Active casing handling device with movable sleeve

Abstract

The present disclosure provides an "active casing treatment device equipped with a movable sleeve". A method and system for a compressor are provided, the compressor being equipped with a movable sleeve and an active casing treatment device that form a separate airflow chamber. In one example, a method includes: allowing intake air to flow through a casing in a first direction to an impeller of a compressor; selectively allowing intake air to flow from the casing in an opposite second direction through a first chamber, the first chamber circumferentially surrounding the casing; and selectively allowing intake air to flow through a second chamber in the first direction to the impeller, the second chamber circumferentially surrounding the first chamber. In this way, at higher air flow rates, compressor surge can be reduced without reducing compressor efficiency.

Description

Technical Field

[0001] The present description generally relates to methods and systems for controlling a vehicle engine to reduce noise emitted during surge recirculation flow.

[0002] Background technology / invention content

[0003] By incorporating a turbocharger into a vehicle's engine, the efficiency and power output of the engine can be improved. Forcing additional air into the engine's combustion chambers will proportionally induce the combustion of additional fuel, thereby producing more power than is available from the intake air at ambient pressure. A turbocharger may include an exhaust-driven turbine coupled to a compressor via a drive shaft. The compressor may be fluidly coupled to an intake manifold in the engine, the intake manifold being connected to a plurality of engine cylinders that produce exhaust gas during combustion, which may be directed to a turbine wheel, thereby driving the rotation of the turbine, and in turn driving the rotation of the compressor. The use of a compressor allows a smaller displacement engine to provide as much power as a larger displacement engine, but with additional fuel economy benefits.

[0004] However, compressors are susceptible to surge and blockage. For example, when the driver releases the accelerator pedal, airflow is reduced, resulting in less forward flow passing through the compressor at a high pressure ratio (PR), which may cause compressor surge. In another example, surge may be caused in part by high levels of cooled exhaust gas recirculation (EGR), which increases compressor pressure while reducing mass flow through the compressor. Compressor surge may cause NVH issues, such as unwanted noise from the engine's intake system.

[0005] Compressor clogging may be encountered at high flows when an increase in compressor speed causes a decreasing increase in flow rate. When the flow at any point in the compressor reaches a clogging condition, no further flow rate increases are possible. This condition represents a change in the maximum compressor volumetric flow rate as a function of the pressure ratio. Clogging occurs when the mass of airflow through the compressor cannot be increased for a given speed of the compressor. The flow rate in the compressor may be limited by the size of the compressor inlet, and when the flow at the inlet reaches the speed of sound, it may not be possible to increase the flow further. As an example, clogging may occur when the driver steps from a part load or idle condition to a high load condition, such as when going uphill with a load.

[0006] Various methods have been developed to address the problem of compressor inefficiency that causes surge, including providing a recirculation path for the airflow. Horner et al. show an example method in US6,648,594B1. Therein, a compressor housing is disclosed, the compressor housing forming an active sleeve treatment device, the active sleeve treatment device having multiple bypass channels that act as shortcuts for airflow. The channel is fluidly connected to an intake duct that is separated from the main air inlet of the compressor by the compressor housing. The airflow through the channel is controlled by a slidable or rotatable sleeve. In order to reduce compressor surge, the sleeve can be adjusted to open a slot that allows recirculation in the intake duct to allow air to flow from the compressor impeller to the compressor inlet. At high engine speeds, additional air can enter the compressor through the intake duct to reach the compressor impeller, thereby preventing engine blockage.

[0007] However, the inventors herein have recognized potential problems with such systems. As an example, during light engine loads near the surge limit, undesirable noise generated by oscillations of the airflow may occur. The noise may be suppressed by providing a recirculation path in an active casing treatment device with a damping element such as a deflector or baffle. However, incorporating such structure in the recirculation path may impede airflow during high engine operating loads near or in the plugged region of compressor operation. To prevent turbocharger plugging, it is desirable to have high volume airflow through the flow path in a direction opposite to the surge recirculation flow, but the presence of the noise suppression element may restrict the flow, making the active casing treatment device's response to avoid conditions that lead to compressor plugging less effective.

[0008] Another potential problem with active sleeve handling devices such as those described above arises from situations where the removable sleeve may become stuck. Over time, particulates and other matter may infiltrate the space between the removable sleeve and the compressor sleeve, causing the sleeve to stick to the sleeve and obstructing operation of the sleeve. This may result in erratic operation of the compressor and, depending on where the fixed sleeve is located, may increase the likelihood of turbocharger surge or plugging.

[0009] In one example, the problem described above can be solved by a method comprising: flowing intake air through a sleeve in a first direction to an impeller of a compressor; selectively flowing intake air from the sleeve in an opposite second direction through a first chamber, the first chamber circumferentially surrounding the sleeve; and selectively flowing intake air in the first direction through a second chamber to the impeller, the second chamber circumferentially surrounding the first chamber. In this way, noise generated during low engine speeds and light engine loads can be minimized without adversely affecting high volume flow during heavy engine loads.

[0010] As an example, an active casing treatment device for a compressor inlet is configured with a movable sleeve. By sliding the sleeve axially along the compressor casing in which the active casing treatment device is disposed, the sleeve can alternate between opening a discharge port of the active casing treatment device while closing an injection port, or closing the discharge port while opening the injection port. The discharge port includes an opening to a first chamber disposed between the compressor casing and the movable sleeve, and the injection port includes an opening to a second chamber disposed between the movable sleeve and the compressor housing. The discharge port fluidically couples the first chamber to an internal passage of airflow passing through the compressor inlet. Similarly, the injection port fluidically couples the second chamber to an internal passage of the compressor inlet. The first chamber may include a noise deflector or baffle to mitigate noise caused by surging flow, while such structures may not be present in the second chamber.

[0011] The movement of the sleeve is controlled by an actuating mechanism that displaces the sleeve axially to adjust the flow between the discharge port and the injection port. The mechanism may also rotationally move the sleeve to prevent the sleeve from sticking to the compressor casing. The actuating mechanism may be configured with a chain link that enables the motor of the actuating mechanism to be positioned outside the compressor housing while still participating in the movement of the movable sleeve. The movement of the chain link as controlled by the motor is converted into adjustment of the position of the movable sleeve relative to the discharge port and the injection port.

[0012] In this way, by providing separate recirculation paths for compressor operation outside of surge and plugging limits, undesirable noise during light load engine operation can be effectively suppressed without reducing compressor efficiency during higher end engine operation. Sticking of the sleeve to the compressor sleeve is prevented by minimizing the contact surface that butts against a surface formed by three or more ribs spaced circumferentially around the sleeve and a continuous surface at the end of the cover port. The axial contact length of the ribs provides stability to prevent the sleeve from becoming misaligned on the sleeve and binding. The relatively small contact area inhibits the accumulation of material between the sleeve and the sleeve. The technical effect of configuring the active sleeve treatment device with separate surge and plugging recirculation paths is to maintain the extension of the surge and plugging limits while including additional features of the active sleeve treatment device, such as noise suppression.

[0013] It should be understood that the above summary is provided to introduce in simplified form selected concepts that are further described in the detailed description. This is not intended to identify key or essential features of the claimed subject matter, the scope of which is uniquely defined by the claims that follow the detailed description. Furthermore, the claimed subject matter is not limited to implementations that solve any disadvantages mentioned above or in any part of this disclosure. BRIEF DESCRIPTION OF THE DRAWINGS

[0014] Figure 1An example engine system for a vehicle is shown.

[0015] Figure 2A A cross-sectional view of a compressor inlet with an active casing handling device and a movable sleeve is shown, with the discharge port open to flow.

[0016] Figure 2B A cross-sectional view of a compressor inlet with an active casing handling device and a removable sleeve is shown, wherein the injection port is open to flow.

[0017] Figure 3 An isometric perspective view of the compressor inlet is shown with the movable sleeve connected to the rotary actuator.

[0018] Figure 4A A side view of a movable sleeve connected to a link of a rotary actuator is shown in a first position.

[0019] Figure 4B A side view of a movable sleeve connected to a link of a rotary actuator is shown in a second position.

[0020] Figure 5 A front view of the compressor inlet is shown, with the movable sleeve connected to the first branch of the chain link of the rotary actuator.

[0021] Fig. 6A A schematic diagram of a movable sleeve connected to a rotary actuator via a chain link is shown in a first position.

[0022] Figure 6B A schematic diagram of a movable sleeve connected to a rotary actuator via a chain link is shown in a second position.

[0023] Fig. 7A A schematic diagram of a movable sleeve connected to a linear actuator via a chain link is shown in a first position.

[0024] Figure 7B A schematic diagram of a movable sleeve connected to a linear actuator via a chain link is shown in a second position.

[0025] Figure 8 A flow chart of an example method of operating an active sleeve handling device coupled to a movable sleeve is presented.

[0026] Fig. 9 An example compressor performance map is shown.

[0027] Figure 2 to Figure 4B Shown approximately to scale. DETAILED DESCRIPTION

[0028] The following description relates to systems and methods for controlling the operation of an active casing treatment device of a turbocharger compressor to reduce the occurrence of surge and plugging. Figure 1 A non-limiting embodiment of a hybrid vehicle system including a turbocharged engine is shown in FIG. A turbocharged engine may utilize an exhaust turbine driven compressor that may be positioned in the intake tract of the engine. FIG. 2A to FIG. 2B As shown, the compressor may include a casing having an inlet duct (e.g., an air intake duct) surrounding a casing and an impeller (e.g., a compressor impeller) disposed at a downstream end of the casing. The impeller may include one or more blades and may be rotatable about a central axis of the compressor. The compressor may be equipped with an active casing treatment device, the active casing treatment device including a plurality of ports disposed in a wall of the casing, providing an alternative path for air circulation to avoid compressor surge and blockage. A movable sleeve configured to slide axially to align with each of the plurality of ports may circumferentially surround the casing disposed in the inlet duct. A first chamber coupled to a discharge port of the active casing treatment device is disposed between an inner surface of the movable sleeve and an outer surface of the compressor casing, and may constitute a first circulation path for air recirculation during light engine loads. A second chamber coupled to an injection port of the active casing treatment device may be formed between an outer surface of the movable sleeve and an inner surface of the compressor casing, thereby acting as a second circulation path for injecting air into the outlet end of the compressor during high engine loads. The sliding of the movable sleeve may be by Figure 3 The movable sleeve is controlled by an actuation mechanism shown, which includes connecting elements or links that drive the axial and rotational movement of the movable sleeve. Figure 4A and Figure 4B The pivoting of the chain link that translates into axial and rotational sliding of the movable sleeve is shown in FIG. Figure 5 The attachment of the chain link to the outer surface of the movable sleeve relative to the central axis of the compressor is shown from a front view. FIG. 6A to FIG. 6B FIG. 4 shows the adjustment of the movable sleeve between the first position and the second position as performed by the rotary actuator. FIG. 7A to FIG. 7B As shown, the linear actuator can similarly slide the movable sleeve between the first position and the second position. Figure 8 As shown, the positioning of the movable sleeve relative to the plurality of ports may be based on compressor surge and blockage conditions, for example, based on Fig. 9 In this way, in addition to avoiding engine surge and blockage, the active sleeve treatment device equipped with a movable sleeve can also be used to reduce undesirable noise during light engine loads.

