Turbocharger assembly

Abstract

A turbocharger assembly can include a housing including a bore defined by a bore wall and a pin socket forming an opening in the bore wall; a bearing including a pin opening defined by a pin opening surface; a pin, wherein the pin includes a longitudinal pin axis and a pin surface; a groove in the pin opening surface or the pin surface, wherein the groove includes an axial length; wherein, in a positioned state of the bearing in the bore and the pin in the pin socket with a portion of the pin in the pin opening, there is a gap between the bearing and the bore wall, wherein the groove is in fluid communication with the gap to form a lubricant supply path from the gap to an interface between the pin surface and the pin opening surface.

Description

Technical Field

[0001] The topics disclosed in this article generally relate to turbocharger components used in internal combustion engines. Background Technology

[0002] A turbocharger may include a rotating assembly comprising a turbine impeller and a compressor impeller connected to each other via a shaft. For example, the turbine impeller may be welded or otherwise attached to the shaft to form a shaft and impeller assembly (SWA), and the compressor impeller may be fitted to the free end of the shaft. An electric compressor may include one or more compressor impellers connected to one or more shafts that can be driven by an electric motor. As an example, the shaft attached to one or more bladed impellers may be supported by one or more bearings housed in bearing housings that may form a central housing rotating assembly (CHRA). During operation of a turbocharger or electric compressor, the shaft may be expected to rotate at speeds exceeding 200,000 rpm, depending on factors such as the size of various components. To ensure proper rotor dynamics, the rotating assembly should be well balanced, well supported, and well lubricated under a wide variety of conditions, such as operation, temperature, pressure, etc. Attached Figure Description

[0003] A more complete understanding of the various methods, apparatuses, components, systems, arrangements, etc., and their equivalents described herein can be obtained by referring to the examples shown in the accompanying drawings and by referring to the following specific embodiments, wherein:

[0004] Figure 1 It is a diagram of a turbocharger, an internal combustion engine, and a controller;

[0005] Figure 2A and Figure 2B These are side and end views of an example turbocharger assembly;

[0006] Figure 3 yes Figure 2A and Figure 2B A cross-sectional view of an exemplary turbocharger assembly along the plane indicated by line AA;

[0007] Figure 4 yes Figure 2A and Figure 2B A cross-sectional view of an exemplary turbocharger assembly along the plane indicated by line BB;

[0008] Figure 5 yes Figure 2A and Figure 2B A cross-sectional view of an exemplary turbocharger assembly along a plane indicated by line CC;

[0009] Figure 6 This is a side view of an example of a pin;

[0010] Figure 7 yes Figure 6 An exemplary pin is shown in a cross-sectional view along the plane indicated by line DD.

[0011] Figure 8A and Figure 8B yes Figure 6 A cross-sectional view of an exemplary pin along a plane indicated by line EE, and a corresponding cross-sectional view of an example including the outer ring of the bearing assembly;

[0012] Figure 9A and Figure 9B They are Figure 7 Enlarged views of several parts of the view in Figure 8;

[0013] Figure 10 These are perspective views of examples of pins and bearing assemblies;

[0014] Figure 11A and Figure 11B It has an outer ring ( Figure 11A ) and without an outer ring ( Figure 11B A perspective view of an example turbocharger assembly;

[0015] Figure 12A and Figure 12B A perspective view of an example of a bearing and a cross-sectional view of an exemplary bearing with a pin;

[0016] Figure 13 This is an example of a graph showing vibration relative to the compressor speed;

[0017] Figure 14A , Figure 14B and Figure 14C These are views of an example grinding wheel and an example of the manufacturing process, respectively; and

[0018] Figure 15 It is a series of views of the outline example. Detailed Implementation

[0019] The following text describes examples of turbocharged engine systems, followed by various examples of parts, components, methods, and so on.

[0020] Turbochargers are frequently used to increase the output of internal combustion engines. (Reference) Figure 1 As an example, system 100 may include an internal combustion engine 110 and a turbocharger 120. Figure 1As shown, system 100 may be part of vehicle 101, wherein system 100 is housed in the engine compartment and connected to exhaust duct 103, which directs exhaust gas to exhaust outlet 109, for example, located behind passenger compartment 105. Figure 1 In one example, a processing unit 107 may be provided to process exhaust gas (e.g., reduce emissions via catalytic conversion of molecules, etc.).

[0021] like Figure 1 As shown, the internal combustion engine 110 includes an engine block 118 that houses one or more combustion chambers operably driven by a shaft 112 (e.g., via a piston), and an intake port 114 that provides a flow path for air reaching the engine block 118 and an exhaust port 116 that provides a flow path for exhaust from the engine block 118.

[0022] The turbocharger 120 can be used to extract energy from exhaust gas and provide that energy to intake air, which can then combine with fuel to form combustion gases. For example... Figure 1 As shown, the turbocharger 120 includes an air inlet 134, a shaft 122, a compressor housing assembly 124 for a compressor impeller 125, a turbine housing assembly 126 for a turbine impeller 127, another housing assembly 128, and an exhaust outlet 136. The housing assembly 128 may be referred to as the central housing assembly because it is located between the compressor housing assembly 124 and the turbine housing assembly 126.

[0023] exist Figure 1 In this configuration, shaft 122 may be a shaft assembly comprising various components (e.g., consider a shaft and impeller assembly (SWA) in which turbine impeller 127 is welded to shaft 122, etc.). As an example, shaft 122 may be rotatably supported by a bearing system (e.g., journal bearings, rolling element bearings, etc.) disposed in housing assembly 128 (e.g., in bores defined by one or more bore walls), such that rotation of turbine impeller 127 causes rotation of compressor impeller 125 (e.g., because it is rotatably coupled via shaft 122). As an example, central housing rotating assembly (CHRA) may include compressor impeller 125, turbine impeller 127, shaft 122, housing assembly 128, and various other components (e.g., compressor side plates disposed at an axial position between compressor impeller 125 and housing assembly 128).

[0024] exist Figure 1 In the example, the variable geometry component 129 is shown partially disposed between the housing assembly 128 and the housing assembly 126. This variable geometry component may include blades or other components to change the geometry of the passageway leading to the turbine impeller space in the turbine housing assembly 126. As an example, a compressor assembly with variable geometry may be provided.

[0025] exist Figure 1 In the example, the exhaust valve (or simply exhaust valve) 135 is positioned near the exhaust inlet of the turbine housing assembly 126. The exhaust valve 135 can be controlled to allow at least some of the exhaust gas from the exhaust port 116 to bypass the turbine impeller 127. Various exhaust valves, exhaust valve components, etc., can be applied to conventional fixed-nozzle turbines, fixed-blade nozzle turbines, variable-nozzle turbines, twin-scroll turbochargers, etc. As an example, the exhaust valve can be an internal exhaust valve (e.g., at least partially inside the turbine housing). As an example, the exhaust valve can be an external exhaust valve (e.g., operatively coupled to a duct in fluid communication with the turbine housing).

[0026] exist Figure 1 The example also shows an exhaust gas recirculation (EGR) duct 115, which may optionally be provided with one or more valves 117 to allow exhaust gas to flow to a location upstream of the compressor impeller 125.

[0027] Figure 1 An exemplary arrangement 150 for directing exhaust gas to an exhaust turbine housing assembly 152 and another exemplary arrangement 170 for directing exhaust gas to an exhaust turbine housing assembly 172 are also shown. In arrangement 150, a passage 156 is included within the cylinder head 154 to guide exhaust gas from the cylinder to the turbine housing assembly 152; while in arrangement 170, a manifold 176 enables the installation of the turbine housing assembly 172, for example, without any separate intermediate length exhaust piping system. In exemplary arrangements 150 and 170, turbine housing assemblies 152 and 172 can be configured for use with wastegates, variable geometry assemblies, etc.

[0028] exist Figure 1In this document, an example of controller 190 is shown including one or more processors 192, memory 194, and one or more interfaces 196. This controller may include a circuitry, such as that of an engine control unit (ECU). As described herein, various methods or techniques may be implemented, for example, by combining the controller with control logic. The control logic may depend on one or more engine operating conditions (e.g., turbo rpm, engine rpm, temperature, load, lubricant, cooling, etc.). For example, sensors may transmit information to controller 190 via one or more interfaces 196. The control logic may depend on this information, and subsequently, controller 190 may output control signals to control engine operation. Controller 190 may be configured to control lubricant flow, temperature, variable geometry components (e.g., variable geometry compressors or turbines), exhaust valves (e.g., via actuators), electric motors, or one or more other components associated with the engine, turbocharger (or multiple turbochargers), etc. As an example, turbocharger 120 may include one or more actuators and / or one or more sensors 198, which may be coupled, for example, to one or more interfaces 196 of controller 190. As an example, the exhaust valve 135 can be controlled by a controller that includes an actuator that responds to electrical signals, pressure signals, etc. As an example, the actuator for the exhaust valve can be, for example, a mechanical actuator that can operate without electricity (e.g., consider a mechanical actuator configured to respond to a pressure signal supplied via a conduit).

