Entryway system including turbocharger and VANE pack

Abstract

An entryway system including a turbocharger for receiving exhaust gas and delivering compressed air to an internal combustion engine. The system also includes a vane pack having a vane ring with a plurality of vanes disposed thereon. The vane pack includes a plurality of spacers positioned adjacent to a leading or trailing edge of a respective vane and with each spacer separated from an adjacent spacer by at least at least one vane. A vane clearance distance defined between any portion of an adjacent side of a first vane and the vane ring surface of the vane ring is greater than a vane clearance distance defined between any portion of an adjacent side of a second vane and the vane ring surface of the vane ring so as to manipulate a vane moment associated with the first vane that occurs during the operation of the system.

Description

ENTRYWAY SYSTEM INCLUDING TURBOCHARGER AND VANE PACKCROSS-REFERENCE TO RELATED APPLICATIONS

[0001] This application claims priority to and all the benefits of United States Provisional Application No. 63 / 529,182, filed July 27, 2023, which is hereby incorporated by reference in its entirety.BACKGROUND OF THE DISCLOSURE1. Field of the Disclosure

[0002] This disclosure relates generally to an entry way system including a single or divided volute turbocharger having variable turbine geometry and including aerodynamic spacers and a vane ring having a plurality of vanes.2. Description of the Related Art

[0003] Entryway systems including turbochargers receive exhaust gas from an internal combustion engine and deliver compressed air to the internal combustion engine. Turbochargers increase the power output of the internal combustion engine, lower fuel consumption of the internal combustion engine, and / or reduce emissions produced by the internal combustion engine. Delivery of compressed air to the internal combustion engine by the turbocharger allows the internal combustion engine to be smaller, yet able to develop the same or similar amount of horsepower as larger, naturally aspirated internal combustion engines. Having a smaller internal combustion engine for use in a vehicle reduces the mass and aerodynamic frontal area of the vehicle, which helps reduce fuel consumption of the internal combustion engine and improve fuel economy of the vehicle.

[0004] Some turbochargers include a turbine having a single volute turbine housing. The single volute turbine housing includes a turbine inlet, a turbine outlet, and an interior volume.The turbine inlet is configured for attachment to an internal combustion engine (e.g., to an exhaust manifold or to a cylinder head of an internal combustion engine) and includes a plurality of inlet ports configured to be in fluid communication with exhaust paths of the internal combustion engine upon attachment. The interior volume of the turbine housing delivers exhaust gas from the internal combustion engine to a turbine wheel disposed in the interior volume. After energy is extracted from the exhaust gas by the turbine wheel, the exhaust gas exits the turbine housing via the turbine outlet. The volute guides the exhaust gas from the exhaust manifold of the engine into an arcuate flow for distribution of exhaust around the circumference of the turbine wheel to rotate the turbine wheel.

[0005] Some turbochargers include a turbine having a divided volute turbine housing, with the turbochargers therefore sometimes alternatively referred to as a divided volute turbocharger (or, when two volutes are utilized, a dual volute turbocharger). The volutes of a divided volute turbine housing are generally isolated from one another such that no mixing of exhaust gas occurs until after the exhaust gas passes the tongues of the respective volutes. The divided volute turbine housing includes a turbine inlet, a turbine outlet, and an interior volume. The turbine inlet is configured for attachment to an internal combustion engine (e.g., to an exhaust manifold or to a cylinder head of an internal combustion engine) and includes a plurality of inlet ports configured to be in fluid communication with exhaust paths of the internal combustion engine upon attachment. The interior volume of the turbine housing defines at least two divided volutes in fluid communication with the respective inlet ports for delivering exhaust gas from the internal combustion engine to a turbine wheel disposed in the interior volume. After energy is extracted from the exhaust gas by the turbine wheel, the exhaust gas exits the turbine housing via the turbine outlet. The volutes guide the exhaust gas from the exhaust manifold of the engine into an arcuate flow for distribution of exhaust around the circumference of the turbine wheel to rotate the turbine wheel.

[0006] Turbochargers also include a compressor. The compressor includes a compressor wheel coupled to the turbine wheel via a shaft. The compressor is powered by the rotation of the turbine wheel, which in turn drives a compressor wheel within a compressor housing of the compressor.

[0007] To aid in directing and controlling the exhaust flow from the volute or divided volutes to the turbine wheel uniformly, a vane pack including a vane ring (sometimes alternatively referred to as a nozzle ring or vaned nozzle stator) with a plurality of vanes can be disposed on an annular disk in the turbine housing interior between the volutes and turbine wheel. These vanes can be fixed to the annular disk (sometimes alternatively referred to as a fixed nozzle ring or fixed vaned nozzle stator) or can be rotatably coupled to the annular disk (sometimes alternatively referred to as a variable nozzle ring or variable vaned nozzle stator) to create a variable turbine geometry (VTG).