[0029] Reference will be made to compressor operating limits throughout the following detailed description and may be made in conjunction with Fig. 9The compressor performance diagram shown is used to illustrate the compressor operating limits. Fig. 9 The flow rate in the compressor is shown to vary with the pressure ratio across the compressor. The surge limit marks the lower limit airflow for compressor operation, while the blockage limit defines the upper limit airflow. For example, dashed line 902 represents the lower limit boundary as the surge limit, and the upper limit indicated by dashed line 904 represents the blockage limit. Compressor surge may occur during low compressor flow conditions, such as during a rapid engine unloading event, during which the turbine continues to rotate at a relatively high speed, thereby pressurizing the air downstream of the compressor. This causes a high pressure area to form at the outlet of the compressor, thereby driving a reversal of the direction of airflow, which may cause degradation of the turbocharger. The compressor operating efficiency - as shown by the curve marked with percentages - decreases as the operating point approaches the surge limit. Operating in the area to the left of dashed line 902 may result in compressor surge and even lower efficiency (e.g., at relatively low compressor mass flows and medium to high pressure ratios). Moving the surge line to the left can improve the compressor operating efficiency for a given operating point.

[0030] Operation beyond the upper boundary of the compressor pressure ratio relative to mass flow (e.g., in the region defined by relatively high compressor mass flow and relatively low pressure ratio to the right of dashed line 904) can result in turbocharger plugging. Blockage may occur during a transient overspeed event where, for example, an increase in engine load subjects the turbocharger to a flow that exceeds the turbocharger's tolerance capabilities. The rotational speed of the turbine driving the compressor may be higher than the maximum design speed of the turbocharger. Repeated occurrences of turbocharger plugging may also cause degradation of the turbocharger and / or limit engine torque.

[0031] Now turn Figure 1 , an example of cylinder 14 of internal combustion engine 10 is shown, which may be included in vehicle 5. Engine 10 may be controlled at least in part by a control system including controller 12 and by input from a vehicle driver 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 piston 138 positioned therein. Piston 138 may be coupled to crankshaft 140 such that reciprocating motion of the piston is converted into rotational motion of the crankshaft. As further described below, crankshaft 140 may be coupled to at least one drive wheel 55 of a passenger vehicle via transmission 54. Additionally, a starter motor (not shown) may be coupled to crankshaft 140 via a flywheel to enable a starting operation of engine 10.

[0032] In some examples, the vehicle 5 may be a hybrid vehicle having multiple torque sources available for one or more wheels 55. In other examples, the vehicle 5 is a conventional vehicle having only an engine. In the example shown, the vehicle 5 includes an engine 10 and an electric motor 52. The electric motor 52 may be a motor or a motor / generator. When one or more clutches 56 are engaged, the crankshaft 140 of the engine 10 and the electric motor 52 are connected to the wheels 55 via a transmission 54. In the example shown, a first clutch 56 is provided between the crankshaft 140 and the electric motor 52, and a second clutch 56 is provided between the electric motor 52 and the transmission 54. The controller 12 may send a signal to the actuator of each clutch 56 to engage or release the clutch so as to connect or disconnect the crankshaft 140 with the electric motor 52 and the components connected thereto, and / or to connect or disconnect the electric motor 52 with the transmission 54 and the components connected thereto. The transmission 54 may be a gearbox, a planetary gear system, or another type of transmission. The powertrain may be configured in various ways including hybrid vehicles such as parallel, series, or series-parallel.

[0033] The electric machine 52 receives power from the traction battery 58 to provide torque to the wheels 55. The electric machine 52 may also operate as a generator to provide power to charge the battery 58, such as during braking operations.

[0034] Cylinder 14 of engine 10 may receive intake air via a series of intake passages 142, 144, and 146. Intake passage 146 may 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 1 Engine 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 be optionally omitted.

[0035] A throttle 162 including a throttle plate 164 may be provided in the engine intake passage to vary the flow rate and / or pressure of intake air provided to the engine cylinders. For example, the throttle 162 may be provided as Figure 1 It is shown positioned downstream of compressor 174 , or may alternatively be provided upstream of compressor 174 .

[0036] Exhaust passage 148 may 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. For example, 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 shown), HEGO (Heated EGO), nitrogen oxides (NOx), hydrocarbons (HC), or carbon oxides (CO) sensors. Emission control device 178 may be a three-way catalyst, a NOx trap, various other emission control devices, or combinations thereof.

[0037] Each cylinder of engine 10 may include one or more intake valves and one or more exhaust valves. For example, cylinder 14 is shown as including at least one intake poppet valve 150 and at least one exhaust poppet valve 156 located in an upper region of cylinder 14. In some examples, each cylinder of engine 10 including cylinder 14 may include at least two intake poppet valves and at least two exhaust poppet valves located in 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 corresponding valve position sensors (not shown).

[0038] In some cases, the controller 12 can change the signal provided to the actuators 152 and 154 to control the opening and closing of the corresponding intake valve and exhaust valve. The valve actuator can be an electric valve actuation type, a cam actuation type, or a combination thereof. The intake valve and exhaust valve timing can be controlled simultaneously, or any possible one of variable intake cam timing, variable exhaust cam timing, dual independent variable cam timing, or fixed cam timing can be used. Each cam actuation system may include one or more cams, and the valve operation can be changed using one or more of the cam profile conversion system (CPS), variable cam timing (VCT), variable valve timing (VVT), and / or variable valve lift (VVL) systems that can be operated by the controller 12. For example, the cylinder 14 may alternatively include an intake valve controlled via electric valve actuation and an exhaust valve controlled via a cam actuation including CPS and / or VCT. In other examples, 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).

[0039] Cylinder 14 may have a compression ratio, which is the ratio of volumes when piston 138 is at bottom dead center (BDC) to top dead center (TDC). In one example, the 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 high 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.

[0040] In some examples, each cylinder of engine 10 may include a spark plug 192 for starting combustion. Ignition system 190 may provide an ignition spark to combustion chamber 14 via spark plug 192 in response to a spark advance signal SA from controller 12 in a selected operating mode. The timing of signal SA may be adjusted based on engine operating conditions and driver torque requirements. For example, a spark may be provided at maximum brake torque (MBT) timing to maximize engine power and efficiency. Controller 12 may input engine operating conditions including engine speed, engine load, and exhaust AFR into a lookup table, and output corresponding MBT timing for the input engine operating conditions. In other examples, the engine may ignite the charge by compression as in a diesel engine.

[0041] In some examples, each cylinder of engine 10 may be configured with one or more fuel injectors for providing fuel thereto. As a non-limiting example, cylinder 14 is shown as 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 fuel rails. Fuel injector 166 is shown as being directly coupled to cylinder 14 to inject fuel directly into the cylinder in proportion to the pulse width of signal FPW-1 received from controller 12 via electronic driver 168. In this manner, fuel injector 166 provides a fuel injection referred to as direct injection of fuel into cylinder 14 (hereinafter also referred to as "DI"). Although Figure 1 Fuel injector 166 is shown positioned on one side of cylinder 14, but may alternatively be located on top of the piston, such as near the location of spark plug 192. Such a location may increase mixing and combustion when the engine is operated with alcohol-based fuels due to the lower volatility of some alcohol-based fuels. Alternatively, the injector may be located on top of and near the intake valve to increase 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. Additionally, the fuel tank may have a pressure sensor that provides a signal to controller 12.

[0042] Fuel injector 170 is shown arranged in intake passage 146, rather than in cylinder 14, in a configuration that provides what is known as port fuel injection (hereinafter referred to as "PFI") into the intake port upstream of cylinder 14. Fuel injector 170 may inject fuel received from fuel system 8 in proportion to the pulse width of signal FPW-2 received from controller 12 via electronic driver 171. It should be noted that a single driver 168 or 171 may be used for both fuel injection systems, or as shown, multiple drivers may be used, such as driver 168 for fuel injector 166 and driver 171 for fuel injector 170.

[0043] In an alternative example, each of fuel injectors 166 and 170 may be configured as a direct fuel injector for injecting fuel directly into cylinder 14. In another example, each of fuel injectors 166 and 170 may be configured as a port fuel injector for injecting fuel upstream of intake valve 150. In other examples, cylinder 14 may include only a single fuel injector configured to receive different fuels in varying relative amounts from a fuel system as a fuel mixture and further configured to inject such a fuel mixture directly into the cylinder as a direct fuel injector or to inject the fuel mixture upstream of the intake valve as a port fuel injector.

[0044] Fuel can be delivered to the cylinder by two injectors during a single cycle of the cylinder. For example, each injector can deliver a portion of the total fuel injection burned in cylinder 14. In addition, the distribution and / or relative amount of the fuel delivered from each injector can vary with operating conditions, such as engine load, knock and exhaust temperature, as described below in this article. The fuel injected by the port can be delivered during an open intake valve event, a closed intake valve event (e.g., substantially before the intake stroke), and during both open and closed intake valve operations. Similarly, for example, the directly injected fuel can be delivered during the intake stroke, and partially during the previous exhaust stroke, during the intake stroke, and partially during the compression stroke. Therefore, even for a single combustion event, the injected fuel can be injected from the port injector and the direct injector at different times. In addition, for a single combustion event, multiple injections of the delivered fuel can be performed in each cycle. Multiple injections can be performed during the compression stroke, the intake stroke, or any suitable combination thereof.

[0045] Fuel injectors 166 and 170 may have different characteristics. These characteristics include differences in size, for example, one injector may have a larger injection hole than the other injectors. Other differences include, but are not limited to: different injection angles, different operating temperatures, different targets, different injection timings, different injection characteristics, different locations, etc. In addition, depending on the distribution ratio of the injected fuel in injectors 170 and 166, different effects may be achieved.

