maintaining the VID in an open position. Thus, 604 continues to Figure 6 606 in the.

[0073] Alternatively, at 604, if the engine is operating below the surge threshold (e.g., when the current engine speed and load point are in the first region 706 shown in the map 700), the method continues to 608 to close the VID. Closing the VID may include the controller sending an electronic signal to the actuator of the VID to adjust the VID from the open position to the closed position or to maintain the VID in the closed position. As described above, the closed position of the VID is Figure 2B 、 Figure 3B 、 Figure 3D and Figure 4A As explained above with reference to these figures, in the closed position, the inner surface of the VID narrows along the length of the VID and generates a swirling flow at the outlet end of the VID. Adjusting the VID from the open position to the closed position may include pivoting each vane of the VID via an actuator coupled to the pivot axis of the vane so that the outlet end of each vane pivots toward the central axis of the compressor and the inlet end of each vane pivots away from the central axis of the compressor.

[0074] Go to Figure 8 , a flow chart illustrating a method 800 for coordinating control of a position of a variable inlet device positioned in an inlet duct of a compressor and control of an active case process of the compressor. Specifically, the variable inlet device (VID) may be Figures 3A to 3D The VID 300 is shown in FIG. The VID may be positioned in the inlet duct of a compressor having active case treatment upstream of the impeller, such as Figures 5A to 5B The instructions for executing the method 800 may be provided by a controller (e.g., Figure 1 The controller 12 shown or Figures 2A to 2B The controller 211 shown in FIG. 2 is based on instructions stored in the controller's memory and in conjunction with sensors from the engine system (such as those referenced above). Figure 1 According to the method described below, the controller may use the engine actuator of the engine system to adjust the engine operation. For example, the controller may use the actuator of the VID to open the position (such as Figure 3A 、 Figure 3C and Figure 5Bshown) and closed position (as Figure 3B 、 Figure 3D and Figure 5A As shown above, the VID is adjusted between Figures 2A to 2B An example of such an actuator coupled to a VID is shown in FIG. In an alternative embodiment, the VID may be passively actuated via a pressure difference between the outer and inner surfaces of the outlet end of the vanes of the VID, such as Figures 5A to 5B In these embodiments, method 800 may not be executed by a controller, but rather may be performed passively via the various passages and actuation paths described above based on varying pressure differentials occurring at certain thresholds (e.g., surge thresholds). Thus, in the methods described below, the opening and closing of the VID may occur passively based on varying pressure differentials above and below the surge threshold.

[0075] At 802, the method includes estimating and / or measuring engine operating conditions. The engine operating conditions may include engine speed, engine load, engine temperature (such as engine coolant temperature), mass air flow to the engine, intake manifold pressure, pressure differential across the compressor, mass air flow rate through the compressor, position of the VID, position of active case treatments (e.g., position of a sliding sleeve along an inner wall of the case relative to drain slots, surge slots, and recirculation slots on the inner wall), etc. At 804, the method includes determining whether current engine operation is below a surge threshold. Current engine operation below a surge threshold may include current (e.g., currently determined) engine load and engine speed being below a surge line or threshold. For example, a map of engine load versus engine speed (such as Figure 9 The mapping shown in FIG900) can be stored in the memory of the controller. Figure 9 , map 900 includes an operating boundary line 902. All possible engine speed and engine load operating points of the engine may be contained within the axis and operating boundary line 902. Map 900 also includes a surge threshold line 904 and a choke threshold line 906. When the engine is operated at an engine speed and engine load point that falls below or to the left of surge threshold line 904, the likelihood of compressor surge may be increased relative to when the engine is operated at an engine speed and engine load point that falls above or to the right of surge threshold line 904. Additionally, when the engine is operated at an engine speed and engine load point that falls above or to the right of choke threshold line 906, the likelihood of compressor choke may be increased relative to when the engine is operated at an engine speed and engine load point that falls below or to the left of choke threshold line 906.