[0029] Figure 2A A side view of an example of a turbocharger assembly 200 is shown, and Figure 2B A turbine-end view showing an example of a turbocharger assembly 200.

[0030] As shown in the figure, the turbocharger assembly 200 includes a shaft 220, a compressor impeller 240, a turbine impeller 260, a central housing 280, and a compressor plate 290. As also shown, the turbocharger assembly 200 further includes a lubrication system feature 400, a pin socket feature 500, and a pin 700. Figure 2A and Figure 2B In the example, the turbocharger assembly 200 may be oriented relative to gravity, for example, to facilitate the flow of the lubricant portion due to gravity.

[0031] Figure 2A Lines AA and CC are shown, while Figure 2B Lines AA and BB are shown. Figure 3 A cross-sectional view of the turbocharger 200 along line AA is shown; Figure 4 A cross-sectional view of the turbocharger 200 along line BB is shown; and Figure 5A cross-sectional view of the turbocharger 200 along line CC is shown.

[0032] exist Figure 3 In the diagram, turbocharger assembly 200 is shown including a nut 241 attached to a shaft 220, which is part of a shaft and impeller assembly (SWA) including a turbine impeller 260. For example, the turbine impeller 260 may include a hub portion 265, which is a transition portion between the shaft 220 and the turbine impeller 260. As an example, the turbine impeller 260 may be welded or otherwise attached to the shaft 220, wherein various components are positioned along the shaft 220 such that tightening the nut 241 mechanically compresses the compressor impeller 240 and causes rotation of the shaft 220 to rotate the compressor impeller 240.

[0033] exist Figure 3 In the example, to reduce the exhaust flow inward into the central housing 280, the hub portion 265 of the SWA may include one or more sealing elements, such as, for example, piston rings disposed between the hub portion 265 and the bore wall of the turbine side bore of the central housing 280. To further reduce the airflow inward into the central housing 280, a thrust collar 270 (e.g., optionally with a lubricant slinger, etc.) may be disposed in a bore of the compressor plate 290, wherein one or more sealing elements may be positioned between the thrust collar 270 and the bore wall of the compressor plate 290.

[0034] exist Figure 3 In the example, turbocharger assembly 200 includes bearing assembly 300, which is at least partially disposed in a bore 281 defined by bore wall 283 of central housing 280. As shown, shaft 220 is rotatably supported by bearing assembly 300 such that rotation of turbine impeller 260 (e.g., via exhaust flow) can drive rotation of compressor impeller 240.

[0035] Bearing assembly 300 is shown as a rolling element bearing assembly (REB assembly) that can be lubricated via lubrication flow through lubrication system feature 400. Figure 3In one example, lubrication system feature 400 includes an opening 401 leading to a bore 403 in a central housing 280, the opening 401 being in fluid communication with another opening 405, which may form intersecting holes in the central housing 280. As shown, opening 401 may receive a plug 402 (e.g., a sealing element, such as a ball, etc.) to seal bore 403 relative to opening 401, such that bore 403 is supplied with lubricant via opening 405. As shown, lubrication system feature 400 includes lubricant passages 440 and 460, wherein lubricant passage 440 directs lubricant from bore 403 toward the compressor side of turbocharger assembly 200, and wherein lubricant passage 460 directs lubricant from bore 403 toward the turbine side of turbocharger assembly 200. In this example, lubricant passages 440 and 460 supply lubricant through a common bore (e.g., bore 403).

[0036] exist Figure 3 In one example, bearing assembly 300 may include a lubricant nozzle that directs lubricant to rolling elements (such as, for example, ball bearings). Lubricant may flow from bearing assembly 300 and bore 281 via various channels (e.g., channel 480 in fluid communication with orifice 281), compressor-side channel 484, and turbine-side channel 486, from which lubricant may flow to a common lubricant outlet 490 of the central housing 280. As an example, an internal combustion engine may include a lubricant pump (e.g., an oil pump, etc.) that supplies lubricant under pressure to turbocharger assembly 200 via a conduit, such that pressurized lubricant is received in orifice 403. Since lubricant outlet 490 can be at a pressure lower than the supplied lubricant pressure, lubricant system feature 400 enables pressure-driven flow of lubricant. When the supply pressure drops, for example, due to shutting down the lubricant pump, some remaining lubricant may be discharged by gravity, which may collect at or through lubricant outlet 490. In this example, when the lubricant is discharged, one or more lubricant films between the bearing assembly 300 and the bore 281 of the central housing 280 may be very thin, allowing the bearing assembly 300 to rest on the bore wall 283; note that the bearing assembly 300 can bear the weight of various components, such as the compressor impeller 240 and turbine impeller 260 (e.g., and thrust collar 270, etc.). When the lubricant pump resumes operation, the pressurized flow of lubricant via the lubricant system feature 400 can cause the lubricant film to form or thicken, and the lubricant flows to the lubricant rolling elements of the bearing assembly 300.

[0037] Lubricants reduce friction between components, form a lubricating film, and transfer heat away from the turbocharger assembly 200. However, components may come into contact under various conditions, which can lead to noise, wear, vibration, and so on. For example, in the case of two components in contact, contact forces can cause noise, vibration, and acoustic harshness (NVH).

[0038] NVH (Noise, Vibration, and Harshness) can be used to characterize vehicles, particularly cars and trucks. While noise and vibration can be measurable, harshness is often a subjective quality (e.g., measured through surveys, analytical tools that provide results reflecting human subjective impressions, etc.) because it can be part of the field of psychoacoustics. In various cases, engine-related noise (e.g., turbocharger noise) may be present in the interior space of a vehicle (e.g., the cabin), which may disturb one or more occupants of the vehicle.

[0039] exist Figure 4 In the turbocharger assembly 200, a pin 700 is positioned relative to a pin socket feature 500. Figure 4 In the example, pin 700 can perform one or more functions. For instance, pin 700 can restrict the movement of at least a portion of bearing assembly 300. However, as mentioned, if the two components come into contact with each other, one or more NVH (noise, vibration, and harshness) problems may occur. Figure 4 In the example, pin 700 is shown to include features that can mitigate one or more NVH problems. For example, pin 700 can enable lubricant flow and / or lubricant film formation, which can reduce the occurrence of one or more NVH problems, including one or more of rotational speed-related problems, lubricant pressure-related problems, thrust-related problems, etc.

[0040] exist Figure 4 In the example, bearing assembly 300 is shown as including an outer ring 310, an inner ring 330, and a rolling element 320, the rolling element 320 being at least partially disposed between the outer ring 310 and the inner ring 330, for example using a bearing retainer 325. Figure 4 In the example, the inner ring 330 can be optional; for example, consider a shaft that directly includes raceways for the rolling elements; however, in Figure 4 In the middle, the inner ring 330 is assembled to the shaft 220, wherein the inner ring 330 includes raceways for the rolling element 325. Furthermore, in Figure 4 In the example, the bearing assembly 330 includes a set of compressor-side rolling elements 320-1 with corresponding bearing retainers 325-1 and a set of turbine-side rolling elements 325-2 with corresponding bearing retainers 325-2, as well as a multi-piece inner ring 330, which may include a compressor-side inner ring 330-1 and a turbine-side inner ring 330-2.

[0041] As mentioned, the outer ring 310 may include lubricant nozzles, such as, for example, one or more compressor-side lubricant nozzles and one or more turbine-side lubricant nozzles, which can supply lubricant via channels 440 and 460, respectively, wherein the lubricant nozzles guide the lubricant to rolling elements 320-1 and 320-2, respectively.

[0042] exist Figure 4 The example illustrates several lubricant regions, including a lubricant film region 392, a compressor-side lubricant well region 394, and a turbine-side lubricant well region 396. As an example, channel 440 can supply lubricant to the compressor-side lubricant well region 394, which may be in fluid communication with one or more compressor-side lubricant nozzles of the outer ring 310, and channel 460 can supply lubricant to the turbine-side lubricant well region 396, which may be in fluid communication with one or more turbine-side lubricant nozzles of the outer ring. Regarding the lubricant film region 392, it may receive lubricant via one or more routes, which may be via the compressor-side lubricant well region 394 and / or via the turbine-side lubricant well region 396. As shown, the lubricant well regions 392, 394, and 396 span an axial length and an azimuth angle relative to the axis of rotation of the inner ring 330. For example, each of the lubricant regions 392, 394, and 396 may span 360 degrees.