[0008] In entryway systems having rotatable vanes, each of the plurality of vanes also includes a first shaft and an opposing second shaft extending from opposing flat sides of the vanes. A vane lever is coupled, and preferably fixed via riveting or welding, to the second shafts of the vanes. Each of the vane levers includes a body portion and a flange portion. The vane levers are configured to rotate each of the vanes in a coordinated manner about their respective vane pivot point (VPP) between the closed position and the open position and through the one or more intermediate positions. The adjustment ring is retained between the vane levers and the second vane ring, with the flange portion of each of the vane levers disposed within an opening in the adjustment ring.

[0009] The vane pack also typically includes a plurality of spacers disposed radially outwardly from the plurality of vanes between the vane rings. The spacers function to minimize flow disturbance of exhaust gas flowing from the volutes through the plurality of vanes to the turbine wheel.

[0010] In typical entryway systems and turbochargers having VTG, the combination of rotatable vanes and spacers provide adequate performance in terms of providing exhaust gas to the turbine blades. However, in current systems, and owing to a difference in the vane moments of the plurality of vanes during operation of the entryway system where the plurality of vanes routinely move between open and closed positions, it has been found that there can be uneven and enhanced wear on the flange portions of vane levers having higher relative vane moments relative to the majority of other vane moments.

[0011] As such, there remains a need to optimize the configuration of rotatable vanes and spacers on the vane pack for use in entryway systems and turbochargers having VTG to equalize the vane moments for each of the plurality of vanes, including those vanes which include spacers associated therewith and others that do not include spacers associated therewith, thereby reducing overall wear on the vane levers.SUMMARY OF THE DISCLOSURE AND ADVANTAGES

[0012] The entryway system includes a turbocharger for receiving exhaust gas from an internal combustion engine and for delivering compressed air to the internal combustion engine and a vane pack coupled to said turbocharger. The turbocharger includes a turbine housing comprising a turbine housing interior adapted to receive a turbine wheel having a plurality of equally spaced turbine blades, said turbine housing defining a turbine housing outlet in fluid communication with said turbine housing interior, and one or more volutes adapted for fluid communication with the internal combustion engine and said turbine housing interior for delivering exhaust gas from the internal combustion engine to said turbine housing interior. The vane pack coupled to the turbocharger includes a vane ring disposed in said turbine housing interior and around said turbine wheel, said vane ring comprising an annular disk including a vane ring surface disposed between an inner circumferential ring and an outer circumferential ring with said inner circumferential ring defining an orifice for receiving said turbine wheel,said vane ring surface including a plurality of vanes rotatably disposed thereon in a spaced apart manner along said vane ring surface with each of said vanes rotatable between an open position and a closed position including one or more intermediate positions, and a plurality of spacers disposed in a spaced apart manner on said vane ring surface and positioned circumferentially outward relative to each of said plurality of vanes with each respective one of said plurality of spacers positioned adjacent to a leading edge or a trailing edge of a corresponding respective one of said plurality of vanes and with each one of said plurality of spacers separated from an adjacent one of said plurality of spacers by at least at least one of said plurality of vanes. The entryway system includes wherein a vane clearance distance defined between any portion of an adjacent side of a first one of said plurality of vanes and said vane ring surface of said vane ring is greater than vane clearance distance defined between any portion of an adjacent side of a second one of said plurality of vanes and said vane ring surface of said vane ring so as to manipulate a vane moment associated with said first one of said plurality of vanes having said vane clearance distance that occurs during the operation of the entryway system.

[0013] The subject disclosure is also directed to a vane pack for the entryway system that includes the afore-mentioned bypass depression in the vane ring and / or additional vane ring and / or includes the altered adjacent surface or altered opposing adjacent surface of the first one of the vanes to increase the vane clearance distance between the first one of the vanes and the vane ring surface of the vane ring or the additional vane ring.

[0014] The manipulation of the vane pack to include the afore-mentioned bypass depression in the vane ring and / or additional vane ring and / or includes the altered adjacent surface or altered opposing adjacent surface of the first one of the vanes to increase the vane clearance distance functions to reduce the wear on the vane lever of the vane pack in anentryway system, and in particular in certain embodiments to reduce the wear on the vane lever associated with the first one of the plurality of vanes.

[0015] The subject disclosure is also directed to an associated method for reducing wear on the vane lever of a vane pack in an entry way system during operation of the entry way system by manipulating a vane moment associated with a first one of the plurality of vanes by increasing a vane clearance distance between any portion of an adjacent side of the first one of the plurality of vanes and the vane ring surface of the vane ring such that the vane clearance distance is greater than a vane clearance distance between any portion of an adjacent side of a second one of the plurality of vanes and the vane ring surface of the vane ring.BRIEF DESCRIPTION OF THE DRAWINGS

[0016] Other advantages of the subject disclosure will be readily appreciated, as the same becomes better understood by reference to the following detailed description when considered in connection with the accompanying drawings wherein:

[0017] FIG. 1 is a schematic representation of an entryway system including a turbocharger having variable turbine geometry and having a volute-containing turbine housing along with turbine wheel disposed in the turbine housing;

[0018] FIG. 2 is a schematic representation of an internal combustion engine and a cross- sectional end view of a single volute turbine housing of FIG. 1 adapted for fluid communication with the internal combustion engine that also includes a portion of a vane ring having rotatable vanes disposed on an annular disk and aerodynamic spacers;