[0076] Map 900 includes three regions: a first region 908 below or to the left of surge threshold line 904, a second region 910 above or to the right of surge threshold line 904 and below or to the left of choke threshold line 906, and a third region 912 above or to the right of choke threshold line 906. As further explained below, when the engine is operating at an engine speed and engine load point that fall within first region 908, the engine may be operating under lighter load conditions, and the controller may actuate the VID to a closed position while also actuating an active case treatment (ACT) to a position for surge control. In one example, actuating the ACT to a position for surge control may include adjusting a sliding sleeve of the ACT to a first position in which a plurality of sleeve slots of the sliding sleeve are aligned with a discharge port (such as a throttle port). Figures 5A to 5B In the first position, gas can flow between the intake passage of the compressor and the recirculation passage of the ACT via the exhaust port and the recirculation port of the ACT. When the engine is operated at an engine speed and an engine load point that falls within the second region 910, the engine can operate at a medium load condition, and the controller can actuate the VID to an open position and actuate the ACT to supply air to the surge port and the injection port (such as Figures 5A to 5B In one example, actuating the ACT to close both the surge port and the injection port may include adjusting the sliding sleeve of the ACT to a second position, in which a plurality of sleeve slots are not aligned with the exhaust port or the injection port. Therefore, gas does not flow between the intake passage and the recirculation passage via either the exhaust port or the injection port. Finally, when the engine is operated at an engine speed and an engine load point falling within the third region 912, the engine may operate under a higher load condition, and the controller may actuate the VID to an open position and actuate the ACT to a position for throttle control. In one example, actuating the ACT to a position for throttle control may include adjusting the sliding sleeve of the ACT to a third position, in which a plurality of sleeve slots are aligned with the injection port. In the third position, gas flows between the intake passage and the recirculation passage via the injection port and the recirculation port. In an alternative embodiment, the controller may utilize a map of compressor conditions other than a map of engine speed and engine load, such as the pressure difference across the compressor relative to surge and choke lines and the mass air flow through the compressor, to determine where to adjust VID and ACT.

[0077] Return to Figure 8 At 804, the controller may use a method similar to Figure 9900 is stored in the mapping table or lookup table to determine whether the engine is operating below the surge threshold. For example, the controller may determine the current engine speed and engine load, and then look up whether the operating point is above the surge threshold or below the surge threshold and / or above the choke threshold or below the choke threshold. In one example, the surge threshold may be a preset surge threshold stored in the mapping table or lookup table, and the choke threshold may be a preset choke threshold stored in the mapping table or lookup table. If the engine is operating below the surge threshold (e.g., the current engine speed and load point are in the first region 908), the method continues to 806 to close the VID and adjust the ACT to open to the surge slot. Closing the VID may include the controller sending an electronic signal to an actuator of the VID to adjust the VID from an open position to a closed position or to maintain the VID in the closed position. As described above, the closed position of the VID is Figure 3B 、 Figure 3D and Figure 5A As explained above with reference to these figures, in the closed position, the inner surface of the VID narrows along the length of the VID and generates a swirl flow at the outlet end of the VID. Adjusting the VID from the open position to the closed position may include pivoting each vane of the VID via an actuator coupled to the pivot axis of the vane so that the outlet end of each vane pivots toward the central axis of the compressor and the inlet end of each vane pivots away from the central axis of the compressor. Adjusting the ACT to open to the surge slot may include adjusting a slidable sleeve of the ACT to a first position in which a plurality of sleeve slots of the ACT are aligned with a discharge port (such as Figures 5A to 5B ACT 512 and exhaust port 532 are aligned as shown in FIG. In one example, the method of 806 may include closing the VID while adjusting the ACT to open toward the surge slot. In this manner, in response to the engine operating below the surge threshold, the controller may send two actuation signals, one for closing the VID and one for opening the ACT toward the surge slot.