[0043] exist Figure 4 In this example, the maximum outer diameter of the outer ring 310 received in the bore 281 of the central housing 280 can be slightly smaller than the inner diameter of the bore wall 283 of the bore 281 of the central housing 280, such that one or more gaps are formed at locations where lubricant can be present. For example, a large portion of the outer surface of the outer ring 310 can be coated with lubricant, and a large portion of the bore wall 283 can be coated with lubricant. In this example, one or more lubricant regions can form one or more lubricant extrusion films, which can be sized to provide properties intended to reduce NVH, etc. As an example, the lubricant extrusion film can be referred to as an extrusion film damper (SFD).

[0044] As an example, in a rolling element bearing assembly (REB assembly), a series of rolling elements can be positioned between an inner ring and an outer ring, wherein the inner ring can be press-fitted onto a shaft, and the outer ring's rotational movement is restricted by an anti-rotation pin. In this example, the lubricant film formed between the outer ring and the bore wall of the central housing can be a squeeze film damper (SFD).

[0045] In another type of bearing system, known as a journal bearing system, journal bearings (or multiple journal bearings) can be used without rolling elements; note that a hybrid approach can utilize both journal bearings and REB assemblies. Regarding fully floating rotary journal bearings, two hydrodynamic lubricant films arranged in series can be used, one being an inner film (between the shaft and the journal bearing) and the other an outer film (between the journal bearing and the central housing). Regarding semi-floating journal bearings, they can include a hydrodynamic inner lubricant film and a squeeze film damper (SFD) (an outer oil film between the journal bearing and the central housing). While various examples mention the use of REB assemblies, by way of example, semi-floating journal bearings can be used, where, for example, the journal bearing includes an opening that can receive a pin (such as, for example, pin 700). While various examples involve a central housing, by way of example, a bore, such as bore 281, can be formed using components other than the central housing (e.g., consider a bearing housing that could be a cylinder that can be received in the central housing, etc.).

[0046] Regarding pin socket feature 500, Figure 4 The diagram shows a pin socket or pin hole 501, an opening 510, an axial surface 520 (e.g., a stop surface), a mating region 530 (e.g., for threaded connection, for interference fit, etc.), a transition region 540, and a lubricant well region 570 that may define one or more lubricant wells relative to the pin 700, for example, wherein the pin 700 is at least partially received in the lubricant well region 570. Figure 4 In the example, the pin socket 501 can be formed as a transverse hole intersecting with the hole 281 of the central housing 280.

[0047] exist Figure 5 In the example, the opening 580 and pin socket 501 in the hole wall 283 of the hole 281 of the central housing 280 can be defined by the perimeter formed by the intersection of two cylinders. The intersection curve of the two cylinders with radii “a” and “b” is given by parametric equations in Cartesian coordinates (x, y, z):

[0048] x(t) = b cos(t)

[0049] y(t) = b sin(t)

[0050] z(t) = + / - (a 2 – b 2 sin 2 (t)) 0.5 .

[0051] In this example, the hole in the housing can have a radius "a", and a portion of the pin socket in the housing can have a radius "b", wherein such "cylinders" can intersect at right angles (and see, for example, see...). Figure 10 , Figure 11A and Figure 11B ).

[0052] exist Figure 4 In the example, pin 700 is shown as being at least partially received in an opening 370 of the outer ring 310 of bearing assembly 300 (e.g., consider intersecting "cylinders"). Pin 700 can be stationary when it is securely fitted into the central housing 280 via at least some pin-hole features 500 (e.g., features of mating regions 530, etc.). Conversely, the outer ring 310 of bearing assembly 300 can be semi-floating, for example, via one or more lubricant films (e.g., consider lubricant regions 392, 394, and 396, etc.), while pin 700 restricts rotational movement of the outer ring 310 when tightened.

[0053] As mentioned, one or more NVH problems may arise when components come into contact. For example, consider the outer ring 310 rotating within the bore 281 of the central housing 280 such that the wall 372 of the outer ring 310 defining the opening 370 contacts the pin 700. In this example, the contact between the wall 372 (e.g., the wall surface) and the pin 700 (e.g., the outer surface of the pin 700) can occur with a force sufficient to generate noise (e.g., kinetic energy converted into acoustic energy).

[0054] Sound intensity I can have energy units per unit area per unit time, and sound energy density w=I / c can have energy units per unit volume.

[0055] As an example, NVH can be periodic and / or random. For example, periodic NVH can be driven by rotational speed (e.g., RPM) or one or more other periodic phenomena; however, random NVH can be driven by one or more random processes, which can be random, or for example, random when they occur and periodic during their occurrence, etc.

[0056] As an example, NVH can be caused by an imbalance of one or more components. Consider, for example, a rotating assembly, such as a center housing rotating assembly (CHRA), where turbocharger assembly 200 may be a CHRA. In this example, a certain amount of imbalance may exist for one or more of the components, such as, for example, compressor impeller 240, turbine impeller 260, thrust collar 270, inner ring 330, etc. As an example, the imbalance can manifest in a manner dependent on one or more operating conditions, such as, for example, the rotational speed of a shaft, which could be a turbocharger shaft, an internal combustion engine crankshaft, etc. As an example, in a case where the flow of lubricant, with a variable speed (e.g., dependent on crankshaft speed, etc.), is driven by a lubricant pump, NVH can depend on the operating mode of the lubricant pump. As an example, at low engine RPM (crankshaft RPM), a crankshaft-driven lubricant pump can provide a lower pressure than at higher engine RPM, and in this example, the engine's exhaust energy may be related to the rotational speed of the turbine impeller, which is part of the SWA supported by bearings (e.g., REB assembly, journal bearings, etc.).

[0057] As mentioned, the outer ring 310 of the bearing assembly 300 may include an opening 370 that may receive a portion of the pin 700. To reduce the risk, occurrence (e.g., frequency, etc.) and / or magnitude of one or more NSV problems, the pin 700 may include a groove positioned to deliver a certain amount of lubricant from a gap region between the outer ring 310 and the bore wall 283 of the central housing 280 to the interface between the pin 700 and the wall 372 of the outer ring 310 defining the opening 370. In this example, the lubricant at the interface can achieve energy damping, thereby advantageously altering the kinematics. For example, consider damped vibrations, which may include vibrations transmitted from the outer ring 310 to the central housing 280 via the pin 700.

[0058] As mentioned, pin 700 can achieve one or more of anti-rotation (e.g., rotation limiting) and anti-axial translation (e.g., translation limiting). In cases where a type of motion causes undesirable performance, one or more grooves can be provided that mitigate the undesirable performance. For example, consider clockwise rotation, where the groove is positioned to reduce contact from this clockwise rotation, which can depend on turbocharger performance, including the turbine impeller's expected rotational direction in response to the exhaust flow. As another example, consider counterclockwise rotation, where the groove is positioned to reduce contact from this counterclockwise rotation, which can depend on turbocharger performance, including the turbine impeller's expected rotational direction in response to the exhaust flow. As yet another example, consider positioning the groove to reduce contact from axial translation toward the compressor side of the turbocharger, which can depend on turbocharger performance, including the turbine impeller's expected rotational direction in response to the exhaust flow. As another example, consider positioning the grooves to reduce contact from axial translation toward the turbine side of the turbocharger, which can depend on turbocharger performance, including the turbine impeller's expected rotational direction in response to the exhaust flow. As an example, a pin may include one or more grooves, each of which may be designed for one or more specific types of motion. As an example, a pin may include four grooves, which may be sufficient to address the aforementioned four types of contact. As an example, the shape and / or size and / or number of grooves may differ for different types of motion (e.g., different types of contact).

[0059] As an example, a pin may include a symmetrical arrangement of grooves and / or an asymmetrical arrangement of grooves. Regarding a symmetrical arrangement, consider four grooves at 0 degrees, 90 degrees, 180 degrees, and 270 degrees around the axis of the pin. In this example, the pin may be positioned in an opening in an outer ring (e.g., a journal), wherein two of the grooves are generally axially aligned along an axis parallel to the axis of rotation of the shaft, and the other two of the grooves are aligned along a transverse axis parallel and orthogonal to the axis of rotation of the shaft. To facilitate alignment, the pin may include a mark, multiple marks, etc., which may be located at the top of the pin (e.g., the head portion of the pin). For example, the pin may include an indicator (e.g., a mark) to be generally aligned in a direction toward the compressor side or the turbine side. Where the pin includes symmetry in the grooves, the indicator may be adapted to be generally aligned toward the compressor side or the turbine side. Although the compressor side and turbine side are mentioned, reference is made to... Figure 2A The center housing 280 may include one or more features to facilitate pin positioning for alignment of the pin relative to the outer ring (e.g., or journal) around the pin's axis. For example, consider via... Figure 2A A downward-pointing (e.g., along the direction of gravity) mark or through Figure 2AThe pin is positioned using upward-pointing markers. As an example, one or more reference points (e.g., reference point markers) can be used to facilitate the positioning of the pin in the center housing, such that one or more features of the pin (e.g., one or more grooves) are properly aligned to mitigate one or more types of NVH problems.