[0019] FIG. 3 is a side perspective view of the turbine portion of the turbocharger of FIG.2 without the turbine wheel and turbocharger shaft;

[0020] FIG. 4 is a side section view of a portion of FIG. 3;

[0021] FIG. 5 is a schematic representation of an internal combustion engine and a cross- sectional end view of a dual volute turbine housing of FIG. 1 adapted for fluid communicationwith the internal combustion engine that also includes a portion of a vane ring having rotatable vanes disposed on an annular disk and aerodynamic spacers;

[0022] FIG. 6 is a side perspective view of the turbine portion of the turbocharger of FIG.5 without the turbine wheel and turbocharger shaft;

[0023] FIG. 7 is a side section view of a portion FIG. 6;

[0024] FIG. 8 is an exploded view of a vane pack for use in the single volute or dual volute system of FIGS. 2 or 5;

[0025] FIG. 9 is an end view of a vane of the vane ring, illustrating a vane pivot point (VPP) of the vane;

[0026] FIG. 10 is a partial end view of the plurality of vanes and spacers disposed on a second vane ring of the pair of vane rings of the vane pack adjacent to the adjustment ring and with the vane ring including a bypass depression in accordance with one embodiment of the subject disclosure;

[0027] FIG. 1 1 is a section view of the portion ofthe vane pack of FIG. 10 that also includes the first vane ring of the pair of vane rings;

[0028] FIG. 12 is a partial end view of the plurality of vanes and spacers disposed on a second vane ring of the pair of vane rings of the vane pack adjacent to the adjustment ring and with the vane ring including a bypass depression in accordance with another embodiment of the subject disclosure;

[0029] FIG. 13 is a section view of the portion of the vane pack of FIG. 12 that also includes the first vane ring of the pair of vane rings;

[0030] FIG. 14 is a partial end view of the plurality of vanes and spacers disposed on a second vane ring of the pair of vane rings of the vane pack adjacent to the adjustment ring and with the vane ring including a bypass depression in accordance with yet another embodiment of the subject disclosure;

[0031] FIG. 15 is a section view of the portion of the vane pack of FIG. 14 that also includes the first vane ring of the pair of vane rings;

[0032] FIG. 16 is a section view a portion of a vane pack illustrating a single vane of the plurality of vanes disposed between the pair of vane rings of the vane pack with the single vane including a tapered side adjacent a first vane ring of the pair of vane rings in accordance with another embodiment of the subject disclosure;

[0033] FIG. 17 is a section view a portion of a vane pack illustrating a single vane of the plurality of vanes disposed between the pair of vane rings of the vane pack with the single vane including chamfered side adjacent to a first vane ring of the pair of vane rings to defines a recessed slot in accordance with another embodiment of the subject disclosure;

[0034] FIG. 18 is a section view a portion of a vane pack illustrating a single vane of the plurality of vanes disposed between the pair of vane rings of the vane pack with the single vane including shorter length between a vane pivot point and a leading edge of the vane in accordance with still another embodiment of the subject disclosure;

[0035] FIG. 19 is a side section view illustrating the relationship of the outer surface of each of the body portions of the vane levers and the corresponding outer surface of the opening defined by the adjustment ring;

[0036] FIG. 20 is a graph plotting the magnitude of the vane moments of each of the plurality of vanes in embodiments of a single volute entryway system comparing vane packs having four spacers and six spacers and thirteen vanes; and

[0037] FIG. 21 is a graph plotting the magnitude of the vane moments of the plurality of vanes of a single volute entryway system having six spacers comparing the change in vane moment through the addition of a chamfered recessed slot on the trailing edge of vane 2, a spherical bypass depression associated with the trailing edge of vane 2, and cylindrical bypass depression associated with the trailing edge of vane 2, with vane 2 in each instancecorresponding to the vane pack having thirteen vanes and corresponding to the single vane that is not positioned either adjacent to the trailing edge or leading edge when the vane pack is in the closed position wherein vane 2 also does not have a spacer positioned adjacent to either a leading edge or a trailing edge.DETAILED DESCRIPTION OF THE DISCLOSURE

[0038] With reference to the Figures, wherein like numerals indicate like parts throughout the several views, a schematic representation of a system 30 (i.e., an entryway system 30) is shown in FIG. 1. The system 30 includes a turbocharger 32 having a turbine portion 33 for receiving exhaust gas from an internal combustion engine 34 and a compressor portion 35 for delivering compressed air to the internal combustion engine 34. Although not required, the turbocharger 32 is typically used in passenger and commercial automotive applications. However, it is to be appreciated that the turbocharger 32 may be used in nonautomotive applications such as heavy equipment applications, non-automotive diesel engine applications, non-automotive motor applications, and the like.