[0078] Alternatively, at 804, if the engine is not operating below the surge threshold (e.g., the current engine speed and load point are in the second region 910 or the third region 912 shown in map 900), the method continues to 808 to determine if the engine is operating above the choke threshold. For example, the controller may determine the current engine speed and engine load and then look up (using map 900 or a similar map or lookup table stored in the controller's memory) whether the operating point is above the choke threshold or below the choke threshold. If the engine is operating above the choke threshold (e.g., the current engine speed and load point are in the third region 912), the method continues to 810 to open the VID and adjust the ACT to open toward the choke slot. Opening the VID may include the controller activating an actuator (such as an ACT) of the VID. Figures 2A to 2BThe actuator 209 shown in FIG sends an electronic signal to adjust the VID from the closed position to the open position or to maintain the VID in the open position. As described above, the open position of the VID is Figure 3A 、 Figure 3C and Figure 5B As explained above with reference to these figures, in the open position, the inner surface of the VID does not restrict flow through the VID from the inlet end to the outlet end of the VID. Adjusting the VID from the closed position to the open position may include pivoting a plurality of adjacently arranged vanes of the VID in a direction relative to a central axis of the compressor (about which the impeller rotates) via an actuator coupled to a pivot axis of the vanes to reduce overlap of the plurality of adjacently arranged vanes at the outlet end of the VID and increase a diameter of the outlet end of the VID. Adjusting the ACT to open toward the choke slot may include adjusting a slidable sleeve of the ACT to a third position in which a plurality of sleeve slots of the ACT are aligned with the injection port (such as Figures 5A to 5B ACT 512 and injection port 534 shown in FIG. ). In one example, the method 810 may include opening the VID while adjusting the ACT to open the choke slot. In this manner, in response to the engine operating above the choke threshold, the controller may send two actuation signals, one for opening the VID and one for opening the ACT to the choke slot.

[0079] Alternatively, at 808, if the engine is not operating above the choke threshold, the engine may be operated at an engine speed and load point in the second region 910 shown in the map 900. In response to operating below the choke threshold but above the surge threshold, the method continues to 812 to open the VID and adjust the ACT to move the engine toward the surge slot (e.g., Figures 5A to 5B ) and a choke slot (e.g., Figures 5A to 5B 534 shown in FIG. 2 . Adjusting the ACT to close both the surge slot and the choke slot may include adjusting a slidable sleeve of the ACT to a second position in which the plurality of sleeve slots are not aligned with the exhaust port or the injection port. In one example, the method at 812 may include opening the VID while adjusting the ACT to open both the surge slot and the choke slot. In this manner, in response to the engine operating below a choke threshold and above a surge threshold, the controller may send two actuation signals, one for opening the VID and one for closing the ACT to both the choke slot and the surge slot.

[0080] In an alternative embodiment, when the VID is passively actuated via a pressure differential across the VID via a passage or actuation port in the wall of the inlet duct (rather than actively actuated via a controller), the method may include flowing gas through the recirculation chamber (e.g., in the opposite direction of flow through the intake passage) in the opposite direction of flow through the intake passage. Figure 4A and Figure 5A This may occur during conditions where the engine is operating below the surge threshold, i.e. Figure 8 806 in, and results in a higher pressure at the outlet end of the compressor than at the inlet end. The pressure difference across the compressor results in a reverse flow through the recirculation chamber, which generates airflow through a passage or actuation port directly adjacent to the VID and downstream of the discharge port, surge slot, and impeller and upstream of the recirculation port, as shown in FIG. Figures 5A to 5B As shown. The airflow through the passage or actuation port exerts a pressure on the outer surface of the vanes of the VID (e.g., the wall facing the inlet passage) that is greater than the pressure experienced by the inner surface of the vanes, such as the pressure caused by the airflow through the inlet passage. The pressure difference across the vanes of the VID actuates the VID to the closed position, causing 804 to continue to Figure 8 806 in it.

[0081] During conditions where the engine is operating above a surge threshold and the pressure at the outlet end is less than or equal to the pressure at the compressor inlet end, the method may include airflow through the intake passage being equal to or greater than airflow through the recirculation chamber and passage or actuation port, resulting in a pressure experienced at the inner surface of the vanes of the VID being greater than or equal to the pressure applied to the outer surface of the vanes, thereby actuating or maintaining the VID in an open position. In this manner, 804 proceeds to Figure 8 808 in it.