[0060] Figure 5 The image shows a cross-sectional view of a portion of a turbocharger assembly 200, wherein the pin 700 includes a head 710, an optional marking 713, an optional drive feature 715, an axial face 720 (e.g., a stop surface), a mating region 730, a transition region 740, and a section extending axially along the pin 700 across its length (e.g., which can be determined by the dimension Δz). g The groove portion 750, end portion 780, and end surface 790 of one or more grooves (as indicated). Figure 5 In the example, two trenches are visible. Note that there may be one or more other trenches, wherein the two trenches have approximately equal dimensions.

[0061] As explained, the center housing 280 may include a pin-slot feature 500 that facilitates acceptable positioning of the pin 700 within the center housing 280. For example, the pin 700 may be axially positioned via an axial face 720 such that the end 790 of the pin 700 extends to a desired depth into the bore 281 of the center housing 280 and / or the outer ring 310 of the bearing assembly 300. As shown, this depth may be measured, for example, using the longitudinal axis of the bore 281, such as by the dimension Δz. z As instructed. Figure 5 The example illustrates another dimension, which is the axial dimension Δz of the end portion 780 of pin 700 along the axis of pin 700. e For example, in Figure 5 As shown in the example, each of the two grooves extends into the opening 370 of the outer ring 310 of the bearing assembly 300, and the end surface 790 of the pin 700 does not contact the inner ring 330 of the bearing assembly 300 (e.g., there is a gap between the end surface 790 of the pin 700 and the outer surface of the inner ring 330).

[0062] exist Figure 5In the example, pin 700 may include one or more types of features along at least a portion of mating region 730, which may mate with one or more types of features along at least a portion of mating region 530 of pin socket 501. Features may include, for example, one or more guides, one or more threads, one or more interference mating surfaces, etc. As an example, pin 700 may be threaded along at least a portion of mating region 730 by a thread that mates with a corresponding thread along at least a portion of mating region 530. As an example, pin 700 may be unthreaded, and pin socket 501 may be unthreaded, such that pin 700 is mated along at least a portion of mating region 730 and along at least a portion of mating region 530 via interference mating via interference surfaces. In any example, if pin 700 is provided with a mark 713, mark 713 may be oriented such that one or more grooves of pin 700 are suitably oriented relative to hole 281 (e.g., relative to hole axis, etc.).

[0063] Figure 6 A side view of an example pin 700 is shown, illustrating a head 710, an axial surface 720, a mating region 730, a transition region 740, a groove portion 750, an end portion 780, and an end surface 790, wherein a chamfer 785 (e.g., an annular conical surface, etc.) may be present as a transition from the diameter of the end portion 780 to the smaller diameter of the end surface 790. Figure 6 In the figure, pin 700 is shown to have a groove 751, which can be defined by an axial length along the pin axis and a lateral dimension shown as Δg. The lateral dimension can be measured using a straight-line distance, arc distance, and / or angle. As shown, the lateral dimension is shown as the maximum lateral dimension centered approximately along the axial length of the groove 751. Figure 6 In the example, groove 751 is shown as generally symmetrical along a longitudinal axis, wherein groove 751 can be formed into pin 700 via one or more types of techniques. As an example, groove 751 can be formed via machining techniques (e.g., using a grinding wheel with a V-shaped edge profile; see [reference]). Figure 13 (etc.)

[0064] Figure 7 Show pin 700 along as Figure 6 The image shows a cross-sectional view of line DD. Figure 7 In the example, trenches 752 and 753 are shown, and trenches 752 and 753 can be respectively connected to Figure 6 In the example, groove 751 is spaced approximately 90 degrees apart in both clockwise and counterclockwise directions. As shown, groove 752 can be defined by radius RG, which is located at a distance z from the pin axis. p Measured at a distance R.

[0065] Figure 8A Show pin 700 along as Figure 6 The image shows a cross-sectional view of line EE. Figure 6 In the example, grooves 751, 752, 753, and 754 are shown, which surround the pin axis z. p Arranged at approximately 0 degrees, 90 degrees, 180 degrees, and 270 degrees (e.g., Θ). g The interval is 90 degrees. For example... Figure 8A As shown in the example, the groove 751 can use size RG, angle φ g And, for example, from the diameter of pin 700 to the pin axis z p Measured radial depth Δr g limited.

[0066] Figure 8B The pin 700 is shown in a cross-sectional view through a portion of the outer ring 310 of the bearing assembly 300, which is in a position relative to... Figure 8A The cross-sectional view at a lower axial position, as can be seen from the size of grooves 751, 752, 753 and 754 (see, for example, [reference]). Figure 5 ).like Figure 8A and Figure 8B As shown, the maximum radial depth of the trench (Δr) g It can be along the pin axis z p Located in the axial position, with the locating pin 700, it is within the pin socket 501, and a portion of the groove is along the pin axis z. p The groove extends axially beyond the pin socket 501 (e.g., exiting from the pin socket 501 and entering the bore 281). In this method, the groove can be a reservoir with an opening that can be in fluid communication with a lubricant film in a gap defined between the outer surface of the outer ring and the inner surface of the bore wall. In this example, the size of the groove, combined with the pin position relative to the pin socket, can define the size of the opening relative to the reservoir volume, through which lubricant can flow in and out of the reservoir volume via the defined opening.

[0067] As an example, the size of the groove reservoir and reservoir opening can be determined by prior knowledge of the dynamics that may occur during turbocharger operation. For example, when the outer ring rotates clockwise, the lubricant pressure in the groove reservoir may decrease and / or the lubricant volume in the groove reservoir may decrease (e.g., because lubricant can flow from the groove reservoir to another space via the reservoir opening), and, for example, when the outer ring rotates counterclockwise, the lubricant pressure in the groove reservoir may increase and / or the lubricant volume in the groove reservoir may increase (e.g., because lubricant can flow from another space into the groove reservoir via the reservoir opening). Such hydrodynamics can be used to dampen the rotational movement of the outer ring relative to a pin at least partially received in an opening in the outer ring (e.g., clockwise and / or counterclockwise). This damping can help reduce the risk of one or more types of NVH, reduce the occurrence of one or more types of NVH, and / or reduce the magnitude (e.g., the impact) of one or more types of NVH.

[0068] Refer again Figure 8B The diagram shows a void region 800 and groove regions 810, 820, 830 and 840, wherein regions 800, 810, 820, 830 and 840 may receive lubricant (e.g., be filled with lubricant). Figure 8B The opening 370 of the outer ring 310 (e.g., defined by the surface of the outer ring 310) and the outer surface 757 of the groove region 750 of the pin 700 are also shown.

[0069] exist Figure 8B In the example, turbine side 806 and compressor side 804 are shown. In this example, axial thrust can drive outer ring 310 towards compressor side 804 or towards turbine side 806, wherein the dynamics and direction of this axial thrust can be different. As explained, outer ring 310 can rotate clockwise or counterclockwise, wherein the dynamics can be different.

[0070] exist Figure 8B In the example, regions 820 and 840 can provide a certain amount of damping for axial thrust, which at least results in translational movement of the outer ring 310 (e.g., along an axis pointing from the compressor side 804 to the turbine side 806), while regions 810 and 830 can provide a certain amount of damping for rotation (e.g., clockwise or counterclockwise about an axis pointing from the compressor side 804 to the turbine side 806). As mentioned, the pin can include one or more grooves, where each groove can correspond to one or more specific types of movement that may cause one or more NVH problems. Although Figure 8B The example shows regions 810, 820, 830, and 840, which are numbered in total and are arranged around the pin axis z. pThe pins, spaced approximately 90 degrees apart, may include a single groove or multiple grooves arranged to address one of the four types of movement described above.

[0071] Figure 9A Show Figure 5 An enlarged view of a portion of the cross-sectional view, and Figure 9B Show Figure 6 An enlarged view of a portion of the cross-sectional view. Grooves 791, 792, 793, and 794 can provide space for lubricant and can form lubricant reservoirs that can supply lubricant to and / or receive lubricant from lubricant film region 392.