[0046] The fuel tank in the fuel system 8 can accommodate fuels of different fuel types, such as fuels with different fuel qualities and different fuel components. These differences can include different alcohol contents, different water contents, different octane numbers, different heats of vaporization, different mixed fuels and / or combinations thereof, etc. An example of fuels with different heats of vaporization can include gasoline as a first fuel type with a lower heat of vaporization and ethanol as a second fuel type with a higher heat of vaporization. In another example, the engine can use gasoline as the first fuel type and use alcohol containing a mixed fuel such as E85 (which is close to 85% ethanol and 15% gasoline) or M85 (which is close to 85% methanol and 15% gasoline) as the second fuel type. Other feasible substances include water, methanol, a mixture of alcohol and water, a mixture of water and methanol, a mixture of alcohol, etc.

[0047] The controller 12 Figure 11 is shown as a microcomputer that includes a microprocessor unit 106, an input / output port 108, an electronic storage medium for executable programs (e.g., executable instructions) and calibration values ​​- in this particular example shown as a non-transitory read-only memory chip 110, a random access memory 112, a keep alive memory 114, and a data bus. Controller 12 may receive various signals from sensors coupled to engine 10, including the signals previously discussed and in addition including: a measurement of intake mass air flow (MAF) from mass air flow 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; surface ignition sensing signal (PIP) from Hall effect sensor 120 (or other type of sensor) coupled to crankshaft 140; throttle position (TP) from throttle position sensor; signal EGO from exhaust gas sensor 128, which may be used by controller 12 to determine AFR of the exhaust; and manifold absolute pressure signal (MAP) from MAP sensor 124. Engine speed signal RPM may be generated by controller 12 based on 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 the temperature of catalyst 178 based on signals received from temperature sensor 158 .

[0048] The controller 12 is Figure 1 Various sensors receive signals and use Figure 1 The various actuators of the engine controller may adjust the engine operation based on the received signals and the instructions stored in the memory of the controller. For example, after receiving the signals from the various sensors, the engine controller may send control signals to the actuators to shift the position of the movable sleeve relative to the active sleeve treatment device. The signals may notify the actuators of the movable sleeve arranged along the inlet duct of the compressor 174 to open or close multiple ports disposed in the active sleeve treatment device in response to the current engine speed and engine load relative to the surge threshold and / or the blockage threshold of the compressor (as described below with reference to Figure 8 further explanation).

[0049] As mentioned above, Figure 1 Only one cylinder of a multi-cylinder engine is shown. Thus, each cylinder may similarly include its own set of intake / exhaust valves, fuel injectors, spark plugs, etc. It will be appreciated that engine 10 may include any suitable number of cylinders, including 2, 3, 4, 5, 6, 8, 10, 12, or more cylinders. Additionally, each of these cylinders may include Figure 1Some or all of the various components described and shown with reference to cylinder 14 .

[0050] refer to Figure 1 In the case of an engine 10 and a compressor 174, the performance of the engine may be related to the efficiency of the compressor. The ability of the compressor to operate between the surge threshold and the clogging threshold may affect the stability of the engine during low speeds and the power output obtained from the combustion of the charge air. FIG. 2A to FIG. 2B The active casing treatment device shown in detail in can relieve pressure buildup at the outlet of the compressor by recirculating air to the inlet duct during low engine speed and fired operation. During heavier loads and higher engine speeds, the active casing treatment device can provide an additional path for airflow to reach the compressor over the leading edge of the compressor impeller.

[0051] Figure 2A A first view 200 of a compressor 202 is shown, and Figure 2B A second view 201 of a compressor 202 is shown. The compressor 202 is Figure 1 The compressor 202 includes a central axis 208 about which the impeller 203 can rotate. The central axis 208 can also be the central axis of the inlet duct 210 of the compressor 202 defined by the casing 238 of the compressor. The airflow (e.g., from a compressor such as a compressor 202) entering the compressor 202 via the inlet duct 210 Figure 1 The inlet of the inlet duct 142 of the air intake) is indicated by arrow 212, which can also be a reference for positioning elements relative to each other. Elements in the air flow path with respect to a reference point are considered to be downstream of the reference point, and elements in the air flow path before the reference point are considered to be upstream of the reference point. For example, the inlet duct 210 is upstream of the impeller 203, and the impeller 203 is downstream of the inlet duct 210.

[0052] The impeller 203 may have a plurality of impeller blades 216 and may be connected to a turbine such as a turbine 210 via a shaft 218 that drives the rotation of the impeller 203. Figure 1 The outlet end of the compressor 202 may be defined as the element of the compressor 202 positioned downstream of the leading edge 232 of the impeller 203. The air drawn into the compressor 202 by the rotation of the impeller 203 is accelerated through the diffuser 220 and collected in the volute 222. The deceleration of the airflow in the volute 222 may cause an increase in the pressure in the volute 222, thereby causing the airflow to flow to the intake manifold.

[0053] The compressor 202 may include an active casing treatment device 204 and a movable sleeve 206. The active casing treatment device 204 may include a casing 205 surrounding a portion of the impeller 203 upstream of the leading edge 232, and an internal passage 214 formed within a cavity of the casing 205. Air flowing into the inlet duct 210 passes through the internal passage 214 of the casing 205 positioned within the inlet duct 210 (centered about the central axis 208) toward the downstream end of the internal passage 214 where the impeller 203 is positioned.

[0054] The active sleeve treatment device 204 may include a plurality of ports including a drain port 228 and an injection port 230 positioned downstream of the drain port 228, thereby forming a passage through the sleeve 205. The sleeve 205 may be a substantially cylindrical structure having openings at a first end 224 and a second end 226. Both the drain port 228 and the injection port 230 are disposed at the second end 226 of the active sleeve treatment device 204. The drain port 228 and the injection port 230 may not be continuous around the circumference of the sleeve, but may be interrupted by one or more ribs 246 that connect the sleeve upstream of the second end 226 to the outlet end of the compressor casing. Thus, each of the drain port 228 and the injection port 230 may include a plurality of ports arranged around the circumference of the sleeve 205.

[0055] The width of the injection port 230 measured along the central axis 208 may be greater than the width of the discharge port 228. The discharge port 228 and the injection port 230 are arranged downstream of the leading edge 232 of the impeller 203, and each port fluidly couples the internal passage 214 of the sleeve 205 to one of two chambers positioned outside the sleeve 205. In particular, the injection port 230 fluidly couples the internal passage 214 to a first chamber 234 formed between the outer surface of the sleeve 205 and the inner surface of the movable sleeve 206. The discharge port 228 fluidly couples the internal passage 214 to a second chamber 236 positioned between the outer surface of the movable sleeve 206 and the inner surface of the compressor housing 238.

[0056] As described in detail below, during conditions where compressor surge may occur, such as under low mass flow conditions, the active sleeve treatment device 204 can enable gas to flow from the second end 226 of the internal passage 214 through the discharge port 228 into the first chamber 234. The gas further continues from the first chamber 234 into the first end 224 of the internal passage 214. Thus, when the discharge port is open, the flow of gas striking the leading edge 232 of the impeller 203 can be greater than the flow of gas flowing through the internal passage 214 to the leading edge 232 without additional gas flow through the discharge port 228 (e.g., when the discharge port is blocked). The flow of additional recirculated gas can enable the turbocharger compressor to operate with less gas flow through the intake duct 210 before surge occurs.

[0057] The first chamber 234 may include noise deflecting elements, such as a plurality of protrusions extending radially from the outer surface of the sleeve 205 into the first chamber 234. Alternatively, the noise generated during the recirculation flow may be suppressed by a single noise deflector attached to the outer surface of the sleeve 205, which is bent into the airflow path. In other examples, the noise generated by flowing through the first chamber 234 may be reduced by configuring the first chamber 234 with a structure that changes the volume of the first chamber 234 or the speed of the airflow passing therethrough.

[0058] During conditions where compressor plugging may occur, such as under high mass flow conditions, the active casing treatment device 204 may enable gas to flow in the same direction as through the internal passage 214, but through an alternate path via the second chamber 236 and the injection port 230 to reach the impeller 203. During high mass flow conditions, a low pressure region may exist in the internal passage 214 adjacent to the injection port 230, downstream of the leading edge of the impeller 203. The low pressure region may induce gas to flow from the inlet duct 210 through the second chamber 236 and then to the impeller 203 via the injection port 230. Under high mass flow conditions, the path in the second chamber 236 may enable gas flow through the compressor 202 to be increased when compared to a compressor without the injection port 230. In this way, the additional gas flow may enable more gas to be delivered to the compressor 202 before the compressor plugs and / or may alleviate plugged flow.

[0059] The movable sleeve 206 can be adapted to circumferentially surround the sleeve 205 and separate the first chamber 234 from the second chamber 236. The movable sleeve 206 is a cylindrical structure having a first end 240 and a second end 242, both of which are bent inwardly toward the central axis 208 such that a central portion 244 of the movable sleeve 206 is spaced apart from an outer surface of the sleeve 205. The inner surface of the movable sleeve 206 can also include ribs 246 arranged along the central portion 244, which protrude into the first chamber 234. The ribs can contact the sleeve 205 to maintain the concentric alignment of the sleeve 206 with the sleeve 205.

[0060] The first chamber 234 is formed by the space between the movable sleeve 206 and the sleeve 205, and can be smaller than the second chamber 236. In particular, the internal volume of the first chamber 234 (which is further reduced due to the arrangement of the ribs 246 therein) and the length, diameter, and circumference of the first chamber 234 can each be smaller than those of the second chamber 236. The internal volume of the first chamber 234 can also be smaller than the internal volume of the sleeve 205, and thus the amount of air that can flow through the first chamber can be less than the amount that flows through the internal passage 214 of the sleeve 205. In contrast, the second chamber 236 can have an internal volume that is larger than the internal volume of the first chamber 234 but smaller than the internal volume of the sleeve 205, thereby allowing less air to flow through the second chamber than through the internal passage 214, at least during some conditions.

[0061] By changing the position of the movable sleeve 206 relative to the sleeve 205, airflow can be directed through the first chamber 234 or the second chamber 236. The movable sleeve 206 can be configured to extend axially along the central axis 208 so that the first end 240 of the movable sleeve 206 is upstream of the first end 224 of the sleeve 205. When actuated to move in accordance with engine operation, the second end 242 of the movable sleeve 206 can be positioned in a manner such as Figure 2A As shown, the injection port 230 is aligned with the Figure 2B As movable sleeve 206 is axially displaced, second end 242 slides along the outer surface of sleeve 205 and seals either drain port 228 or injection port 230, thereby preventing flow between internal passage 214 and first chamber 234 or second chamber 236, respectively.