[0082] In this way, a variable inlet device (VID) positioned within the inlet duct of a compressor upstream of the compressor's impeller can be used to regulate flow through the inlet duct and to the impeller. The VID can include a plurality of adjacent vanes arranged in a ring centered along the compressor's central rotational axis. Each vane includes an inlet end positioned upstream of the outlet end, with each vane adapted to pivot about an axis tangential to the ring and perpendicular to the compressor's central rotational axis. In one example, the VID can be adjusted to an open position, in which the outlet ends of the vanes are pivoted away from the central rotational axis and positioned proximate to the wall of the inlet duct. In this position, flow restriction through the VID and to the impeller is reduced, thereby increasing compressor performance in this position. In another example, the VID can be adjusted to a closed position, in which the outlet ends of the vanes are pivoted toward the central rotational axis and adjacent vanes overlap. This creates a narrow path through the VID from the inlet end to the outlet end, and induces pre-swirl to the internal spiral groove of the impeller. Adjusting the VID to the closed position under lighter load conditions has the technical effect of increasing compressor efficiency while also reducing the likelihood of surge. The technical effect of adjusting the VID to the open position under higher load conditions is to reduce flow restriction to the impeller, thereby increasing compressor efficiency and reducing the likelihood of choking under certain conditions. Additionally, as explained above, by combining the VID with active case treatment on the compressor, compressor surge control and choke control can be increased, while also improving compressor efficiency under lighter and higher load conditions.

[0083] As one embodiment, a compressor includes: an impeller rotatable about a central axis; and an inlet duct including a variable inlet device (VID) located therein upstream of the impeller and including a plurality of adjacently arranged blades forming a ring about the central axis, wherein inner surfaces of the blades form a flow path through the VID, and each of the blades is pivotable about an axis arranged tangentially to the ring between an open position and a closed position. In a first example of the compressor, each of the plurality of blades includes an inlet end and an outlet end, the inlet end being arranged upstream of the outlet end, and wherein the flow path is formed within the inner surface of the blade between the inlet end and the outlet end of each blade. A second example of the compressor optionally includes the first example, and further includes wherein each blade includes a side surface extending between the inlet end and the outlet end, and wherein, for each blade, a first side surface of the side surface contacts a side surface of a first adjacent blade, and a second side surface of the side surface contacts a side surface of a second adjacent blade. A third example of the compressor optionally includes one or more of the first and second examples, and further includes wherein the inlet end of the VID is formed by the inlet end of each blade, and the outlet end of the VID is formed by the outlet end of each blade, and wherein in the closed position, the inlet end of the VID has a larger diameter than the outlet end of the VID. A fourth example of the compressor optionally includes one or more of the first to third examples, and further includes wherein in the closed position, the outlet ends of adjacent blades of the plurality of blades overlap more than the inlet ends of adjacent blades of the plurality of blades. A fifth example of the compressor optionally includes one or more of the first to fourth examples, and further includes wherein in the open position, each of the inlet end of the VID and the outlet end of the VID has a larger diameter than the outlet end of the VID in the closed position, and wherein the difference in diameter between the inlet end and the outlet end of the VID in the open position decreases relative to the closed position. A sixth example of the compressor optionally includes one or more of the first to fifth examples, and further includes wherein in the closed position, the outlet end of each blade is positioned closer to the central axis than the inlet end of each blade, and the inlet end of each blade is positioned proximate to the inner wall of the inlet duct. A seventh example of the compressor optionally includes one or more of the first to sixth examples, and further includes wherein in the open position, inner surfaces of the vanes contact each other but do not overlap and are arranged parallel to the central axis. An eighth example of the compressor optionally includes one or more of the first to seventh examples, and further includes wherein in the closed position, inner surfaces of the vanes are angled relative to the flow through the inlet duct and form a smooth surface having a plurality of spiral grooves facing the flow, wherein the vanes are angled inwardly toward the central axis from an inlet end to an outlet end of the VID, the outlet end being arranged in the inlet duct downstream of the inlet end, and wherein the plurality of spiral grooves are formed by overlapping inner surfaces of a plurality of adjacently arranged vanes.A ninth example of the compressor optionally includes one or more of the first to eighth examples and further includes a passage arranged in the inlet duct upstream of the impeller and downstream of the inlet end of the VID, wherein the passage extends outward from the central axis so that an inner wall of the inlet duct in the region of the passage is positioned farther from the central axis than an inner wall of the inlet duct in the region of the inlet duct arranged upstream of the inlet end of the VID. A tenth example of the compressor optionally includes one or more of the first to ninth examples and further includes a recirculation passage formed by a casing of the compressor and surrounding the inlet duct, the recirculation passage being fluidly coupled to the inlet duct via a discharge port and a recirculation port, the discharge port being formed in the wall of the inlet duct downstream of the leading edge of the impeller and the recirculation port being formed in the wall of the inlet duct upstream of the inlet end of the VID.