[0039] The turbine portion 33 includes a turbine housing 36 having an interior surface 38 defining the turbine housing interior 40. The turbine housing interior 40 is adapted to receive a turbine wheel 42 having a plurality of turbine blades 45 (see FIG. 2), here a plurality of evenly spaced turbine blades 45. In addition, the turbocharger 32 typically includes a turbocharger shaft 44, a compressor wheel 46, a compressor housing 48, and a bearing housing 50. During operation of the turbocharger 32, the turbine wheel 42 (and in particular the turbine blades 45 of the turbine wheel 42) receives exhaust gas from the internal combustion engine 34 which causes the turbine wheel 42 to rotate. When present, the turbocharger shaft 44 is coupled to and rotatable by the turbine wheel 42. When present, the compressor wheel 46 is disposed in the compressor housing 48, is coupled to the turbocharger shaft 44, and is rotatable by the turbocharger shaft 44 for delivering compressed air to the internal combustion engine 34. Thebearing housing 50 extends about the turbocharger shaft 44 between the turbine wheel 42 and the compressor wheel 46. The turbocharger 32 also typically includes bearings 52 disposed about the turbocharger shaft 44 and in the bearing housing 50 for rotatably supporting the turbocharger shaft 44.

[0040] In certain other embodiments, as shown in FIGS. 2-4, the interior surface 38 of the turbine housing 36 has a single volute 53 in fluid communication with the internal combustion engine 34 and the turbine housing interior 40 for delivering exhaust gas from the internal combustion engine 34 to the turbine housing interior 40, and hence the entryway system 30 may be referred to alternatively as a single volute entryway system 30. In certain other embodiments, the interior surface 38 of the turbine housing 36 defines a plurality of volutes separated by walls, and hence the turbine housing 36 is defined as a divided volute turbine housing. In this embodiment, as shown in FIGS. 4-6, the divided volute turbine housing 36 is a dual volute turbine housing 36 and the entryway system 30 may be referred to as a dual volute entryway system 30, where the interior surface 8 defines a first volute 54 and a second volute 56 that are respectfully separated by a wall 60. The wall 60 includes first and second tongues 61, 63, which represent different portions of the wall 60 spaced from each other that separates portions of the first and second volutes 54, 56.

[0041] The single volute 53, or the first and second volutes 54, 56, are each respectively in fluid communication with the internal combustion engine 34 and the turbine housing interior 40 for delivering exhaust gas from the internal combustion engine 34 to the turbine housing interior 40. As also shown in FIGS. 1-6, the interior surface 38 also defines a turbine housing outlet 58. The turbine housing outlet 58 is in fluid communication with the turbine housing interior 40 for discharging exhaust gas from the turbine housing interior 40. In addition, the inner surface 38 also defines a wastegate fluidically coupling the single volute 53 to the turbine housing outlet 58 or each or either of the first and second volutes 54, 56 to the turbine housingoutlet 58. The turbine housing 36 may be comprised of any suitable metal. Typically, the turbine housing 36 is comprised of iron or a steel alloy.

[0042] With reference again to FIGS. 2 and 5, the internal combustion engine 34 includes a plurality of cylinders 68. In the illustrated embodiments, the internal combustion engine 34 includes three cylinders 68 for the single volute entryway system (see FIG. 2) and six cylinders 68 for the dual volute entryway system 30. However, it is to be appreciated that the internal combustion engine 34 may include any number of cylinders 68 in either the single volute entryway system 30 or dual volute entryway system 30. For example, the internal combustion engine 34 may include two cylinders 68, four cylinders 68, six cylinders 68, eight cylinders 68, or more cylinders 68. The internal combustion engine 34 may also include an odd number of cylinders (e.g., three cylinders 68 or five cylinders 68). The internal combustion engine 34 may have a V-engine configuration, a flat / boxer engine configuration, a W-engine configuration, an inline engine configuration, and the like. In the illustrated embodiments of FIGS. 2 and 5, the interna] combustion engine 34 has an inline engine configuration.

[0043] For the dual volute entryway system of FIGS. 5-7, the internal combustion engine 34 includes a first group of cylinders 70 and a second group of cylinders 72. In this illustrated embodiment, the first and second groups of cylinders 70, 72 each include half of the cylinders 68 that are included in the internal combustion engine 34. For example, when the internal combustion engine 34 includes six cylinders 68 as shown in FIG. 5, the first group of cylinders 70 includes three of the cylinders 68 and the second group of cylinders 72 includes the other three of the cylinders 68. The first and second groups of cylinders 70, 72 produce exhaust gas in a series of pulses corresponding to an exhaust stroke of each of the first and second groups of cylinders 70, 72. Timing of the exhaust strokes of the cylinders 68 is such that pulses of exhaust gas are alternately emitted from the first group of cylinders 70 and the second group of cylinders 72.

[0044] For ease of description, additional aspects of this subject disclosure may be described with respect to a generic entryway system 30 having a volute 57 that is equally applicable to a single volute entryway system (i.e., with a single volute 53) or a dual volute entryway system 30 (having volutes 54, 56) unless specifically distinguished below.