[0062] In this manner, the movable sleeve 206 in combination with the active sleeve treatment device 204 can prevent both compressor surge and plugging by allowing airflow to pass through a passage in the inlet duct 210 disposed adjacent to the impeller 203 at the downstream end of the sleeve 205. The shape of the movable sleeve 206 having the second end 242 bent inwardly toward the sleeve 205 allows the second end 242 to make coplanar contact with the outer surface of the sleeve 205. For example, the second end 242 includes a face extending coaxially with the axis 208 in a cylindrical manner, the face contacting the outer surface of the sleeve 205 (e.g., sharing a face therewith). When the movable sleeve 206 is in Figure 2A In the first position shown, the face is sized to prevent fluid coupling between the injection port 230 and the second chamber 236, or when the movable sleeve 206 is in the Figure 2B In the second position shown, fluid coupling between the discharge port 228 and the first chamber 234 is blocked. In this manner, the movable sleeve 206 can alternate between sealing the discharge port 228 or the injection port 230 when positioned accordingly. Adjustment of the movable sleeve 206 specific to each of the lower and upper limits of compressor operation is further described below.

[0063] The movable sleeve 206 can be moved to Figure 2A The position shown, where Fig. 9 As shown in the compressor performance diagram, in compressor operation at or beyond the lower surge limit (e.g., to the left of the surge limit), the second end 242 blocks the injection port 230. As a non-limiting example, operating the engine at a relatively high load and low engine speed may cause the compressor 202 to operate at the surge limit or in the surge region. Pressure may accumulate at the outlet end of the compressor 202 and force the airflow to reverse. This reversal may cause degradation of the turbocharger, and the pressurized air may be forced to discharge through the inlet duct 210 with greater vibration.

[0064] To mitigate the formation of the high pressure region, air may be recirculated through the first chamber 234 in the opposite direction to that of flowing through the internal passage 214 as indicated by arrows 248. Air flows from the area adjacent to the impeller 203 through the discharge port 228 to return to the first end 224 of the sleeve 205. The airflow then continues to re-enter the internal passage 214 to flow once again to the impeller 203. The discharge port 228 thus acts as a vent to "drain" the additional pressure that builds up at the outlet end of the compressor 202 when operating below the surge limit of the compressor. The arrangement of the leading edge 240 of the sleeve limits and dampens the oscillations of the surge flow so that noise is minimized and redirected into the compressor rather than released upstream into the atmosphere.

[0065] Compared to the internal passage 214 of the sleeve 205, the relatively narrow discharge port 228 and the small internal volume of the first chamber 234 can restrict the flow through the first chamber 234 to a small portion of the total airflow through the compressor 202. In one example, when the movable sleeve 206 is adjusted to open the discharge port 228 and close the injection port 230, 5% of the air flowing to the impeller 203 is recirculated through the discharge port. As another example, the fraction of flow recirculated through the discharge port 228 can be 2%, 10%, or 15% of the total flow through the compressor. By incorporating ribs 246 in the flow path, the flow is further restricted in the first chamber 234. During certain engine operations, such as cruising or acceleration, the discharge port 228 remains open and maintains pressure balance across the compressor by achieving a slow and constant recirculation of air.

[0066] In contrast, during conditions that push the compressor close to or beyond the clogging limit, the movable sleeve 206 is actuated to Figure 2B The position shown. Conditions that lead to turbocharger blockage may include a sudden increase in engine load, a degraded wastegate, an engine / turbocharger mismatch, etc. In the case where the exhaust port 228 is sealed by the second end 224 of the movable sleeve 206, the recirculation of air through the first chamber 234 is blocked. Air enters the inlet duct 210, thereby flowing through the internal passage 214 to the impeller 203, wherein an additional amount of air is delivered to the area adjacent to the impeller 203 via the second chamber 236 (after arrow 250) and the injection port 230. The injection port 230 is located in an area that often experiences low pressure during high flow, and the low pressure helps to draw air into the second chamber 236 toward the injection port 230. In addition, the second chamber 236 has an internal volume larger than the first chamber 234 as described above, and the width of the injection port 230 can be configured so that enough additional air can be directed through the second chamber 236 and the injection port 230 to effectively deliver the required airflow to the intake manifold of the engine.

[0067] By providing an alternate path through the second chamber 236 and the injection port 230 that is separate from the surge recirculation route (including the discharge port 228 and the first chamber 234), a faster and higher volume airflow for mitigating turbocharger plugging is achieved during compressor operation at or beyond a preset plugging limit. The sonic velocity of air flowing through the internal passage 214 of the compressor 202 that often causes compressor plugging can be mitigated by providing additional airflow to the area adjacent to the impeller 203 in the same direction as the flow through the internal passage 214 of the casing 205. In summary, FIG. 2A to FIG. 2BThe active sleeve treatment device 204 and movable sleeve 206 improve the efficiency and performance of the compressor 202 by extending surge and blockage limits and enhance the vehicle passenger experience by reducing noise during light engine loads.

[0068] The adjustment of the alignment of the movable sleeve with the elements of the active sleeve handling device described above may be achieved by coupling the movable sleeve with an actuation device. Figure 3 An example of such a device is shown in FIG. 1 , which shows a rotary actuator 306 coupled to a movable sleeve 206. FIG. 2A to FIG. 2B The compressor 202. FIG. 2A to FIG. 2B The movable sleeve 206 includes a central axis 208, which may also be the central axis of the compressor 202, the impeller ( Figure 3 The central axis 208 may be rotatable about the central axis (e.g., the central axis 208 is the axis of rotation of the impeller). The direction of the airflow into the inlet duct 210 of the compressor 202 is shown by arrow 212. Figures 3 to 7B Comparison between the illustrated views provides a set of reference axes 302 indicating a "y" vertical direction, an "x" horizontal direction, and a "z" lateral direction.

[0069] The movable sleeve 206 may be a cylindrical housing configured to surround the casing ( Figure 3 206). The length of the movable sleeve 206, as defined in a transverse direction to the reference axis 302, extends axially along the inlet duct 210. The movable sleeve is spaced apart from the inner surface of the compressor housing 238, which circumferentially surrounds both the inlet duct 210 and the movable sleeve 206. The space between the inner surface of the compressor housing 238 and the outer surface of the movable sleeve 206 forms a second chamber 236 that allows additional airflow to be delivered to the impeller during high load engine operation. Thus, the movable sleeve 206 can be adjusted to block flow through the exhaust port of the active sleeve treatment device and allow flow through the injection port. The space between the inner surface of the movable sleeve 206 and the sleeve can define a first chamber, and flow recirculation in the direction opposite to the airflow indicated by arrow 212 can occur in the first chamber via the exhaust port during light engine loads. The inner surface of the movable sleeve 206 can include a rib structure to center the sleeve around the housing while creating a space that allows airflow to occur. In one example, the structure can be FIG. 2A to FIG. 2BThe rib 246 shown. The arrangement of the first end 240 of the sleeve limits and suppresses the oscillation of the surge flow, so that the noise is minimized and redirected into the compressor rather than released upstream into the atmosphere. The outer surface of the movable sleeve 206 can be attached to the link 318 of the rotary actuator 306. The rotary actuator 306 can be arranged outside the inlet duct 210 of the compressor 202 and adjacent to the inlet end 322 of the compressor housing 238, and is spaced apart from the inlet end 322 by the length of the link 318. The link 318 can include a first branch 316, a second branch 319, a third branch 320, and an arm 326 connected to a motor 328 of the rotary actuator 306. The first branch 316 can include a plurality of segments arranged in a vertically aligned alternating pattern and is connected to the outer surface of the movable sleeve 206. The first branch 316 can extend through the inlet end 322 of the compressor housing 238 via an aperture in the inlet end 322, wherein a portion of the first branch 316 protrudes to the outside of the compressor housing 238. The first branch is constrained to rotate about an axis perpendicular to the central axis 208, which passes from the interior to the exterior of the compressor housing 238. The end of the first branch 316 of the link 318 that protrudes to the exterior of the compressor housing 238 is connected to the first end of the second segment branch 319. The second branch 319 is completely arranged outside the compressor housing 238. The second branch 319 rotates about the same axis as the branch 316 and is coupled to the third branch 320 at the second end, which extends in a direction substantially perpendicular to the central axis 208 away from the inlet end 322 of the compressor housing 238. In another embodiment, the branch 320 can extend in a different direction, such as toward the inlet end 322. The third branch 320 is also completely outside the compressor housing 238. The third branch 320 is connected at one end to an arm 326, which is connected to a motor 328 of the rotary actuator 306. The motor 328 is configured to rotate the arm 326 to change the position of the attached movable sleeve 206. The pivoting of the arm 326 can be converted into both axial and rotational movement of the movable sleeve 206 via the link 318, and the following FIG. 4A to FIG. 4B This is further explained in detail in the description of .

[0070] FIG. 4A to FIG. 4B A side view of the inlet duct 210 of the compressor 202 is shown in FIG. Figures 2A to 3 Components common to compressor 202 are similarly numbered. Inlet duct 210 is surrounded by an inlet end 322 of the compressor housing. FIG. 4A to FIG. 4B4 and 5. The outer surface 404 of the movable sleeve 206 in FIG. 4 is shown as a pin 412 attached to the first branch 316 of the link 318. The first end of the pin 412 can be inserted into the hole in the outer surface 404 of the movable sleeve 206, thereby fixing the first end of the pin 412 to the movable sleeve 206. The pin 412 can include a surface shape, such as a portion of a sphere, so as to be properly coupled with the movable sleeve 206. In addition to the pin 412, the first branch 316 can also include a second segment 414 and a rod 416. The pin 412 of the first branch 316 extends outward from the movable sleeve 206 in a direction perpendicular to the central axis 208. The second end of the pin 412 is coupled to the first end 413 of the second segment 414 of the first branch 316.

[0071] The second section 414 is perpendicular to the pin 412 and may extend along a length of the movable sleeve 206, the length being defined in the direction of flow as indicated by the arrow 212. The second section 414 is positioned such that the first end 413 is upstream of the second end 415 along the outer surface 404 of the movable sleeve 206. Thus, the pin 412 is disposed downstream of the rod 416 of the first end 316 of the arm 318.