[0084] As another embodiment, a method includes adjusting a variable inlet device (VID) positioned in and across a compressor inlet duct upstream of an impeller between an open position and a closed position in response to engine operation relative to a surge threshold of the compressor, wherein in the open position an inner surface of the VID does not restrict flow through the VID from an inlet end to an outlet end of the VID, and in the closed position the inner surface narrows along the length of the VID and generates a swirling flow at the outlet end of the VID. In a first example of the method, the VID includes a plurality of adjacently arranged vanes forming a ring around a central axis of the compressor, wherein inner surfaces of the plurality of adjacently arranged vanes form an inner surface of the VID and a flow path through the VID, and wherein each vane of the plurality of adjacently arranged vanes includes an inlet end and an outlet end, the inlet end being arranged in the inlet duct upstream of the outlet end. A second example of the method optionally includes the first example, and further includes wherein adjusting the VID between the open position and the closed position includes adjusting the VID from the open position to the closed position in response to the engine in which the compressor is installed transitioning to operating at an engine speed and engine load below a surge threshold, and wherein adjusting the VID from the open position to the closed position includes pivoting each vane such that the outlet end of each vane pivots toward the central axis. A third example of the method optionally includes one or more of the first and second examples, and further includes wherein adjusting the VID between the open position and the closed position includes adjusting the VID from the closed position to the open position in response to the engine in which the compressor is installed transitioning to operating at an engine speed and engine load above a surge threshold, and wherein adjusting the VID from the closed position to the open position includes pivoting each vane such that the outlet end of each vane pivots away from the central axis and toward an inner wall of the inlet duct, and wherein pivoting each vane away from the central axis includes reducing overlap of a plurality of adjacently arranged vanes at the outlet end of the VID and increasing a diameter of the outlet end of the VID. A fourth example of the method optionally includes one or more of the first to third examples, and also includes wherein adjusting the VID between the open position and the closed position includes passively adjusting the VID between the open position and the closed position via an actuation port arranged in a wall of the inlet duct between the inlet duct upstream of the VID and downstream of the leading edge of the impeller and a recirculation passage surrounding the inlet duct and in fluid communication with the inlet duct, wherein the actuation port is positioned between an inlet end and an outlet end of the VID, adjacent to outer surfaces of a plurality of adjacently arranged blades.

[0085] As yet another embodiment, a system for an engine includes: a compressor including an impeller rotatable about a central axis; and a variable inlet device (VID) disposed upstream of the impeller in an inlet duct of the compressor, the VID including: a plurality of vanes disposed adjacent to one another to form a ring having an inlet end and an outlet end, the inlet end disposed in the inlet duct upstream of the outlet end, wherein the plurality of vanes are pivotable relative to the central axis from the inlet end to the outlet end; and a controller including computer-readable instructions stored in a memory for: in response to the engine operating below a surge threshold of the compressor, adjusting the VID to a closed position in which the plurality of vanes overlap one another at the outlet end, and inner surfaces of the plurality of vanes form a smooth surface having a plurality of spiral grooves disposed about the ring that narrows from the inlet end to the outlet end; and in response to the engine operating above the surge threshold, adjusting the VID to an open position in which the plurality of vanes do not overlap one another at the outlet end, and inner surfaces of the plurality of vanes form a smooth surface having a plurality of spiral grooves disposed about the ring that gradually widens from the inlet end to the outlet end. In a first example of the system, the system further includes a recirculation passage formed by the outer casing of the compressor and surrounding the inlet duct, the recirculation passage being in fluid communication with the inlet duct via a discharge port and a recirculation port, the discharge port being formed in the wall of the inlet duct downstream of the leading edge of the impeller, and the recirculation port being formed in the wall of the inlet duct upstream of the inlet end of the VID. A second example of the system optionally includes the first example, and further includes wherein in the closed position, the outlet ends of the plurality of vanes contact the inner wall of the inlet duct, and in the open position, the inlet ends of the plurality of vanes contact the inner wall of the inlet duct. A third example of the system optionally includes one or more of the first and second examples, and further includes wherein the outlet end of the VID has a narrower diameter in the closed position than in the open position, and wherein each of the plurality of spiral grooves is formed by overlapping side surfaces of two adjacent vanes of the plurality of vanes.