[0045] In addition to the turbocharger 32, best shown in FIGS. 2, 5, 8, and 10, the entryway system 30 also includes a vane pack 80. The vane pack 80 includes a vane ring 100, and more typically a pair of spaced apart vane rings 100 (referred to hereinafter as either vane rings 100 or as a first vane ring 100 A and a second vane ring 100B (or a vane ring 100 A and an additional vane ring 100B)) disposed in the turbine housing interior 40 between volute 57 and around the turbine wheel 42, with the vane rings 100 having plurality of vanes, shown as first and set of vanes 130 and 140, rotatably disposed to and between each of the vane rings 100, 100A, 100B in a symmetric or in an asymmetric vane pattern, and preferably as shown in the FIGS, and described hereinafter in a symmetric vane pattern. The entryway system 30 also includes a plurality of spacers 400 disposed in a spaced apart manner on and between the vane rings 100, 100A, 100B, with the vanes on the vane rings 100, 100A, 100B and spacers 400 functioning to control the flow of exhaust gas flowing from the one or more volutes 54, 56 to the turbine wheel 42. In particular, the spacers 400 function to minimize flow disturbance of exhaust gas flowing from the one or more volutes 54, 56 to the turbine wheel 42.

[0046] Each vane ring 100 includes or otherwise comprises an annular disk 101 disposed in the turbine housing interior 40 between the divided first and second volutes 54, 56 and the turbine wheel 42. In certain embodiments (see FIG. 8 for example) where there are a pair of spaced apart vane rings 100 A, 100B, the vane rings 100 A, 100B include or comprise a pair of spaced apart annular disks 101 A, 10 IB (the annular disk 101 A may sometimes referred to as a first annular disk 101 A or a lower annular disk 101 A, while the annular disk 101B maysometimes referred to as a second annular disk 101B or upper annular disk 10 IB or more generally as a second vane ring 100B).

[0047] In the embodiments illustrated herein, the plurality of vanes 130, 140 are rotatably disposed between each of the vane rings 100A, 100B in the afore- mentioned symmetric or asymmetric pattern, and in particular are shown in the FIGS, disposed in a symmetric vane pattern in which each of the vanes 130, 140 are equally spaced from one another and are equally spaced relative to an inner and outer circumferential edge 104, 106, defined below. In these embodiments, the spacers 400 also function to provide an axial separation function between the first and second vane rings 100 A, 100B and are disposed between each of the vane rings 100 A, 100B.

[0048] As best shown in FIGS. 2, 5 and 8, each vane ring 100 includes a vane ring surface 102 which includes an inner vane ring surface 102 A and an opposing outer vane ring surface 102B extending between the inner circumferential edge 104 and the outer circumferential edge 106. In the embodiment illustrated, the inner circumferential edge 104 defines a circular orifice for receiving the turbine wheel 42 of the turbocharger 32.

[0049] In each of the illustrated embodiments, the vane ring 100 is illustrated as being circular in shape, and the inner and outer circumferential edges 104, 106 are also described and illustrated as being circular. However, in other embodiments applicable herein, the vane ring(s) 100 may be non-circular in shape, and hence one or both of the inner and outer circumferential edges 104, 106 may also be non-circular. As such, the term “vane ring”, as in “vane ring 100”, specifically describes both circular and non-circular shapes on the inner and / or the outer circumferential edges 104, 106.

[0050] For dual volute entryway systems, each vane ring 100, 100A, 100B is disposed in the turbine housing 36 with the first and second tongue 61, 63 each separately terminating at a position adjacent to the outer circumferential ring 106.

[0051] In single volute entryway systems 30, as shown best in FIG. 2, each vane ring 100,100A, 100B is disposed in the turbine housing 36 the first set of vanes 130 (i.e., a first set of at least two vanes 130) and the second set of vanes 140 are each rotatably disposed in a spaced apart manner from one another such that the second set of vanes 140 such that each vane 130 or 140 is positioned downstream of a portion of the volute 53. Each of the vanes 130, 140 are rotatable along the vane ring surface 102, and in particular are rotatable along the inner vane ring surface 102 A of a respective vane ring 100, 100A, 100B about a vane pivot axis (corresponding to a vane pivot point VPP - see FIG. 9) between a closed position and an open position and through one or more intermediate positions between the closed and open position. The vane pivot axis VPA as defined herein and as illustrated in FIG. 9, extends in a direction normal to a plane defining the vane ring surface 102 of the vane ring 100.

[0052] For dual volute entryway systems 30, as shown best in FIG. 5 the first set of vanes 130 (i.e., a first set of at least two vanes 130) are rotatably disposed in a spaced apart manner from one another on the vane ring surface 102 such that the first set of vanes 130 are positioned downstream of the first volute 54. Still further, the second set of vanes 140 are rotatably disposed in a spaced apart manner from one another such that the second set of vanes 140 (i.e., a second set of at least two vanes 140) are positioned downstream of the second volute 56. Similar to the single volute entryway system 30, each of the vanes 130, 140 are rotatable along the vane ring surface 102, and in particular are rotatable along the inner vane ring surface 102A of a respective vane ring 100, 100A, 100B about a vane pivot axis (corresponding to a vane pivot point VPP - see FIG. 9) between a closed position and an open position and through one or more intermediate positions between the closed and open position (the open, closed and one intermediate position are best illustrated and described with respect to FIGS. 2, 5, and 10-16 below). The vane pivot axis VPA as defined herein, extends in a direction normal to a plane defining the vane ring surface 102 of the vane ring 100.