[0072] The second end 415 of the second segment 414 is coupled to a rod 416 that is parallel to the pin 412 of the first branch 316. The rod 416 of the first branch 316 extends outwardly and away from the outer surface 404 of the movable sleeve 206, such that a portion of the rod 416 is within the inlet end 322 of the compressor housing and a portion is outside the inlet end 322. The end of the rod 416 outside the inlet end 322 is connected to the second branch 319 by a first hinge 408. The first hinge 408 can be a fixed connection point between the first branch 316 and the second branch 319. In particular, the angle 420 formed by the second branch 319 and the second segment 414 of the first branch 316 is rigid and does not change when the link 318 is pivoted by the rotary actuator 306. The angle 420 can be any suitable angle, depending on the size and placement of the link 318 and the movable sleeve 206. In contrast, second branch 319 may be coupled to third branch 310 at a non-rigid second hinge 410. In other words, the angle formed between third branch 320 and second branch 319 may vary as link 318 pivots.

[0073] Figure 4A The movable sleeve 206 in FIG. 1 is shown in a position that closes the discharge port and allows flow through the injection port, which corresponds to the movable sleeve Figure 2B The second position shown in FIG. 1 and will be referred to hereinafter as the second position (eg, open for flow during turbocharger jam). When link 318 is pivoted to Figure 4BAs shown and corresponding to the movable sleeve Figure 2A In the first position shown in FIG. 1 (where the exhaust port is open to flow and the injection port is blocked), the third branch 320 is in the position indicated by Figure 4A 418. This movement causes the second branch 319 to tilt so that the upstream end of the second branch 319 is above the central axis 208, which in turn causes the first branch 316 to pivot at the rigid first hinge 408, causing the pin 412 of the first branch 316 to swing downward through an arc indicated by the arrow 420. The attachment of the pin 412 to the outer surface 404 of the movable sleeve 206 causes the movable sleeve to rotate a distance 422 in a direction perpendicular to the central axis 208 and to be axially displaced a distance 424 in a downstream direction coaxial with the central axis 208. The movable sleeve 206 is thus moved from Figure 4A The second position shown is actuated to Figure 4B First position shown.

[0074] To move the movable sleeve 206 from the first position ( Figure 4B ) moves to the second position ( Figure 4A ), the link 318 may be pivoted so that the third branch 320 is displaced downward in the direction indicated by arrow 426. This will translate into the pin 412 of the first branch 316 swinging through an upward arc indicated by arrow 428. The movable sleeve 206 is moved in a direction opposite to the direction of the movable sleeve 206. Figure 4A The described movement is rotationally displaced a distance 422 and axially displaced a distance 424 in the opposite direction, thereby actuating the movable sleeve to the second position.

[0075] FIG. 6A to FIG. 6B 200 and 210. The movement of the rotary actuator 306 is shown in additional detail in FIG. 6. The first schematic diagram 600 shows a top view of the movable sleeve 206 and the rotary actuator 306 adjusted to the second position, and the second schematic diagram 650 shows a top view of the movable sleeve 206 and the rotary actuator 306 in the first position. The direction of airflow through the movable sleeve is indicated by arrow 212. The movable sleeve 206 has a central axis 208 and is disposed via a first end (e.g., FIG. 4A to FIG. 4B The pin 412 of the first branch 316 of the movable sleeve 206 is attached to the first branch 316 of the link 318. The link 318 connects the movable sleeve 206 to the rotary actuator 306.

[0076] The rotary actuator 306 may be provided by a motor ( FIG. 6A to FIG. 6B320). The first end 602 of the arm 326 is connected to the motor and forms a joint, which is an axis about which the arm 326 can pivot / rotate relative to the reference axis set 302 along a plane formed by the horizontal direction and the transverse direction. The second end 603 of the arm 326 is connected to the third branch 320. In order to move the movable sleeve 206 from Fig. 6A The second position is shifted to Figure 6B In the first position, the second end 603 of the arm 326 can be Fig. 6A The third branch 320 rotates in the direction indicated by the arrow 604, thereby driving the third branch 320 to rotate in the direction indicated by the arrow 604. Fig. 6A The third branch 320 is coupled to the second branch 319 at the second hinge 410. The second branch 319 and the first branch 316, which are arranged at a fixed angle, pivot about the first hinge 408 so that the end of the first branch 316 attached to the movable sleeve 206 swings through an arc indicated by the arrow 420. As described above, the movable sleeve 206 is rotationally displaced a distance 422 and axially displaced a distance 424 downstream, thereby displacing to Figure 6B To actuate the movable sleeve 206 from the first position to the second position (e.g., from Figure 6B The configuration is actuated to Fig. 6A ), rotating the actuator 306 may cause the arm 326 to pivot at the first end 602 through the Figure 6B The arc indicated by arrow 606 is used to cause the third branch 320 to slide in the direction indicated by arrow 426, thereby causing the first branch 316 to swing through the arc indicated by arrow 428.

[0077] The first schematic diagram 600 and the second schematic diagram 650 show that the angle between the arm 326 and the third branch 320 and the angle between the third branch 320 and the second branch 319 can be changed when the arm 316 is pivoted by the rotary actuator 306. However, the angle between the second branch 319 and the first branch 316 is fixed, which enables the pivoting of the arm 326 to be converted into the oscillation of the first branch 316 of the link 318, which is further converted into the rotation and axial displacement achieved via a single actuation movement of the movable sleeve 206.

[0078] Figure 5 The front cross-sectional view in FIG. 1 shows the positioning of the first branch 316 of the link 318 relative to the movable sleeve 206 and the inlet conduit 210. The first branch 316 is located at the pin 412 ( Figure 5 The inlet end 322 of the compressor housing has an inner surface 402, and the space between the inner surface 402 and the outer surface 404 of the movable sleeve 206 forms the second chamber 236.

[0079] The movable sleeve 206 circumferentially surrounds the casing 205, which may include at the downstream end of the casing 205 the components described above with respect to FIG. 2A to FIG. 2B The first chamber 234 is formed in the space between the inner surface of the movable sleeve 206 and the outer surface of the sleeve 205, and has an inner volume that is smaller than the inner volume of the second chamber 236 or the inner passage 214 of the sleeve 205. The rib 246 protrudes from the inner surface of the movable sleeve 206 into the first chamber 234.

[0080] The attachment of the pin 412 to the outer surface 404 of the movable sleeve 206, the rigid coupling of the first branch to the second branch of the link 318, and the alignment of the link 318 relative to the movable sleeve 206 enable both axial and rotational adjustment of the movable sleeve 206 in a single actuation motion. The rod 416 of the first branch 316, represented by the dashed line 407, is positioned a distance 409 from the bisector 405 (dividing the inlet duct 210 in half), the distance 409 being defined in a direction perpendicular to the bisector 405. In one position, such as Figure 4A In the position of the link 318 shown, the pin 412 can be arranged to the left of the bisector 405 by an amount approximately equal to half of the rotation distance 422. In the second position, such as Figure 4B In the illustrated position of link 318, pin 412 may be positioned to the right of bisector 405 by an amount approximately equal to half of rotation distance 422. In this manner, the engagement depth of pin 412 in sleeve 206 is similar at the two selectable positions.

[0081] FIG. 2A to FIG. 6B The movable sleeve 206 may also be adapted to be moved via an actuation mechanism other than the rotary actuator shown. FIG. 7A to FIG. 7B As shown, a first schematic diagram 700, which is a top view of the movable sleeve 206, shows the movable sleeve 206 coupled to the linear actuator 702 in a second position. A second schematic diagram 750 of the movable sleeve 206 and the linear actuator 702 shows the movable sleeve 206 in a first position. Flow through the movable sleeve 206 is indicated by arrows 212, and the central axis 208 is included in the first schematic diagram 700 and the second schematic diagram 750.

[0082] The linear actuator 702 can be positioned outside the inlet duct above the movable sleeve 206, wherein the body of the linear actuator 702 is upstream of the movable sleeve 206 and offset from the central axis 208. The motor 704 of the linear actuator 702 and the retractable arm 706 extending from the motor 704 are parallel to the central axis 208. The linear actuator 702 is similar to FIG. 6A to FIG. 6BThe rotary actuator may include a link 318 configured with a first branch 316, a second branch 319, and a third branch 320. The second branch 319 and the third branch 320 may be arranged outside the inlet duct, while the first branch 316 may extend through the compressor housing.

[0083] The first branch 316 is attached to the movable sleeve 206 at one end and can extend through the compressor housing so that a portion of the first branch 316 protrudes outside the compressor housing. The end of the first branch 316 outside the compressor housing is coupled to the second branch 319 by the first hinge 408 so that the angle between the first branch 316 and the second branch 319 is constant. The second branch 319 of the link 318 is coupled to the third branch 320, both of which can be arranged outside the compressor housing.

[0084] The retractable arm 706 can connect the third branch 320 to the motor 704. The retractable arm 706 and the third branch 320 can be coupled so that the angle between the retractable arm 706 and the third branch 320 is not fixed. The motor 704 activates the linear movement of the retractable arm 706 parallel to the central axis 208. For example, to move the movable sleeve 206 from Fig. 7A The open position shown is actuated to Figure 7B The motor 704 can retract the retractable arm 706 in the direction indicated by the arrow 708 to move the retractable arm 706. The movement of the retractable arm 706 causes the third branch 320 to also shift in the direction of the arrow 708. The change in the position of the third branch 320 can pull the second branch 319 at the end connected to the third branch 320, so that the end of the second branch 319 is as shown by Fig. 7A The first and second branches 319 connected at the first hinge 408 can pivot as a single unit about the first hinge 408 and swing the first branch 316 through an arc indicated by arrow 712. The bending movement of the first branch 316 causes the attached movable sleeve 206 to shift a rotational distance 422 and an axial distance 424 in the downstream direction.

[0085] To actuate the movable sleeve 206 from the closed position to the open position, for example Figure 7B The position is actuated to Fig. 7A The linear actuator 702 can start the motor 704 to move the retractable arm 706 in the position Figure 7BThe third branch 320 also displaces in the direction of arrow 714, causing the end of the second branch 319 connected to the third branch 320 to pivot as indicated by arrow 716. The first branch 316 thus pivots in an upward direction along an arc indicated by arrow 718, causing the movable sleeve 206 to rotate a distance 422 and move an axial distance 424 in the upstream direction.