[0086] In another representation, a method includes adjusting a variable inlet device (VID) positioned in and across a compressor inlet duct upstream of an impeller between an open position and a closed position in response to a current engine speed and engine load operating point of an engine, wherein in the open position, an inner surface of the VID does not restrict flow through the VID from an inlet end to an outlet end of the VID, and in the closed position, the inner surface narrows along the length of the VID and generates a swirl flow at the outlet end of the VID while recirculating airflow from the impeller to a point in the inlet duct upstream of the VID. In one example, recirculating airflow from the impeller to a point in the inlet duct upstream of the VID includes recirculating the airflow through a recirculation passage formed by an outer case of the compressor and surrounding the inlet duct.

[0087] In yet another representation, the compressor includes an impeller rotatable in a first direction about a central axis; and an inlet duct including a variable inlet device (VID) positioned in the inlet duct upstream of the impeller and including a plurality of adjacently arranged blades forming a ring about the central axis, wherein inner surfaces of the blades form a flow path through the VID, each of the blades being pivotable about an axis tangential to the ring between an open position and a closed position, wherein in the closed position the inner surface forms a smooth surface including a plurality of grooves, wherein the direction of curvature of the plurality of grooves is oriented to rotate the flow through the flow path in the first direction.

[0088] Note that the exemplary control and estimation routines included herein can be used with various engine and / or vehicle system configurations. The control methods and routines disclosed herein can be stored as executable instructions in a non-transitory memory and can be implemented by a control system comprising a controller in combination with various sensors, actuators, and other engine hardware. The specific routines described herein may represent one or more of any number of processing strategies, such as event-driven, interrupt-driven, multi-tasking, multi-threading, etc. Therefore, the various actions, operations, and / or functions shown can be performed in parallel in the sequence shown or omitted in some cases. Similarly, in order to achieve the features and advantages of the exemplary embodiments described herein, the processing order is not necessarily required, but is provided for ease of illustration and description. One or more of the actions, operations, and / or functions shown can be repeatedly performed depending on the specific strategy used. In addition, the described actions, operations, and / or functions can graphically represent code to be programmed into the non-transitory memory of a computer-readable storage medium in the engine control system, where the described actions are implemented by executing instructions in a system comprising a combination of various engine hardware components and an electronic controller.

[0089] It will be understood that the configurations and routines disclosed herein are exemplary in nature, and that these specific embodiments should not be considered limiting, as many variations are possible. For example, the above technology can be applied to V-6, I-4, I-6, V-12, opposed 4, and other engine types. The subject matter of the present disclosure includes all novel and non-obvious combinations and sub-combinations of the various systems and configurations and other features, functions, and / or properties disclosed herein.

[0090] The following claims particularly point out certain combinations and subcombinations regarded as novel and non-obvious. These claims may refer to "an" element or "a first" element or the equivalent thereof. Such claims should be understood to include incorporation of one or more such elements, neither requiring nor excluding two or more such elements. Other combinations and subcombinations of the disclosed features, functions, elements, and / or properties may be claimed by amendment of the present claims or by presentation of new claims in this or a related application. Such claims, whether broader, narrower, equal, or different in scope to the original claims, are deemed included within the subject matter of the present disclosure.

Claims

1. A compressor comprising: a pump impeller rotatable about a central axis; as well as an inlet duct including a variable inlet device (VID) located in the inlet duct upstream of the impeller and including a plurality of vanes arranged adjacently forming a ring about the central axis, wherein inner surfaces of the vanes form a flow path through the VID, each of the vanes being pivotable about an axis arranged tangentially to the ring between an open position and a closed position; as well as a recirculation passage formed by the outer casing of the compressor and surrounding the inlet duct, the recirculation passage being fluidly coupled to the inlet duct via a discharge port and a recirculation port, the discharge port being formed in the wall of the inlet duct downstream of the leading edge of the impeller, and the recirculation port being formed in the wall of the inlet duct upstream of the inlet end of the VID, the passage also including an actuation port that fluidly couples the recirculation passage to the inlet duct at a location directly adjacent the plurality of blades.

2. The compressor of claim 1 , wherein each of the plurality of blades includes an inlet end and an outlet end, the inlet end being arranged upstream of the outlet end, and wherein the flow passage is formed within the inner surface of the blade between the inlet end and the outlet end of each blade.