[0053] In the embodiments illustrated in FIGS. 2 and 5, the first set of vanes 130 includes seven vanes 130 positioned adjacent to one another of the vane ring surface 102 around the vane ring 100, while the second set of vanes 140 includes six vanes 140 positioned adjacent to one another of the vane ring surface 102 around the vane ring 100. Accordingly, there are a total of thirteen vanes 130, 140 on the vane ring 102 in the embodiment of FIGS. 2, 5 and 8, which provide exhaust flow to the turbine wheel 42 having the ten equally spaced turbine blades 45. While the embodiments provided herein include thirteen vanes 130, 140, alternative relative amounts of vanes and blades are contemplated, preferably wherein the number of vanes 130, 140 is a different odd number, such as a prime number and wherein the number of turbine blades 42 on the turbine wheel 42 does not equal the number of vanes 130, 140.

[0054] As best illustrated in FIG. 9, each of the vanes 130 and 140 extends in length between a leading edge 132, 142 and a trailing edge 134, 144 and includes an adjacent edge 225 and an opposing adjacent edge 227 that each respectively and separately connect the leading edge 132, 142 to the trailing edge 134, 144. Still further, the adjacent edge 225 and the opposing adjacent edge 227 respectively define vane surfaces 225A and 227A (i.e., an adjacent vane surface 225A and an opposing adjacent vane surface 227A, see FIG.8). Further, as best illustrated in FIG. 8, each of the plurality of vanes 130, 140 also includes a first shaft 133, 143 and an opposing second shaft 137, 147 extending from opposing flat sides of the vanes 130, 140. A vane lever 153 is coupled, and preferably fixed via riveting or welding, to the second shafts 137, 147 of the vanes 130, 140. In other embodiments, the vane levers 153 may be coupled by swaging, or through bolting, and the like. Each of the vane levers 153 includes a body portion 157 and a flange portion 159. The vane levers 153 are configured to rotate each of the vanes 130 and 140 in a coordinated manner about their respective vane pivot point (VPP) between the closed position and the open position and through the one or more intermediate positions, as will be explained further below. In certain embodiments, such asshown in FIG. 8, 11, 13 and 15, an adjustment ring 199 is retained between the vane levers 153 and the second vane ring 100B, with the flange portion 159 of each of the vane levers 153 disposed within an opening 201 in the adjustment ring 199, with the adjustment ring 199 defining each respective opening 201 and with the opening 201 being further defined by an inner surface 202 of the adjustment ring 199.

[0055] As also shown in FIG. 8, an assembly 203 including a pin 205 and block 207 is affixed to the adjustment ring 199, such as by riveting or welding, with a pivot having a pivot shaft (not shown) connecting the assembly 203. The pivot shaft is rotated by a linkage (not shown) connected to an actuator (not shown). The actuator rotates the linkage on the basis of a particular engine operating condition to adjust the flow of exhaust gas through the vanes 130, 140. In particular, the actuator rotates the linkage, which rotates the pivot shaft and adjustment ring 199 through the assembly 203. The rotation of the adjustment ring 199 causes the adjustment ring 199 to contact the vane levers 153 and rotates the vane levers 153 in response, which in turn causes the coupled vanes 130, 140 to move between the closed and open positions and through one or more intermediate positions to adjust the flow of exhaust gas through the vanes 130, 140 on the basis of an engine operating condition, such as engine speed.

[0056] More in particular, as best shown in FIGS. 8 and 19, the flange portion 159 of the vane levers 153 defines an open drive surface 159A, a closed drive surface 159B, and a rampart 159C connecting the open drive surface 159A and closed drive surface 159B. The rampart 159C functions to locate and limit the radial motion of the adjustment ring 199. The open drive surface 159A moves in rolling and sliding contact with the inner surface 202 of the opening 201 of the adjustment ring 199 as the vane pack 80 opens towards the intermediate and opened positions, while the closed drive surface 159B moves in rolling and sliding contact with the inner surface 202 of the opening 201 of the adjustment ring 199 as the vane pack 80 closed towards the closed position from the open or intermediate positions. As will be describedbelow, the subject disclosure provides solutions to limit the wear of the vane levers 153 along the open and closed drive surfaces 159A, 159B of the vane levers 153, and in particular of the vane lever 153 associated with the respective vane 130’ or 140’ that does not include a spacer 400 positioned adjacent to either its leading end 132 or 142 or trailing end 134 or 144 during normal operation by increasing a vane clearance distance VCD between one of the plurality of vanes 130 or 140 and a vane ring surface of one or both of the vane rings 100, 100A, 100B.

[0057] Each of the vane rings 100, 100A, 100B also defines a plurality of first openings 107 between the inner circumferential edge 104 and an outer circumferential edge 106, with the number of openings 107 corresponding to the number of the plurality of vanes 130, 140 and configured to receive a shaft 133, 137, 143, 147 of a respective one of the plurality of vanes 130, 140, as will be explained further below. The openings 107 therefore further define the vane pivot point (VPP) of the respective one vane of the plurality of vanes 130, 140 disposed therein. In embodiments that include the first and second vane rings 100A, 100B, the plurality of openings 107 in at least one the first and second vane rings 100A, 100B extend from the inner vane ring surface 102 A to the outer vane ring surface 102B such that the entirety of the second shafts 137, 147 extends through the opening 107 of the second vane ring 100B such that the vane levers 153 are positioned within the turbine housing interior 40 between the outer vane ring surface 102B of the second vane ring 100B and the turbine housing 36.