[0072] As shown in the figure, Figure 9A and Figure 9B In this configuration, due to the geometry of the "intersecting cylinders," grooves 791 and 793 do not extend as deeply into the opening 370 of the outer ring 310 as grooves 792 and 794; all grooves are in fluid communication with the lubricant film region 392. As an example, a pin may include grooves of different sizes, shapes, locations, etc. For instance, where it is desired that each groove extends to a common depth in the opening of the outer ring (e.g., the journal), the lateral axial grooves (e.g., see grooves 791 and 793) may be positioned lower than the axial grooves (e.g., see grooves 792 and 794), or in other words, the axial grooves may be positioned higher. Again, due to the intersection of the two cylindrical geometries, the axial grooves "see" the maximum radius of the outer ring 310 because they are shown as aligned along the longitudinal axis of the outer ring 310, while the lateral axial grooves "see" a radius smaller than the maximum radius of the outer ring 310 because they are shown as offset from the longitudinal axis of the outer ring 310. As an example, a pin may include grooves designed or over-designed for axial or lateral axis positioning. As an example, a pin may include grooves that are limited in volume (e.g., individually or collectively) such that the lubricant film dynamics are not harmfully or undesirably altered (e.g., see lubricant film region 392, which is in fluid communication with grooves 791, 792, 793 and 794).

[0073] like Figure 9A As shown, the groove 793 may face upward and be concave, so that it can retain lubricant that is unsuitable for discharge from the groove 793 due to gravity, wherein gravity is indicated as along... Figure 9AThe direction is shown in the figure. In this example, the lubricant volume of the groove 793 can be designed accordingly. Furthermore, when the turbocharger assembly 200 is not in operation, the lubricant held in the groove 793 can help lubricate the interface between the pin 700 and the outer ring 310; however, without the groove 793, direct contact may occur between the outer surface of the pin and the surface of the opening of the outer ring, which could be harmful for one or more reasons (e.g., adhesion, coking of the lubricant, etc.).

[0074] Figure 10 A perspective view showing a portion of pin 700 and a portion of bearing assembly 300. (As shown in...) Figure 10 As shown in the example, the outer ring 310 includes a keyway 311, which in Figure 3 The figure shows the bearing assembly 300 on the compressor side. This keyway, together with the key, can be used as a mechanism to limit the movement of the outer ring 310, which is an additional option using the pin 700. As shown, the outer ring 310 may include various features, such as a generally annular region 312 axially disposed between lubricant wells 314 and 316, which is separated from the annular region 312 by regions 315 and 316, respectively. As explained, when disposed in the bore 281 of the housing 280, the annular region 312 may define a lubricant film region 392, which may be in fluid communication with the grooves 751, 752, 753, and 754 of the pin 700. As explained, grooves 752 and 754 extend deeper into the opening 370 of the outer ring 310 than grooves 751 and 753; note that the groove size, position, etc., can be adjusted to achieve the desired depth.

[0075] Figure 11A The pin 700 is shown as viewed from the inside of the outer ring 310, with a portion of the end portion 780 and the end surface 790 visible. Figure 11A In the example, grooves 751, 752, 753 and 754 are not visible because they do not extend to or beyond the opening 370 at the inner surface of the outer ring 310.

[0076] Figure 11B The image shows a pin 700 as viewed from inside a hole 281 in housing 280, with an opening 580 in the hole wall 283 of housing 280 shown, through which the pin 700 extends partially, making a groove 754 (e.g., oriented toward the compressor side) partially visible, while another portion of the groove 754 defines a groove reservoir relative to a lubricant well region 570, the groove reservoir being defined by the surface of a pin insertion port 501 in housing 280.

[0077] exist Figure 11BIn the example, the visible portion of groove 754 may be referred to as a groove opening or groove reservoir opening, which is in fluid communication with a groove reservoir partially defined by another portion of groove 754 and the surface of pin socket 501. As mentioned, lubricant may flow into and / or out of lubricant film region 392 and one or more grooves of the pin to address one or more NVH issues.

[0078] Figure 12A An example of a portion of bearing 1230 is shown, which may be the journal or outer ring of a rolling element bearing assembly (REB assembly). As shown, bearing 1230 includes a wall 1235 (e.g., a pin opening surface) forming a shoulder relative to surface 1236 (e.g., a cylindrical surface) and another shoulder relative to inner surface 1239, wherein wall 1235 defines an opening 1237 (e.g., a transverse hole to the main bore of bearing 1230, etc.), opening 1237 may be sized to receive a pin, such as, for example, pin 700, or, for example, a pin with fewer grooves, more grooves, no grooves, etc.

[0079] exist Figure 12A In the example, wall 1235 can have a varying thickness because it is formed by the intersection of a cylinder and an annular cylinder. In this example, the thickness can be greater "off-axis" than "on-axis". Figure 12A As shown in the example, bearing 1230 may include one or more grooves 1231, 1232, 1233, and 1234 in wall 1235, said grooves being located at one or more locations, including, for example, one or more off-axis locations and / or one or more on-axis locations. Figure 12A In the example, grooves 1232 and 1234 are on-axis, while grooves 1231 and 1233 are off-axis. As shown, the grooves can be defined by length L, depth d, opening width b, and side dimensions (e.g., a and c).

[0080] exist Figure 12A In the example, each of the trenches can be approximated as a V-shaped trench, which may, for example, have a depth d that varies along the length L. For example, if L is measured from surface 1236, the depth d decreases with the length as well as the opening width b and the side dimensions a and c. As an example, the shape of the trench may depend on one or more tools used to form the trench and / or one or more processes used to form the trench (e.g., see...). Figure 14A , Figure 14C and Figure 15 ).

[0081] As mentioned, forces, contacts, NVH, etc., can be directional, and the direction can be axial, off-axis, or another direction. As explained, grooves can be positioned and / or sized (e.g., determined in size, shape, etc.) to address a specific problem. Regarding bearings, they can be configured to be oriented in a finite number of ways within the bore of the housing. For example, a bearing can be symmetrical, such that either end can be a compressor-side end and either end can be a turbine-side end. Alternatively, a bearing can be asymmetrical, as it has a compressor-side end on the compressor side of the bore of the housing and / or a turbine-side end on the turbine side of the bore of the housing.

[0082] In the example of Figure 12, on-axis grooves 1232 and 1234 are shown as being larger than off-axis grooves 1231 and 1233. This method can be used to match and overlap with a pin comprising four grooves of equal and defined size, wherein the overlap is less for the off-axis groove and more for the on-axis groove due to the geometry of the opening 1237.

[0083] As explained, a pin having one or more grooves can be oriented in a desired orientation using one or more guides (which may include markings, inspection tools, etc.) such that the grooves are oriented as desired (e.g., aligned with the axis of the shaft, aligned with an off-axis, etc.). With respect to bearing 1230, the orientation can be simpler and, in many cases, can be ensured (e.g., for asymmetrical bearings, etc.).

[0084] As mentioned, the component may include a pin with at least one groove and / or a bearing with at least one groove. In this component, where both the pin and the bearing are grooved, the grooves may be aligned or misaligned.

[0085] exist Figure 12B In the example, a void region 1210 and groove regions 1211, 1212, 1213 and 1214 are shown, which can receive lubricant (e.g., be filled with lubricant). Figure 12B The opening 1237 of the bearing 1230 (e.g., defined by wall 1235 and surface 1236) and the outer surface 1257 of the pin region 1250 are also shown, which do not include grooves (e.g., at least in Figure 12B (At the horizontal position shown in the cross-sectional view).

[0086] exist Figure 12BIn the example, turbine side 1206 and compressor side 1204 are shown. In this example, axial thrust can drive bearing 1230 towards compressor side 1204 or towards turbine side 1206, wherein the dynamics and direction of this axial thrust can be different. As explained, bearing 1230 can rotate clockwise or counterclockwise, wherein the dynamics can be different.

[0087] exist Figure 12B In the example, regions 1212 and 214 can provide a certain amount of damping for axial thrust, which at least causes translational movement of bearing 1230 (e.g., along an axis pointing from compressor side 1204 to turbine side 1206), while regions 1211 and 1213 can provide a certain amount of damping for rotation (e.g., clockwise or counterclockwise around an axis pointing from compressor side 1204 to turbine side 1206).

[0088] As mentioned, pins and / or bearings may include one or more grooves, each groove corresponding to one or more specific types of movement that may cause one or more NVH problems. Although Figure 12B The example shows regions 1211, 1212, 1213 and 1214, which are numbered in total and are spaced apart at approximately 90 degrees around opening 1237. For the problem of determining one of the four types of movement mentioned above, the bearing may include a single groove or multiple grooves arranged for one type of movement.

[0089] As explained, turbocharger bearings can cause one or more types of NVH (Noise, Vibration, and Harshness) problems. For example, rolling elements rotating at or near critical speeds can tend to produce an unpleasant whirring sound, especially when engine noise is not loud enough to mask turbocharger noise, such as at idle. As explained, at idle, the engine can be at particularly low RPMs with respect to the crankshaft, which is operatively coupled to the pistons. Furthermore, depending on the construction used for lubricant pumping, lubricant pressures may be lower than in the case of higher engine RPMs at non-idling speeds.