[0086] exist FIG. 7A to FIG. 7B In the example, similar to FIG. 6A to FIG. 6B The chain link 318 of the rotary actuator shown may have a first branch 316, a second branch 319, and a third branch 320. However, the orientation of the branches of the chain link 318 may be different because the upstream portion of the linear actuator 702 is arranged above the movable sleeve 206 and aligned along the length of the movable sleeve, rather than being to the side of the movable sleeve as for the rotary actuator. In the first schematic diagram 700 and the second schematic diagram 750 showing the linear actuator 702, the retractable arm 706 and the third branch 320 are nearly coaxial, but are not fixed with respect to the angle formed between the retractable arm 706 and the third branch 320. However, in the first schematic diagram 600 and the second schematic diagram 650 of the rotary actuator 306, the arm 326 pivots so that the angle of the arm 326 relative to the third branch changes from as shown in FIG. Fig. 6A The acute angle shown becomes Figure 6B Obtuse angle shown. Figures 3 to 6B The rotary actuator 306 and FIG. 7A to FIG. 7B The linear actuator 702 achieves both rotation and axial displacement of the movable sleeve 206, and the optional positioning of the actuator can accommodate different tolerances of the available space around the compressor housing. Other arrangements of the position of the rotary or linear actuator are possible and can be selected based on the space available to package the actuator near the compressor housing.

[0087] In this way, the movable sleeve may be adjusted to allow recirculation flow during light engine loads, or to enable additional delivery of air to the impeller when the compressor is operating at high loads. Figure 4A , Fig. 6A and Fig. 7AThe position of the movable sleeve shown may correspond to actuation of the link connecting the movable sleeve to the actuator during high engine loads, wherein the movable sleeve 206 is positioned to block flow through a discharge port, which is arranged upstream of the injection port of the active sleeve treatment device. The injection port is thus opened to allow air to flow into the second chamber in the same direction as it flows into the inlet duct of the compressor. After receiving a signal from the controller, for example, during reduced engine load, the link of the actuator may displace the movable sleeve by a certain axial distance and a certain rotational distance. Blocking flow in the injection port while opening the discharge port allows air to be directed back into the inlet duct from the area adjacent to the impeller in the opposite direction to flow through the inlet duct. The rotational distance that the movable sleeve travels at each position adjustment may prevent the movable sleeve from bonding to the casing in which the active casing treatment device is arranged if material accumulates between the movable sleeve and the casing over time.

[0088] The turbocharger compressor may be operated according to a map where the compressor pressure ratio varies with mass flow rate, such as Fig. 9 900. The X-axis represents flow rate, and the Y-axis represents pressure ratio, or output pressure divided by input pressure. On the left side of the performance diagram, the surge line or surge limit represented by dashed line 902 represents the following situation: the compressor operation may lose stability and exhibit surge behavior ranging from whoosh noise to violent flow oscillations. On the right side of the performance diagram, as shown by dashed line 904 representing the blocking line or blocking limit, the compressor is limited by a blocked flow condition at the inlet of the compressor. The operation to the left can be extended by including a discharge port in the compressor casing just downstream of the leading edge of the compressor impeller. In low flow conditions, such a port allows some of the airflow to be recirculated outside the main flow path to a point further upstream and then reintroduced into the compressor. With proper flow guidance, this recirculation flow is quieter than the recirculation flow that occurs near the surge limit without a discharge port. In high flow conditions, the airflow can circulate through different ports in the casing that are further downstream of the typical discharge port. This second port (injection port) is in an area known to experience relatively low air pressure during high flow conditions, which allows additional air to flow forward into the compressor wheel while normal flow is nearly blocked. This injection port can be blocked to prevent reverse (recirculation) flow from occurring at other operating points on the performance map, which may otherwise result in reduced compressor efficiency. Thus, the movable sleeve described herein allows for selective covering or exposure of the injection port while also allowing for a flow path with respect to the discharge port to minimize noise thrown into the air path upstream.

[0089] The present disclosure describes a compressor sleeve having two ports along the compressor impeller - one port for surge and one port for plugging. A thin cylindrical section of the sleeve extends from upstream of the compressor impeller. The ports are circumferentially located on the sleeve, and there are also a limited number of spokes or supports for delivering substances upstream of each port. A sleeve is mounted around the protruding cylindrical sleeve. In a first position, the sleeve includes features for covering the injection port and for directing the surge recirculation flow from the discharge port to an upstream position pointing back to the compressor impeller. In a second position, the sleeve moves sufficiently to expose the injection port and can cover the discharge port. To prevent sticking, the sleeve can rotate while the sleeve moves axially. The mechanism for providing such movement includes a chain link passing through a turbocharger compressor housing. The chain link causes the first end of the chain link to move through a certain arc. The first end of the chain link is fixed to the sleeve so that when the first end passes through the arc, it causes the sleeve to rotate and translate.

[0090] Go to Figure 8 , a flow chart of a method 800 for controlling the operation of an active casing treatment device (e.g., controlling the flow therein and the position of the active casing treatment device) in conjunction with a movable sleeve disposed in an inlet duct of a compressor is shown. In particular, the active casing treatment device may be the active casing treatment device 204, and the movable sleeve may be FIG. 2A to FIG. 2B The movable sleeve 206 may circumferentially surround the sleeve in which the active sleeve processing device is disposed, and the movable sleeve and the sleeve may be as shown. FIG. 2A to FIG. 2B The method 800 is shown positioned upstream of the impeller in the inlet duct of the compressor. A first chamber fluidly coupled to the discharge port of the active sleeve treatment device can be formed by the space between the outer surface of the sleeve and the inner surface of the movable sleeve. When the discharge port is open, air can be recirculated from the area adjacent to the impeller through the discharge port and the first chamber to the inlet duct. When the injection port is open, a second chamber fluidly coupled to the injection port of the active sleeve and formed by the space between the outer surface of the movable sleeve and the inner surface of the compressor housing can allow additional airflow to be delivered to the impeller area. Instructions for executing method 800 and the remaining methods included herein can be executed by a controller (e.g., Figure 1 The controller 12 shown in FIG. 1 is based on instructions stored in the controller's memory and in conjunction with sensors from the engine system, such as those described above with reference to FIG. Figure 1 According to the method described below, the controller can use an engine actuator of the engine system to adjust the engine operation. For example, the controller can use an actuator of a movable sleeve to adjust the position of the movable sleeve so that the exhaust port or the injection port is like FIG. 2A to FIG. 2B As described above, Figure 3An example of such an actuator is shown in , and operation of a movable sleeve and an active sleeve handling device via the actuator is described in the following method.

[0091] At 802, the method includes estimating and / or measuring engine operating conditions. The engine operating conditions may include engine speed, engine load, intake air mass flow, engine temperature (such as engine coolant temperature), intake manifold pressure, pressure differential across the compressor, position of a movable sleeve, etc. At 804, the method includes determining whether current compressor operation is below a surge threshold. It may be determined that current compressor operation is below a surge threshold based on a current (e.g., currently determined) engine load and engine speed being below a surge line or threshold. For example, a performance map or lookup table of engine load versus engine speed may be stored in a memory of the controller. The controller may determine the current engine speed (e.g., based on a value from Figure 1 The operating point is then checked to see if it is above or below a surge threshold. In one example, the surge threshold may be a preset surge threshold stored in a performance map or lookup table.

[0092] In another example, the compressor operation below the surge threshold may be determined based on a compressor performance map that plots compressor pressure ratio as a function of compressor mass flow. Fig. 9 , the surge limit is represented by dashed line 902. The surge threshold may be defined as a line on the compressor performance map that represents 20% more flow than the flow at the surge limit line. The area to the left of dashed line 902 is the area where the compressor operates below the surge limit, the area including a certain range of pressure ratios relative to flow rates below the minimum flow rate for stable compressor operation. Operating near the surge limit may result in inefficient compressor operation and, in some cases, undesirable noise. Setting the surge threshold above the surge limit allows for some margin and may prevent operation in undesirable areas of the compressor performance map.

[0093] Additionally, as used herein, operating the compressor below a surge threshold may include: Fig. 9 As shown and explained above, the compressor is operating to the right of the surge limit, but within a threshold range of the surge limit (e.g., within a threshold mass air flow of the surge limit). Additionally, the compressor may be operated with a movable sleeve that is adjustable to be open to flow in the discharge port in a first position until a blockage limit is approached over a range of compressor operating conditions.

[0094] If the compressor is operating below the surge threshold, the method proceeds to 806 to adjust the movable sleeve to the first position opening the discharge port. Adjusting the movable sleeve may include sending an electronic signal by the controller to an actuation mechanism of the movable sleeve to slide the movable sleeve from a position in which the injection port is open (and the discharge port is closed, which is referred to as the second position of the movable sleeve) to the first position in which the discharge port is open, or to maintain the movable sleeve in the first position in which the discharge port remains open. As described above, Figure 2A and Figure 4B 2 shows the arrangement of the movable sleeve for opening the discharge port. As explained above with reference to these figures, when the discharge port is opened, the movable sleeve is moved by Figure 8 The pressure at the outlet end of the compressor (defined as being downstream of the leading edge of the compressor wheel) is relieved by allowing flow from the impeller region through the discharge port and the first chamber to return flow to the inlet duct as indicated at 808. The first chamber may be equipped with elements such as FIG. 2A to FIG. 2B The first end 240 of the movable sleeve 206 is shown to reduce noise and dampen oscillations during surge flow, such as flow through the first chamber in a direction opposite to flow through the inlet duct. By adjusting the movable sleeve to open the discharge port and close the injection port, the surge limit of the compressor can be shifted so that more engine operating points can be outside the surge region and dampen noise.

[0095] Alternatively, at 804, if the engine is operating above a surge threshold, the method proceeds to 810 to determine whether the turbocharger operation is above a blockage threshold. Turbocharger blockage may occur when the engine experiences high load and high speed, high air flow, or other parameters that cause the air flow entering the compressor to be higher than the turbocharger can withstand (e.g., higher than the amount of airflow that can physically fit through the compressor). During a blockage, the air velocity entering the compressor impeller may reach nearly the speed of sound, thereby preventing any increase in airflow. Inputs from the various sensors used to detect compressor surge as described above may also be used to assess whether the compressor operation exceeds a blockage threshold (e.g., engine speed and load, compressor mass flow, and pressure ratio). The blockage threshold may also be a preset threshold stored in a performance map or lookup table of engine load versus engine speed, compressor ratio versus mass flow. For example, refer to Fig. 9 , the blockage threshold or blockage limit is indicated by dashed line 904. The area to the right of dashed line 904 indicates a condition where the blockage threshold is exceeded. If the turbocharger is determined to be operating below the blockage threshold (e.g., to the left of the blockage threshold), the method 800 proceeds to 806 so that the controller can send a signal to the actuation mechanism to adjust the movable sleeve so that the exhaust port is opened or maintained open, and the routine continues to 808.