[0058] Referring back to FIGS. 2, 5 and 8, and as noted above, the entryway system 30 also includes a plurality of spacers 400. In particular, the plurality of spacers 400 are disposed in a spaced apart manner on the vane ring surface 102 of the vane ring 100 of the vane ring 100 (or along the inner vane ring surface 102 A of each of the spaced apart vane rings 100A, 100B) and positioned circumferentially outward from each vane of the first and second set of vanes130, 140. The spacers 400 in conjunction with the vanes 130, 140, function to adjust the flowof exhaust gas entering from the volute 53 or the respective first or second volute 54, 56 prior to being received by the turbine blades 45.

[0059] In the embodiment of FIGS. 2 and 5, each spacer 400 is disposed in a spaced apart manner on the vane ring surface 102 and positioned circumferentially outward relative to each of the plurality of vanes 130, 140 with each respective one of the plurality of spacers 400 positioned adjacent to the leading edge 132, 142 or the trailing edge 134, 144 of a corresponding respective one of the plurality of vanes 130, 140.

[0060] The term “adjacent to”, as defined herein with respect to the relationship of the spacers 400, refers to the positioning of the respective spacers 400 circumferentially outward of the vanes 130, 140 and along a radial line (RL) extending from the axis of rotation A-A of the turbine wheel 42 to the outer circumferential edge 106.

[0061] Accordingly, in embodiments having a total of thirteen vanes 130, 140, there are a plurality of spacers 400 disposed on the vane ring 100, 100 A, 100B, with one respective spacer 400 positioned adjacent to the leading edge 132, 142 or the trailing edge 134, 144 of a corresponding one vane of six respective vanes 1 0, 140.

[0062] In the embodiments described and illustrated herein in accordance with the present disclosure, each one of the plurality of spacers 400 is separated from an adjacent one of the plurality of spacers 400 by at least one of the plurality of vanes 130, 140. In other words, the number of vanes 130, 140 is double the number of spacers 400 (i.e., is 2N, where N is the number of spacers and 2N is the number of vanes) in embodiments having an even number of vanes 130, 140 (such as entryway systems 30 having twelve vanes 130, 140) or is one more than double the number of spacers 400 (i.e., 2N + 1, where N is the number of spacers) in embodiments having an odd number of spacers 400 (such as entryway systems 30 having thirteen vanes 130, 140 as shown in the FIGS, herein).

[0063] In a preferred embodiment, the spacing between each pair of the adjacent spacers140 that include exactly one vane 130 or 140 therebetween, measured as a radial distance, is the same. The spacing SI (see FIG. 2) between the pair of adjacent spacers 400 separated by a pair of vanes 130 or 140, also measured as a radial distance, in entryway systems 30 having an odd number of vanes 130, 140 is greater than the spacing S2 of the remaining one adjacent pair of spacers 400 (also see FIG. 2) that are separated by the additional vane 130’ or 140’, and in certain embodiments S2 is two times the distance as SI.

[0064] Referring now to FIG. 9, the vane pivot point (VPP) of the individual vanes 130, 140 are illustrated, which represents the point along the vane 130, 140 around which the 130, 140 rotates in a rotational direction about a pivot axis normal to the vane ring surface 102 between the open position, the closed position, and each of the intermediate positions. The vane pivot point (VPP) of the individual vanes 130, 140 are also defined as a distance “x”, from the leading edge 132, 142 and along the mean line ML. The mean line ML (e.g., a mean chord line) is defined by a locus of points positioned between a leading edge 132, 142 and a trailing edge 134, 144 of the individual vane 130, 140 that extend through vane pivot point (VPP), which is typically respectively positioned halfway between a first side and an opposing second side of individual vane 130, 140. The leading edges 132, 142 are used by convention herein, however the vane pivot point (VPP) of an individual vane 130, 140 could alternatively be defined as a distance “y”, from the trailing edge 134, 144 and along the mean line ML and arrive at the same vane pivot point (VPP). The distance “x” defining the VPP is located at a distance from the leading edge 132, 142 to the trailing edge 134, 144 corresponding to a length x (see FIG. 9) of the mean chord line ML, such as from about 20 to 45 percent of the total length of the mean chord line ML, with the length y equal to the remainer of the total length of the mean chord line ML. Notably, however, while the location of the VPP may be the same or different for each individual vane 130, 140, the VPP’s for each of the vanes 130 and 140 onany given vane ring 100 are positioned in the same relative location when a symmetric vane is utilized (i.e., the lengths x and y on the vanes 130, 140 are constant in a symmetric vane pattern). In the embodiments provided herein, the vane pivot point (VPP) of the respective vanes 130, 140 corresponds to a line extending along the length of shaft 133, 137, 143, 147 of the respective vane 130, 140 and within the respective opening 107 of the respective vane ring 100, 100A, 100B.