3. The compressor of claim 2, wherein each vane includes a side surface extending between the inlet end and the outlet end, and wherein, For each blade, a first side surface of the side surface contacts a side surface of a first adjacent blade, and a second side surface of the side surface contacts a side surface of a second adjacent blade.

4. The compressor of claim 2, wherein an inlet end of the VID is formed by the inlet end of each vane, and an outlet end of the VID is formed by the outlet end of each vane, and wherein in the closed position, the inlet end of the VID has a larger diameter than the outlet end of the VID.

5. The compressor of claim 4, wherein in the closed position, outlet ends of adjacent ones of the plurality of blades overlap more than inlet ends of adjacent ones of the plurality of blades, and wherein In the open position, each of the inlet end of the VID and the outlet end of the VID has a larger diameter than the outlet end of the VID in the closed position, and wherein the diameter difference between the inlet end and the outlet end of the VID in the open position is reduced relative to the closed position.

6. The compressor of claim 2, wherein in the closed position, the outlet end of each vane is located closer to the central axis than the inlet end of each vane, and the inlet end of each vane is located proximate an inner wall of the inlet duct.

7. The compressor of claim 1, wherein in the open position, the inner surfaces of the vanes contact each other but do not overlap and are arranged parallel to the central axis.

8. The compressor of claim 1 , wherein in the closed position, the inner surface of the vane is angled relative to the flow through the inlet duct and forms a smooth surface having a plurality of spiral grooves facing the flow, wherein the vane is angled inwardly toward the central axis from an inlet end to an outlet end of the VID, the outlet end being arranged in the inlet duct downstream of the inlet end, and wherein the plurality of spiral grooves are formed by overlapping the inner surfaces of adjacently arranged plurality of vanes.

9. The compressor according to claim 1, further comprising a channel arranged in the inlet duct upstream of the impeller and downstream of the inlet end of the VID, wherein the channel extends outward from the central axis so that an inner wall of the inlet duct in the area of the channel is located farther away from the central axis than the inner wall of the inlet duct in the area of the inlet duct arranged upstream of the inlet end of the VID.

10. A method for a compressor, comprising: a variable inlet device (VID) positioned in and across an inlet duct of the compressor upstream of an impeller, regulating between an open position and a closed position in response to engine operation relative to a surge threshold of the compressor, wherein in the open position an inner surface of the VID does not restrict flow through the VID from an inlet end to an outlet end of the VID, and wherein in the closed position the inner surface narrows along a length of the VID and creates a swirling flow at the outlet end of the VID, wherein the VID includes a plurality of adjacently arranged blades forming a ring about a central axis of the compressor, wherein inner surfaces of the plurality of adjacently arranged blades form the inner surface of the VID and a flow path through the VID, and wherein each blade of the plurality of adjacently arranged blades includes an inlet end and an outlet end, the inlet end being arranged in the inlet duct upstream of the outlet end, wherein adjusting the VID between the open position and the closed position comprises passively adjusting the VID between the open position and the closed position via an actuation port disposed in a wall of the inlet duct between the inlet duct upstream of the VID and downstream of a leading edge of the impeller and a recirculation passage surrounding and in fluid communication with the inlet duct, wherein the actuation port is positioned between the inlet end and the outlet end of the VID adjacent to outer surfaces of the plurality of adjacently arranged vanes.

11. The method of claim 10, wherein adjusting the VID between the open position and the closed position comprises adjusting the VID from the open position to the closed position in response to an engine in which the compressor is installed transitioning to operation at an engine speed and engine load below the surge threshold, and wherein adjusting the VID from the open position to the closed position comprises pivoting each vane such that the outlet end of each vane pivots toward the central axis.

12. The method of claim 10 , wherein adjusting the VID between the open position and the closed position comprises adjusting the VID from the closed position to the open position in response to an engine in which the compressor is installed transitioning to operation at an engine speed and engine load above the surge threshold, and wherein adjusting the VID from the closed position to the open position comprises pivoting each vane such that the outlet end of each vane pivots away from the central axis and toward the inlet duct inner wall, wherein pivoting each vane away from the central axis comprises reducing an overlap of the plurality of adjacently arranged vanes at the outlet end of the VID and increasing a diameter of the outlet end of the VID.

Images