[0096] If the controller determines that the compressor is operating above the jam threshold (e.g., the compressor is Fig. 9 If the compressor is operated to the right of the blockage line, the method proceeds to 812, where the movable sleeve is actuated to the second position to open the injection port and close the discharge port. In addition, as used herein, the compressor operating above the blockage threshold may include: Fig. 9 As shown and explained above, the compressor is operating to the left of the blockage limit, but within a threshold range of the blockage limit (e.g., within a threshold mass air flow of the blockage limit). Additionally, in some examples, the movable sleeve may be adjusted to open the injection port when the compressor is operating close to the blockage limit but the compressor is not operating in the blockage region, such as when the compressor mass flow and pressure ratio are within 5% or 10% of the blockage threshold.

[0097] At 814, air flows from the inlet duct through the second chamber and injection port to the impeller area. This enables additional airflow to be delivered to the compressor's impeller, thereby reducing the velocity of the air flowing into the leading edge of the compressor impeller, which during blockage reaches nearly the speed of sound. The second chamber does not include a noise suppression structure and therefore does not restrict flow.

[0098] After enabling flow through the injection port of the active sleeve treatment device, the method proceeds to 816 to determine whether the turbocharger operation is still above the blockage threshold. If the blockage threshold is still exceeded, the method returns to 812 to maintain the movable sleeve in the second position where the injection port is open to flow. However, if the engine operation drops below the blockage threshold, the routine continues to 818 to adjust the movable sleeve to the first position to open the exhaust port and allow air to recirculate through the first chamber to return to the inlet duct. In some examples, the controller can maintain the movable sleeve in the second position until the turbocharger operation is below the blockage threshold by a suitable amount, such as 5% or 10% above the blockage threshold.

[0099] In this way, a movable sleeve coupled to an active casing treatment device positioned within an inlet duct of a compressor and upstream of an impeller of the compressor can be used to adjust flow in the inlet duct. The movable sleeve circumferentially surrounds a casing in which the active casing treatment device is disposed and is itself surrounded by a compressor housing. The movable sleeve is spaced apart from both the casing and the compressor housing so that a first chamber is formed between the casing and the movable sleeve, the first chamber being fluidly coupled to a discharge port in the active casing treatment device. The first chamber can be provided with a noise suppression structure, such as a flow restrictor or a deflector. The second chamber is formed by the space between the movable sleeve and the compressor housing. The second chamber is fluidly coupled to an injection port in the active casing treatment device. In one example, when the turbocharger operation (e.g., compressor mass flow and pressure ratio) is below a blockage threshold and / or below a surge threshold, the movable sleeve can be adjusted to allow flow through the discharge port instead of the injection port. In this position, airflow is allowed to recirculate from the impeller to the inlet duct via the discharge port and the first chamber, thereby alleviating pressure buildup at the outlet end of the compressor and extending surge margin, and suppressing oscillations generated during surge flow. In another example, the movable sleeve can be adjusted to be open to flow in the injection port rather than the discharge port, thereby mitigating pressure gradients generated during conditions (e.g., engine speed and load) that exceed a blockage threshold. Additional flow is directed to the impeller via the second chamber and the injection port. The technical effect of adjusting the position of the movable sleeve, and therefore the flow in the compressor, is to expand the range of engine operating conditions in which the compressor can operate stably and efficiently.

[0100] Figures 1 to 7BAn example configuration with relative positioning of various components is shown. If shown as directly contacting each other or directly connected, then at least in one example, such elements can be referred to as direct contact or direct connection, respectively. Similarly, at least in one example, the elements shown as being adjacent or adjacent to each other can be adjacent or adjacent to each other, respectively. As an example, components arranged in coplanar contact with each other can be referred to as coplanar contact. As another example, in at least one example, elements that are positioned apart from each other with only a spacing therebetween and no other components can be referred to as coplanar contact. As another example, elements shown as being above / below each other, on opposite sides or on the left / right side of each other can be referred to as coplanar contact relative to each other. In addition, as shown in the figure, in at least one example, the highest point of the topmost element or element can be referred to as the "top" of the component, and the lowest point of the bottommost element or element can be referred to as the "bottom" of the component. As used herein, top / bottom, upper / lower, above / below can be relative to the longitudinal axis of the accompanying drawings and are used to describe the positioning of the elements in the accompanying drawings relative to each other. Thus, in one example, the element shown as being above other elements is vertically positioned above other elements. As another example, the shapes of elements shown in the drawings may be referred to as having those shapes (e.g., such as round, straight, planar, curved, rounded, chamfered, angled, etc.). Additionally, in at least one example, elements shown as intersecting each other may be referred to as intersecting elements or intersecting each other. Additionally, in one example, elements shown as being within another element or shown as being outside another element may be referred to as intersecting elements or intersecting each other.

[0101] As an embodiment, a method includes: flowing intake air through a casing in a first direction to an impeller of a compressor; selectively flowing intake air from the casing in an opposite second direction through a first chamber, the first chamber circumferentially surrounding the casing; and selectively flowing intake air in the first direction through a second chamber to the impeller, the second chamber circumferentially surrounding the first chamber. In a first example of the method, the casing circumferentially surrounds at least a portion of the impeller, and wherein selectively flowing intake air from the casing through the first chamber includes selectively flowing intake air from the casing to the first chamber via a discharge port of the casing. The second example of the method optionally includes the first example, and also includes wherein selectively flowing intake air in the first direction through the second chamber to the impeller includes selectively flowing intake air in the first direction through the second chamber to the impeller via an injection port of the casing. A third example of the method optionally includes one or more of the first and second examples, and further includes wherein selectively causing intake air to flow from the sleeve through the first chamber via the exhaust port includes actuating the movable sleeve to a first position based on a mass air flow through the sleeve being below a threshold mass air flow, wherein when the movable sleeve is in the first position, the exhaust port is open to the first chamber. A fourth example of the method optionally includes one or more of the first to third examples, and further includes wherein selectively causing intake air to flow through the second chamber in a first direction to the impeller via the injection port includes actuating the movable sleeve to a second position based on a mass air flow through the sleeve being above a threshold mass air flow, wherein when the movable sleeve is in the second position, the injection port is open to the second chamber.

[0102] As another embodiment, a compressor includes: an impeller rotatable about a central axis and housed in a compressor housing; a sleeve at least partially surrounding the impeller, the sleeve including an injection port and a discharge port; and a movable sleeve circumferentially surrounding the sleeve and defining a first airflow chamber between an outer surface of the sleeve and an inner surface of the movable sleeve, and a second airflow chamber between an outer surface of the movable sleeve and an inner surface of the housing, the movable sleeve being configured to selectively block and open the injection port and the discharge port. In a first example of the compressor, the sleeve forms an internal passage that fluidly couples the inlet of the compressor to the impeller, and the discharge port fluidly couples the internal passage to the first airflow chamber, and the injection port fluidly couples the internal passage to the second airflow chamber. A second example of the compressor optionally includes the first example, and also includes wherein each of the first airflow chamber and the second airflow chamber is fluidly coupled to the inlet of the compressor. The third example of the compressor optionally includes one or more of the first and second examples, and also includes wherein the movable sleeve is adjustable to a first position, in which the discharge port is open and the injection port is blocked, thereby fluidly coupling the internal passage to the first airflow chamber, so that the intake air in the internal passage flows through the discharge port and flows to the first airflow chamber. The fourth example of the compressor optionally includes one or more of the first to third examples, and also includes wherein the movable sleeve is adjustable to a second position, in which the discharge port is blocked and the injection port is open, thereby fluidly coupling the internal passage to the second airflow chamber, so that the intake air in the second airflow chamber flows through the injection port and flows to the impeller. The fifth example of the compressor optionally includes one or more of the first to fourth examples, and also includes wherein the discharge port is located upstream of the injection port in the direction of intake air flow through the compressor. The sixth example of the compressor optionally includes one or more of the first to fifth examples, and also includes a support rib that is coupled to the movable sleeve and protrudes into the first airflow chamber. A seventh example of a compressor optionally includes one or more of the first to sixth examples, and further includes wherein the movable sleeve includes an inwardly curved downstream end, and wherein the inwardly curved downstream end includes a face configured to be in coplanar contact with an outer surface of the sleeve. An eighth example of a compressor optionally includes one or more of the first to seventh examples, and further includes wherein the face of the inwardly curved downstream end is sized to prevent flow through a discharge port or an injection port. A ninth example of a compressor optionally includes one or more of the first to eighth examples, and further includes: the movable sleeve includes an inwardly curved upstream end, and the inwardly curved upstream end restricts air flow in the first airflow chamber and directs it toward the impeller.

[0103] As another embodiment, a system includes a compressor, the compressor comprising: a housing; an impeller, the impeller being housed in the housing and rotatable about a central axis; a sleeve, the sleeve at least partially surrounding the impeller and forming an internal passage, the internal passage fluidically coupling an inlet of the compressor to the impeller, the sleeve including an injection port and a discharge port; a movable sleeve, the movable sleeve circumferentially surrounding the sleeve; a first airflow chamber, the first airflow chamber extending along an outer surface of the sleeve; and a second airflow chamber, the second airflow chamber extending along an outer surface of the movable sleeve; an actuating mechanism, the actuating mechanism coupled to the movable sleeve; and a controller storing instructions, the instructions executable to: actuate the actuating mechanism to move the movable sleeve to a first position in response to compressor operation in a surge region, in which the discharge port is open to the first flow chamber and the injection port is blocked; and actuate the actuating mechanism to move the movable sleeve to a second position in response to compressor operation in a blocked region, in which the discharge port is blocked and the injection port is open to the second airflow chamber. In a first example of the system, the actuation mechanism includes a link that couples the motor to the movable sleeve, wherein the motor is positioned outside the housing and the link passes through the housing. A second example of the system optionally includes the first example, and further includes wherein the exhaust port is positioned upstream of the injection port in the sleeve in the direction of intake air flow through the internal passage. A third example of the system optionally includes one or more of the first and second examples, and further includes wherein the injection port is positioned in the sleeve at a low pressure region, so that when the movable sleeve is in the second position, the intake air in the second chamber flows through the injection port and flows to the impeller. A fourth example of the system optionally includes one or more of the first to third examples, and further includes wherein the exhaust port is positioned in the sleeve at a high pressure region, so that when the movable sleeve is in the first position, the intake air in the internal passage flows through the exhaust port and flows to the first chamber.