[0090] When both the engine and engine lubricant are cold (e.g., at ambient temperature or much below the engine's operating temperature), various types of NVH problems can be most severe under cold start conditions. As an example, grooved pins and / or grooved bearings can help reduce or eliminate the unpleasant noise generated by the turbocharger under cold idling conditions.

[0091] Figure 13An example of a vehicle 1301 with a turbocharger 1302 is shown, the turbocharger 1302 including a turbocharger assembly, such as, for example, a turbocharger assembly 200. In this example, tests can be performed to characterize unpleasant NVH, which can be plotted as a graph of the relationship between energy or other parameters and RPM, which can be engine RPM, turbocharger shaft RPM, etc. Figure 13 An exemplary plot 1310 shows test data for turbocharged engines with and without grooved pins (e.g., non-grooved pins and grooved pins). As shown, grooved pins can be used to modify NVH characteristics. In particular, rapid energy transfer, which may correspond to bearing / pin phenomena within a range of engine RPMs, can be or include, for example, the engine idle RPM, can be mitigated. In this approach, instead of altering the RPM that would otherwise be optimal for the engine idle RPM, the pins can be grooved, or grooved pins can be provided, which mitigates undesirable NVH.

[0092] Figure 14A An example of a grinding wheel 1470 is shown, which includes an end profile adapted to form one or more grooves in a pin. Figure 14B A cross-sectional view of an example pin 1407 is shown. Pin 1407 can be a blank or workpiece suitable for use without grooves, whereby one or more grooves can be formed in pin 1407 using a grinding wheel 1470; and Figure 14C A cross-sectional view of an example bearing outer ring 310 including various features is shown.

[0093] exist Figure 14A The diagram shows various dimensions, including impeller diameter D, bore diameter H, profile length X, profile width U, and profile angle V. o Such dimensions can be parameters of a grinding wheel (e.g., a cutting wheel, etc.) or other tools used to form one or more grooves in a pin or bearing.

[0094] exist Figure 14B The diagram shows various dimensions, including those along the pin axis z. p Pin length L in the direction P and the pin diameter D along a portion of the pin 1407 that can form one or more grooves. P .exist Figure 14B In the example including the pin axis z p In the plane, the grinding wheel 1470 is brought into contact with the pin 1407; note that the contact used to form the groove can be with the grinding wheel 1470 along the pin axis z. p Offset planar contact.

[0095] exist Figure 14CIn the example, bearing 310 features a compressor-side end 371, a turbine-side end 373, and lubricant injection openings 318-1 and 318-2 aligned with lubricant wells 314 and 316, respectively. Figure 14C Various dimensions are shown, including the pin opening axis z. po Bearing length L B The bearing outer diameter OD at the lubricant film formation surface 312 B (Adjacent to the pin opening 370), bearing inner diameter ID B Bearing inner diameter ID B At the axial portion of bearing 310 within the span of lubricant film forming surface 312, such that at pin opening 370, bearing 310 has a portion that can be partially formed by OD. B Subtract ID B A defined thickness. For example, in Figure 14C In the cross-sectional view, it can be seen from OD B Subtract ID from middle B And divide the result by 2 (e.g., (OD) B -ID B ) / 2) to define the thickness as the axial thickness; however, as mentioned, due to the geometry of the intersecting cylinders, the wall of the pin opening 370 may not be constant, where for a given OD B and ID B The off-axis thickness is greater than the on-axis thickness. In cases where both off-axis and on-axis grooves are formed in the bearing, the groove length can be considered relative to the thickness of the wall defining the pin opening, for example, to accommodate short-circuit lubricant flow (e.g., grooves not facing the pin surface and / or extending to ID). B (grooves). As an example, the groove length along the wall defining the pin opening can vary in the axial direction (on the shaft) and the anti-rotation direction (off the shaft), for example, to achieve a certain fraction or percentage of the bearing thickness and / or wall thickness, which can provide in ID B The groove does not extend to the inner surface. As an example, consider limiting the groove length to 75% of the bearing thickness (e.g., (OD)). B -ID B ) / 2) and / or limit the groove length to 75% of the wall thickness of the wall defining the pin opening. In such examples, the groove length limit may be less (e.g., but sufficient for one or more NVH issues) or may be greater, for example, up to about 90%, to provide greater interface coverage, despite some possible increase in lubricant leakage from the interface to the axial longitudinal bore of the bearing (e.g., where the lubricant flow from the through groove can be a lubricant short circuit).

[0096] Figure 14CExamples of grinding wheels 1470 (e.g., appropriately sized, shaped, aligned, etc.) are also shown, which are at least partially inserted into openings 370 to form one or more grooves. For example, consider aligning the plane of the grinding wheel on an axis to form one or two grooves (e.g., optionally, forming two grooves simultaneously), aligning the plane of the grinding wheel off-axis to form one or two grooves (e.g., optionally, forming two grooves simultaneously), and / or aligning the plane of the grinding wheel at a desired angle to form one or more grooves, etc.

[0097] As an example, the same grinding wheel can be appropriately sized to form pin grooves and bearing grooves. As an example, different types, sizes, and shapes of tools, etc., can be used to form one or more grooves.

[0098] As an example, one or more grooves can be formed according to one or more technical specifications, which may include location, cutting depth, cutting length, width, etc. As an example, the cutting depth may be less than approximately 5 mm, and may be less than approximately 2 mm. As an example, one method may include using a roughing grinding wheel and then using a finishing grinding wheel, which may be evaluated regarding grit size, etc.

[0099] Figure 15 Examples of profiles 1500 that can be used to form one or more trenches are shown. As shown, the profiles can be symmetrical or asymmetrical. Profile 1501 includes a central ridge with two valleys, profile 1502 includes a deep valley offset from the center, profile 1503 includes a flat valley bed with rounded walls, profile 1504 includes a flat valley bed with sloping walls, profile 1505 includes a semi-circular shape, profile 1506 includes a slightly parabolic shape, profile 1507 includes a flat bed with a single sloping wall, profile 1508 includes two sloping sections with straight portions, and profile 1509 includes a V-shape.

[0100] Regarding groove formation, methods such as milling, keyway milling, and optionally subsequent side milling can be used. As an example, grooves can be formed into cuts using cutting techniques.

[0101] As an example, a groove can have one or more contours, such as, for example, one or more of the following: elliptical, lenticular, polygonal (e.g., triangle, rectangle, etc.), circular, etc.

[0102] As an example, a groove can have a lens-shaped opening, which can be represented on a curved surface (e.g., the surface of a cylindrical pin portion).

[0103] As an example, a groove can be volumetric. As an example, a groove can be defined by a surface (such as, for example, a surface of a portion of a volumetric geometry). For example, consider an ellipsoid, which can be elongated or oblate. As another example, consider a parabola. As an example, the volume of a groove can be represented by a portion of a lenticular body of revolution, where the lenticular shape can be defined by the intersection of two arcs (e.g., two circles, two ellipses, etc.).

[0104] Regarding the oblate spheroid, it can be a "pointed" rather than a "flattened" ellipsoid, that is, an ellipsoid whose polar radius c is greater than its equatorial radius a, and therefore c > a (e.g., a central ellipsoid). Symmetrical egg-shaped objects can include the same shape at both ends and can approximate an oblate spheroid. An oblate spheroid is a surface of revolution obtained by rotating the ellipse about its major axis and has the following Cartesian equation:

[0105] .

[0106] As an example, a portion of a capsule shape can be formed, wherein the capsule is a rotating motion field shape, which is a cylinder having two hemispherical caps at either end. As an example, a portion of an elongated ellipsoid with one or two conical ends can be formed.

[0107] As explained, grooves can be provided in the pin and / or bearing, wherein the grooves extend axially relative to the longitudinal axis of the pin (e.g., or the axis of the bearing opening, etc.). As an example, one or more grooves can be defined using a cylindrical coordinate system having a z-axis along the longitudinal axis of the pin. As an example, grooves can be defined in separate coordinate systems, which can be used for corresponding shapes (e.g., geometries, etc.) that overlap or intersect with the cylindrical coordinate system. For example, consider a lenticular body of revolution defined relative to an axis of rotation, wherein the lenticular body of revolution can be positioned relative to the surface of the pin and / or the surface of the bearing represented in the cylindrical coordinate system, such that a portion of the pin and / or a portion of the bearing can become a groove partially represented by a portion of the lenticular body of revolution.

[0108] As explained, anti-rotation pins and openings in bearings can achieve various functions in a turbocharger. For example, consider the axial positioning of the rotor assembly within a bore in the center housing, where the pin can transfer the thrust load of the rotor assembly from the bearing (e.g., the outer ring or journal) to the center housing, and where the pin can limit (e.g., resist) a certain amount of rotation of the bearing (e.g., the outer ring or journal). The undesirable function of an anti-rotation pin, at least partially positioned in an opening in the bearing, can provide a transmission path for noise and vibration from the rotor assembly to the center housing.

[0109] In various types of turbochargers, during operation, an anti-rotation pin, at least partially housed in an opening in the bearing, can be the sole metal-to-metal connection between the rotor assembly and the center housing. As explained, during operation (e.g., under sufficient lubricant pressure, etc.), the outer ring can be supported in a bore in the center housing by a film of lubricant, which can be a squeeze film damper (SFD).

[0110] As explained, pins and / or bearings may be provided with one or more grooves that are in fluid communication with the SFD (Self-Damping Fluid), allowing the grooves to receive lubricant. For example, consider a pin where an axial groove feature is added near the end of the pin, where some lubricant present between the central housing and the outer ring flows through the axial groove feature to the interface region between the pin and the pin bore in the outer ring (e.g., see opening 370 of outer ring 310). In this example, the presence of lubricant at this interface promotes the formation of a lubricant film between the pin and the outer ring, which forms a damping element to reduce the transmissibility of vibrations from the outer ring to the pin. Regarding bearings, consider... Figure 12A and Figure 12B The bearing 1230, wherein surface 1236 can be a surface that can form a lubricant film region relative to the surface of the housing bore. As shown, an opening 1237 is in surface 1236, allowing lubricant to be supplied via, for example, as shown. Figure 12B Regions 1211, 1212, 1213 and 1214 flow into one or more of channels 1231, 1232, 1233 and 1234.

[0111] As explained, groove features (e.g., grooves) can be formed via one or more processes, which may include rolling and / or machining, which may be performed, for example, after turning. As explained, the process may involve removing material from the pin (e.g., see...). Figure 14B ) and / or remove material from the bearing (e.g., see Figure 14C ).

[0112] The location and / or length of the groove can be selected such that a certain amount of overlap appears in the gap between the bore wall of the central housing and the outer ring, wherein the groove can extend axially into the interface between the outer ring and the pin.

[0113] Refer again Figure 11A and Figure 11B Grooves can be constructed and locating pins positioned such that the grooves do not extend axially beyond the inner diameter of the outer ring (e.g., see...). Figure 11AIn cases where additional lubricant flow is desired to reach the space defined by the inner diameter of the outer ring, the grooves may extend beyond the inner diameter of the outer ring; however, this arrangement may be intended to limit lubricant short-circuiting within the bearing assembly, thereby reducing the lubricant flow via the lubricant nozzles of the outer ring to a level insufficient to supply lubricant to the rolling elements. To eliminate the risk of short-circuiting, in an assembled turbocharger assembly, the ends of one or more grooves of the pin may lack the inner surface of the outer ring (e.g., journal), such that lubricant in the lubricant film region (e.g., see lubricant film region 392) does not flow excessively through the one or more grooves and into the bearing assembly (e.g., REB assembly).

[0114] As in Figure 12A As shown in the example, grooves 1231, 1232, 1233, and 1234 do not extend to the inner surface 1239 of bearing 1230, which helps reduce the risk of lubricant short circuits, where it is desirable to reduce this risk. As explained, wall 1235 can extend from surface 1236 to surface 1239 and can be part of a transverse bore (e.g., a cylinder with intersecting axes, etc.). In a given geometry, where the length of the groove on the shaft is used for the groove off the shaft, because wall 1235 can be thicker off the shaft, it can be ensured that the length is not long enough for a short circuit, depending on the extent to which the pin extends into opening 1237 and overlaps wall 1235.

[0115] Parameters such as the width of the groove, the number of grooves, and the orientation of one or more grooves can be selected to preserve sufficient surface area for contact between the pin and the surface of the outer ring defining the opening of the pin. For example, groove depth can be used to increase volume rather than groove width, ensuring sufficient contact surface. When the contact surface is reduced, the force experienced by a specific surface area of ​​the pin can increase, which may cause some wear on the pin, for example, at the edges of the groove. With a limited groove width, the contact may be more uniform, allowing the edges of the groove to be close enough to experience a common level of force (e.g., stress, etc.). With a groove width that is too wide, one edge may experience a different force level than another edge, which may result in a higher force per unit area and greater wear on one edge.

[0116] As an example, the pin and / or pin socket may include a chamfer (bevel) that can form a guide for positioning and / or interference fit, which can help distribute force more evenly around the circumference of the opening. This can allow compression to occur more gradually, making the pressing operation smoother, easier to control, and so on. As an example, the shoulder around the opening of the bearing may include one or more chamfers that can allow lubricant to flow into one or more grooves in the wall of the bearing defining the opening.

[0117] Regarding thermal control, various materials expand when heated and contract when cooled. Thus, the pin can be cooled (e.g., and / or the housing can be heated, depending on the material, stress, etc.). As an example, the thermal control process may include heating and / or cooling of one or more components, where compression is caused by the thermal equilibrium of the pin in the pin socket at ambient temperature (e.g., and at the operating temperature of a turbocharger). This process can be a contraction fit process. As an example, the pin can be cooled using one or more reagents (e.g., carbon dioxide at approximately -78.5 degrees Celsius, liquid nitrogen at approximately -196 degrees Celsius, etc.). In a state below ambient temperature (e.g., below approximately 20 degrees Celsius), where the housing with the pin socket can be at least at ambient temperature, the cooled pin can be positioned in the pin socket such that the cooled pin contacts the contact surface of the pin socket to restrict axial movement. In this state, the pin and housing can remain in this position until the temperature of the pin rises, causing the diameter of the pin to expand to form an interference fit.

[0118] As an example, thermal processes involving cooling pins may be more effective for turbocharger life because heating for thermal expansion (e.g., above ambient temperature) may introduce one or more types of material property changes (e.g., tempering, etc.), may introduce undesirable stresses, etc.

[0119] As an example, a pin fitted via thermal interference may be scratch-free because the contact surface of the pin does not translate or rotate against the contact surface of the pin socket in a manner that would scratch the contact surface of the pin. In this method, one or more surfaces of the pin may be scratch-free, etc., which may mean that, to avoid debris, the bearing with the orifice is positioned by the smoother part of the pin compared to the scratched part.

[0120] As an example, the pin can be made of low-alloy steel. As an example, the center housing can be made of cast iron (e.g., gray cast iron). As an example, the pin can be a machined part (e.g., formed from a blank cylinder of low-alloy steel, etc.). As an example, the pin socket of the center housing can be formed via a machined cast center housing.

[0121] As an example, a pin may include an end socket, which may have an M configuration (e.g., M4, etc.). As an example, in the case where a machining apparatus for a central housing includes one or more tools for a threaded pin socket, the size of these tools may be determined by the "M" configuration, specifically the drill bit size. For example, consider a machining process using a 7mm drill bit for an M8 x 1 threaded socket. In this example, the 7mm diameter socket may be formed with a desired axial length, wherein the 7mm diameter socket may be tapped to form a thread, or may be left untapped (untapped), making it unthreaded. Where the socket includes a 7mm diameter portion, the pin may include a smaller diameter portion that transitions to a larger diameter portion, wherein the larger diameter portion has a diameter exceeding 7mm by approximately 0.005mm to approximately 0.1mm (e.g., 7+mm), with the aim of forming an interference fit when at least a portion of the 7mm diameter portion of the socket of the housing contacts at least a portion of the 7+mm diameter portion of the pin. As an example, the diameter of a portion of the pin may be approximately 0.015 mm to approximately 0.05 mm larger than that of a portion of the pin socket, or, for example, approximately 0.02 mm to approximately 0.04 mm larger than that of a portion of the pin socket, with the aim of forming an interference fit.

[0122] Table 1 below shows some exemplary dimensions of the “M” construction.

[0123]

[0124] As an example, a turbocharger assembly may include: a housing including a bore defined by a bore wall and a pin socket forming an opening in the bore wall; a bearing including a pin opening defined by a pin opening surface; a pin including a longitudinal pin axis and a pin surface; a groove in the pin opening surface or the pin surface, wherein the groove has an axial length; wherein, with the bearing positioned in the bore and the pin in the pin socket, and a portion of the pin in the pin opening, a gap exists between the bearing and the bore wall, wherein the groove is in fluid communication with the gap to form a lubricant supply path from the gap to the interface between the pin surface and the pin opening surface.

[0125] As an example, a groove may be present in the pin surface, wherein the axial length of the groove overlaps at least a portion of the bearing-bore wall clearance and at least a portion of the pin opening surface in the bearing to form a lubricant supply path from the clearance to the interface between the pin surface and the pin opening surface.

[0126] As an example, the bearing can be a rolling element bearing assembly (e.g., a REB assembly).

[0127] As an example, a bearing may include an outer ring, wherein the pin opening surface is a surface of the outer ring (e.g., a wall surface defining the pin opening, which may be, for example, a transverse hole intersecting the longitudinal hole of the outer ring).