[0104] It should be noted that the example 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 in non-temporary memory as executable instructions and can be executed by a control system including a controller in combination with various sensors, actuators and other engine hardware. The specific routines described herein can represent any number of processing strategies, such as one or more of event-driven, interrupt-driven, multi-tasking, multi-threading, etc. Therefore, the various actions, operations and / or functions shown can be performed in the order shown, in parallel, or omitted in some cases. Similarly, the processing order is not necessarily required to achieve the features and advantages of the example embodiments described herein, but is provided for the convenience of explanation and description. Depending on the specific strategy being used, one or more of the actions, operations and / or functions shown can be repeatedly performed. In addition, the described actions, operations and / or functions can be represented graphically as codes in a non-temporary memory of a computer-readable storage medium that will be programmed into an engine control system, wherein the described actions are performed by executing the instructions in a system including a combination of various engine hardware components and an electronic controller.

[0105] It will be appreciated that the configurations and routines disclosed herein are exemplary in nature, and these specific embodiments should not be viewed in a limiting sense, as numerous variations are possible. For example, the above techniques may be applied to V6, inline 4, inline 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.

[0106] The following claims particularly point out certain combinations and subcombinations deemed 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 one or more such elements, neither requiring nor excluding a combination of two or more such elements. Other combinations and subcombinations of the disclosed features, functions, elements, and / or properties may be claimed by amending the present claims or presenting new claims herein or in a related application. Such claims, whether larger, smaller, equal, or different in scope to the original claims, are deemed to be included within the scope of the subject matter of the present disclosure.

[0107] According to the present invention, a method is provided, the method comprising: causing intake air to flow through a casing in a first direction to an impeller of a compressor; selectively causing intake air to flow from the casing in an opposite second direction through a first chamber, the first chamber circumferentially surrounding the casing; and selectively causing intake air to flow in the first direction through a second chamber to the impeller, the second chamber circumferentially surrounding the first chamber.

[0108] According to one embodiment, the sleeve circumferentially surrounds at least a portion of the impeller, and wherein selectively flowing the intake air from the sleeve through the first chamber includes selectively flowing the intake air from the sleeve to the first chamber via a discharge port of the sleeve.

[0109] According to one embodiment, the above invention is further characterized in that selectively allowing the intake air to flow in the first direction through the second chamber to the impeller includes selectively allowing the intake air to flow in the first direction through the second chamber to the impeller via the injection port of the sleeve.

[0110] According to one embodiment, the above invention is further characterized by selectively allowing intake air to flow from the sleeve through the first chamber via the exhaust port includes actuating the movable sleeve to a first position based on a mass air flow rate through the sleeve being less than a threshold mass air flow rate, wherein the exhaust port is open to the first chamber when the movable sleeve is in the first position.

[0111] According to one embodiment, the above invention is further characterized in that selectively allowing intake air to flow through the second chamber in a first direction to the impeller via the injection port includes actuating the movable sleeve to a second position based on a mass air flow rate through the sleeve being higher than a threshold mass air flow rate, wherein when the movable sleeve is in the second position, the injection port is open to the second chamber.

[0112] According to the present invention, a compressor is provided, which has: an impeller, which is rotatable about a central axis and accommodated in a compressor housing; a sleeve, which at least partially surrounds the impeller, the sleeve including an injection port and a discharge port; and a movable sleeve, which surrounds the sleeve in a circumferential direction and defines a first air flow chamber between an outer surface of the sleeve and an inner surface of the movable sleeve, and a second air flow chamber between an outer surface of the movable sleeve and an inner surface of the housing, the movable sleeve being configured to selectively block and open the injection port and the discharge port.

[0113] According to one embodiment, the sleeve forms an internal passage fluidly coupling an inlet of the compressor to the impeller, and wherein the discharge port fluidly couples the internal passage to the first air flow chamber, and the injection port fluidly couples the internal passage to the second air flow chamber.

[0114] According to one embodiment, the above invention is further characterized by each of the first air flow chamber and the second air flow chamber being fluidly coupled to an inlet of a compressor.

[0115] According to one embodiment, the movable sleeve is adjustable to a first position in which the exhaust port is open and the injection port is blocked, thereby fluidly coupling the internal passage to the first airflow chamber so that intake air in the internal passage flows through the exhaust port and into the first airflow chamber.

[0116] According to one embodiment, the movable sleeve is adjustable to a second position in which the discharge port is blocked and the injection port is open, thereby fluidly coupling the internal passage to the second air flow chamber so that intake air in the second air flow chamber flows through the injection port and to the impeller.

[0117] According to one embodiment, the discharge opening is located upstream of the injection opening in the direction of intake air flow through the compressor.

[0118] According to one embodiment, the above invention is further characterized by a support rib coupled to the movable sleeve and protruding into the first airflow chamber.

[0119] According to one embodiment, the movable sleeve comprises an inwardly curved downstream end, and wherein the inwardly curved downstream end comprises a face configured for coplanar contact with an outer surface of the sleeve.

[0120] According to one embodiment, the above invention is further characterized in that the face of the inwardly curved downstream end is sized to impede flow through the discharge or injection port.

[0121] According to one embodiment, the movable sleeve comprises an inwardly curved upstream end, and wherein the inwardly curved upstream end restricts air flowing in the first air flow chamber and directs it towards the impeller.

[0122] According to the present invention, a system is provided, the system having: a compressor, the compressor comprising: a housing; an impeller, the impeller being housed in the housing and rotatable about a central axis; a sleeve, the sleeve at least partially surrounding the impeller and forming an internal passage, the internal passage fluidically coupling an inlet of the compressor to the impeller, the sleeve comprising an injection port and a discharge port; a movable sleeve, the movable sleeve circumferentially surrounding the sleeve; a first airflow chamber, the first airflow chamber extending along an outer surface of the sleeve; and a second airflow chamber, the second airflow chamber extending along an outer surface of the movable sleeve; an actuating mechanism, the actuating mechanism coupled to the movable sleeve; and a controller storing instructions executable to: actuate the actuating mechanism to move the movable sleeve to a first position in response to compressor operation in a surge region, in which the discharge port is open to the first flow chamber and the injection port is blocked; and actuate the actuating mechanism to move the movable sleeve to a second position in response to compressor operation in a blocked region, in which the discharge port is blocked and the injection port is open to the second airflow chamber.

[0123] According to one embodiment, the actuation mechanism comprises a link coupling the motor to the movable sleeve, wherein the motor is positioned outside the housing and the link passes through the housing.

[0124] According to one embodiment, the discharge opening is positioned in the sleeve upstream of the injection opening in the flow direction of the inlet air through the inner passage.

[0125] According to one embodiment, the injection port is positioned in the sleeve at the low pressure area so that when the movable sleeve is in the second position, intake air in the second chamber flows through the injection port and to the impeller.

[0126] According to one embodiment, the discharge port is positioned in the sleeve at the high pressure area so that when the movable sleeve is in the first position, intake air in the internal passage flows through the discharge port and into the first chamber.

Claims

1. A method for a compressor, the method comprising: allowing intake air to flow in a first direction through the sleeve via the internal passage to an impeller of the compressor; selectively causing intake air to flow from the sleeve in an opposite second direction through a first chamber that circumferentially surrounds the sleeve and the internal passage; as well as Intake air is selectively caused to flow in the first direction through a second chamber to the impeller, the second chamber circumferentially surrounding the first chamber.

2. The method of claim 1, wherein the sleeve circumferentially surrounds at least a portion of the impeller, and wherein selectively causing intake air to flow from the sleeve through the first chamber comprises selectively causing intake air to flow from the sleeve to the first chamber via a discharge port of the sleeve.

3. The method of claim 2, wherein selectively flowing intake air in the first direction through the second chamber to the impeller comprises selectively flowing intake air in the first direction through the second chamber to the impeller via an injection port of the sleeve.

4. The method of claim 3, wherein selectively causing intake air to flow from the sleeve through the first chamber via the exhaust port comprises actuating a movable sleeve to a first position based on a mass air flow rate through the sleeve being below a threshold mass air flow rate, wherein when the movable sleeve is in the first position, the exhaust port is open to the first chamber.

5. The method of claim 3, wherein selectively causing intake air to flow in the first direction through the second chamber to the impeller via the injection port comprises actuating a movable sleeve to a second position based on a mass air flow through the sleeve being above a threshold mass air flow, wherein the injection port is open to the second chamber when the movable sleeve is in the second position.

6. A compressor, comprising: an impeller rotatable about a central axis and received in the compressor housing; a casing at least partially surrounding the impeller, the casing comprising an injection port and a discharge port; as well as A movable sleeve circumferentially surrounds the sleeve and defines a first airflow chamber between an outer surface of the sleeve and an inner surface of the movable sleeve, and a second airflow chamber between an outer surface of the movable sleeve and an inner surface of the shell, the movable sleeve being configured to selectively block and open the injection port and the discharge port, wherein the first airflow chamber circumferentially surrounds the internal passage, and the second airflow chamber circumferentially surrounds the first airflow chamber.

7. The compressor of claim 6, wherein the sleeve forms an internal passage that fluidly couples an inlet of the compressor to the impeller, and wherein the discharge port fluidly couples the internal passage to the first air flow chamber, and the injection port fluidly couples the internal passage to the second air flow chamber.

8. The compressor of claim 7, wherein each of said first and second air flow chambers are fluidly coupled to said inlet of said compressor.

9. The compressor of claim 7, wherein the movable sleeve is adjustable to a first position in which the discharge port is open and the injection port is blocked, thereby fluidly coupling the internal passage to the first air flow chamber so that intake air in the internal passage flows through the discharge port and into the first air flow chamber.

10. The compressor of claim 7, wherein the movable sleeve is adjustable to a second position in which the discharge port is blocked and the injection port is open, thereby fluidly coupling the internal passage to the second air flow chamber so that intake air in the second air flow chamber flows through the injection port and flows to the impeller.

11. The compressor of claim 6, wherein said discharge port is located upstream of said injection port in a direction of intake air flow through said compressor.

12. The compressor of claim 6, further comprising a support rib coupled to the movable sleeve and protruding into the first air flow chamber.

13. The compressor of claim 6, wherein said movable sleeve includes an inwardly curved downstream end, and wherein said inwardly curved downstream end includes a face configured for coplanar contact with an outer surface of said sleeve.

14. The compressor of claim 13, wherein said face of said inwardly curved downstream end is sized to prevent intake air from passing through said discharge port or said injection port.

15. The compressor of claim 6, wherein said movable sleeve includes an inwardly curved upstream end, and wherein said inwardly curved upstream end restricts air flow in said first air flow chamber and directs it toward said impeller.

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