[0128] As an example, a bearing can be a journal bearing. A journal bearing can be a one-piece component, which is a single piece of material. The journal bearing may include one or more journal surfaces along the bore wall, the journal surfaces forming one or more corresponding lubricant film regions relative to a rotatable shaft having one or more journal surfaces, wherein the rotatable shaft is rotatably supported by the journal bearing in a housing (e.g., a central housing).

[0129] As an example, a bearing can be positioned using a pin at least partially disposed in a pin opening of the bearing, wherein the pin can be used to restrict axial and / or rotational movement of the bearing while allowing a certain amount of movement in the radial direction (e.g., along the pin axis). Movement in the radial direction can achieve some variation in the lubricant film thickness between the outer surface of the bearing and the inner surface of the bore in the housing.

[0130] As an example, the gap between the bearing and the bore wall of the housing can define one or more lubricant film regions. For example, consider a lubricant film region adjacent to the pin opening of the bearing. As an example, the lubricant film region can be or may include a squeeze film damper region (e.g., acting as a squeeze film damper (SFD)).

[0131] As an example, the pin surface of a pin may include multiple grooves, and / or the pin opening surface of a bearing may include multiple grooves. As an example, a groove may be a groove in the pin surface, and another groove may be a groove in the pin opening surface.

[0132] As an example, in the turbocharger assembly with the pin positioned in the pin opening of the bearing, the groove can be aligned with the longitudinal axis of the bore in the housing receiving at least a portion of the bearing. In this example, in the positioned state, the bearing can translate along the longitudinal axis to form contact between the pin surface and the pin opening surface. As an example, in the positioned state, the groove can be orthogonal to the longitudinal axis of the bore in the housing. In this example, in the positioned state, the bearing can rotate clockwise or counterclockwise to form contact between the pin surface and the pin opening surface.

[0133] As an example, the groove may include a V-shaped profile in a plane, wherein the longitudinal pin axis of the pin (e.g., received or receivable in the pin opening of the bearing) is normal to the plane. As an example, the pin surface of the pin may include a groove with a V-shaped profile, and / or the pin opening surface of the pin opening of the bearing may include a groove with a V-shaped profile. As an example, in the case where grooves are present in the pin surface and the pin opening surface, the groove profiles may be different or similar; note that the pin groove may form a cylindrical outer surface of the pin pointing radially inward (into the pin), and the pin opening groove may form a cylindrical surface of the bearing pointing radially outward (into the bearing).

[0134] As an example, the groove can be a pin surface groove, wherein a portion of the axial length of the groove overlaps with the pin socket of the housing (e.g., a central housing). As an example, the pin socket of the housing can be a transverse hole intersecting a through-hole of the housing to form an opening in the wall of the through-hole, wherein a pin can extend a distance from the opening into the through-hole, for example, a distance sufficient for a portion of the pin to be received in the pin opening of a bearing at least partially disposed in the through-hole of the housing.

[0135] As an example, the pin surface may include metal, and the pin opening surface of the bearing may also include metal. In this example, during the operation of the turbocharger assembly, lubricant is supplied through the lubricant supply path from the gap to the interface between the pin surface and the pin opening surface, the lubricant reducing the energy generated at the interface by the movement of the bearing.

[0136] As an example, a turbocharger assembly may include at least four grooves in fluid communication with the interface between the pin and the bearing (e.g., the interface defined by the pin surface and the pin opening surface), wherein the movement of the bearing includes at least one of rotational movement and axial movement, and wherein the pin restricts this movement (e.g., to an amount less than about 10 degrees, to an amount less than about 5 mm, etc.).

[0137] As an example, the groove could be a pin surface groove of a pin, wherein the pin includes a head portion that includes markings for aligning the grooves in the bore of the housing. In this example, it may be desirable to align the grooves to address one or more problems, such as one or more NVH issues. For example, in the case where a turbocharger assembly is found to exhibit one or more NVH issues during operation, the pin can be oriented (e.g., rotated, etc.) to align the grooves, wherein the grooves can provide lubrication at an interface at least partially defined by the surface of the pin. This approach can target specific NVH issues that occur under specific operating conditions (e.g., the rotational speed of the turbocharger shaft, the rotational speed of the internal combustion engine, etc.). As an example, the pin may include multiple grooves, wherein the pin can be oriented in a manner that helps mitigate one or more NVH issues. As explained, markings can facilitate alignment and / or indicate which alignments can help mitigate one or more NVH issues.

[0138] As an example, the groove can be a pin surface groove of a pin, wherein the pin includes an end surface, and wherein the groove does not extend to the end surface.

[0139] As an example, the groove may be a pin surface groove of a pin, wherein the pin socket of the housing includes a mating region, wherein the pin includes a mating region to secure the pin in the pin socket relative to the mating region of the pin socket, and wherein the groove is disposed in the region between the mating region and the end surface of the pin.

[0140] As an example, a method may include: during turbocharger operation, allowing lubricant to flow into a lubricant film region between a bearing and a bore wall of a housing, wherein a pin extends from an opening in the bore wall into a pin opening defined by a pin opening surface of the bearing, and wherein a groove exists at the interface between the pin surface of the pin and the pin opening surface of the bearing; and allowing at least a portion of the lubricant to flow via the groove from the lubricant film region to the interface between the pin opening surface and the pin surface. This method can help mitigate one or more problems, such as, for example, one or more NVH problems that may occur during operation of a turbocharger assembly. As an example, in the foregoing exemplary method, the at least a portion of the lubricant at the interface may reduce the energy generated by the movement of the bearing. For example, a method may include reducing the energy generated by moving the bearing, wherein the movement of the bearing occurs simultaneously with the operation of an internal combustion engine and the flow of exhaust gas to a turbocharger including the bearing.

[0141] Although some examples of methods, devices, systems, arrangements, etc. have been shown in the accompanying drawings and described in the foregoing specific embodiments, it will be understood that the disclosed exemplary embodiments are not limiting, but are capable of many rearrangements, modifications, and substitutions.

Claims

1. A turbocharger assembly comprising: A housing, the housing including a hole defined by a hole wall and a pin socket forming an opening in the hole wall; A bearing, the bearing including a pin opening defined by a pin opening surface; A pin, wherein the pin includes a longitudinal pin axis and a pin surface; A groove in the pin opening surface or the pin surface, wherein the groove includes an axial length; In a state where the bearing is positioned in the bore and the pin is positioned in the pin socket, with a portion of the pin in the pin opening, a gap exists between the bearing and the bore wall. The groove is in fluid communication with the gap to form a lubricant supply path from the gap to the interface between the pin surface and the pin opening surface. The groove is in the pin surface, and the axial length of the groove overlaps with at least a portion of the gap and at least a portion of the pin opening surface to form a lubricant supply path from the gap to the interface between the pin surface and the pin opening surface.

2. The turbocharger assembly according to claim 1, wherein, The bearing includes a rolling element bearing assembly.

3. The turbocharger assembly according to claim 1, wherein, The bearing includes an outer ring, wherein the pin opening surface is the surface of the outer ring.

4. The turbocharger assembly according to claim 1, wherein, The bearing in question is a journal bearing.

5. The turbocharger assembly according to claim 1, wherein, The gap defines the area of ​​the lubricant film.

6. The turbocharger assembly of claim 5, wherein, The lubricant film region includes the extruded film damper region.

7. The turbocharger assembly of claim 1, wherein, The pin surface includes multiple grooves.

8. The turbocharger assembly of claim 1, wherein, The pin opening surface includes multiple grooves.

9. The turbocharger assembly of claim 1, further comprising another groove in the pin opening surface.

10. The turbocharger assembly of claim 1, wherein, In the positioned state, the groove is aligned with the longitudinal axis of the hole in the housing.

11. The turbocharger assembly of claim 1, wherein, In the positioned state, the bearing can translate to form contact between the pin surface and the pin opening surface.

12. The turbocharger assembly of claim 1, wherein, In the positioned state, the groove is orthogonal to the longitudinal axis of the hole in the housing.

13. The turbocharger assembly of claim 1, wherein, In the positioned state, the bearing can rotate clockwise or counterclockwise to form contact between the pin surface and the pin opening surface.

14. The turbocharger assembly of claim 1, wherein, In the operating state of the turbocharger assembly, lubricant is supplied through a lubricant supply path from the gap to the interface between the pin surface and the pin opening surface, the lubricant reducing the energy generated at the interface by the movement of the bearing.

15. The turbocharger assembly of claim 1, comprising at least four grooves, wherein, The movement of the bearing includes at least one of rotational movement and axial movement.

16. The turbocharger assembly of claim 1, wherein, The pin includes a head portion that includes markings for aligning the groove in the hole in the housing.

17. The turbocharger assembly of claim 1, wherein, The pin includes an end surface, and wherein the groove does not extend to the end surface.

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