[0065] While not illustrated, a vane angle (a) is defined as the angle made by a radial line RL (see FIG. 10) extending from the axis of rotation A- A of the turbine wheel 42 through the vane pivot point (VPP) and a tangent line TL (not shown) to the bottom of the respective vane 130, 140. As an alternative, the tangent line TL could be defined by a straight chord line passing through a leading edge and trailing edge of the vane. The angle of the tangent line TL relative to the radial line RL is a function of relative radial distances of the leading edge 132, 142 (defined as a first radial distance) and the trailing edge 134, 144 (defined as a second radial distance) of a respective vane 130, 140. Typically, the first radial distance is equal to or greater than the second radial distance, with the vane angle (a) ranging from 90 degrees (a maximum theoretical vane angle (a) when the first radial distance is equal to the second radial distance) (a minimum theoretical vane angle (a) when the first radial distance is maximized and the second radial distance is minimized such that the tangent line TL is coextensive with the radial line RL). As the vane angle (a) decreases from a theoretical maximum vane angle (a) of 90 degrees towards a theoretical minimum vane angle (a) of 0 degrees, the flow of exhaust gas from the volute 54, 56 to the turbine wheel 42 disrupted by the respective vane 130, 140 is correspondingly decreased.

[0066] The vane angles (a) also are used to describe the closed position, the open position, and each of the intermediate positions of the respective vanes 130, 140. In particular, in the closed position (see for example FIGS. 10, 12 and 14), the leading edge 132, 142 of eachrespective one vane of the plurality of vanes 130, 140, is positioned adjacent to the trailing edge 134, 144 of an adjacent one vane of the plurality of vanes 130, 140, and thus the vane angle (a) is from 85 to 95 degrees, such as from 88 to 90 degrees, such as about 90 degrees, such as 90 degrees, which also is referred to herein as a 0% vane opening. The term “adjacent to”, as used in this context, refers to aposition where the leading edge 132, 142 of the respective one vane of the plurality of vanes 130, 140, is in contact with the trailing edge 134, 144 of the adjacent one vane of the plurality of vanes 130, 140. The term “adjacent to” can also refer to wherein there is a very small gap between the leading edge 132, 142 of the respective one vane of the plurality of vanes 130, 140, or wherein the leading edge 132, 142 is in contact with the trailing edge 134, 144 of the adjacent one vane of the plurality of vanes 130, 140. A “small gap”, as defined herein, accounts for the range of vane angles (a) from 85 to 95 degrees as defined above. Conversely, in the open position, which is typically used when the engine is operating at high engine speeds, the leading edge 132, 142 of each respective one vane of the plurality of vanes 130, 140, is spaced at a maximum distance from the trailing edge 134, 144 of an adjacent one vane of the plurality of vanes 130, 140. In certain embodiments, such as in shown in FIGS. 10, 12 and 14, the vane angle (a) is between 30 and 65 degrees, such as from 35 to 55 degrees, such as from 40 to 45 degrees, such as about 45 degrees, such as 45 degrees in the closed position. The intermediate positions refer to any position between the closed position and the open position, and thus the vane angle (a) is between the vane angle (a) defining the closed position and the vane angle (a) defining the open position.

[0067] As noted above, the subject disclosure is directed to reducing wear in the vane levers 153, in in particular with a single vane 130’ or 140’ (see FIGS. 10, 12 and 14) of the plurality of vanes 130, 140 that does not include a respective one of said plurality of spacers 400 disposed adjacent to the leading edge 132 or 142 or disposed adjacent to the trailing edge 134 or 144.

[0068] In entryway systems 30 in which the magnitude of the vane moment varies from vane 130, 140 to vanel30, 140 , it is common for the vane levers 153 to wear unevenly, particularly in areas where the vane lever 153 contacts the interior surface 202 of the adjustment ring 199. In particular, the wear of the vane levers 153 is higher when the vanes 130, 140 have a higher magnitude of a vane moment relative to the other vanes in the entryway system of vanes that have lower vane moments. In the embodiments of FIG. 2 and FIG. 5, the highest magnitude of vane moments of the plurality of vanes 130, 140 are associated with the single vane 130’ or 140’ (see FIGS. 20 and 21) not including the spacer 400.

[0069] To lower the magnitude of vane moments of certain of the vanes to correspond to the magnitude of the other vanes, as noted previously, spacers 400 are introduced radially outwardly from certain of the vanes 130, 140 in these entryway systems 30. However, the inclusion of spacers 400 limits or otherwise alters the flow of exhaust gas through the vanes 130, 140 in the various open and intermediate positions, and thus limits the efficiency and the ability of the turbocharger to rotate the turbine blades 45 at the given vane position. Accordingly, a careful balance between the number of spacers 400 provided and the number of vanes 130, 140 is desirable to achieve both efficiency and reduce wear in the vane levers 153, wherein the addition of spacers 400 allows a desirable amount of exhaust gas movement while maintaining a positive vane moment associated with each of the vanes 130, 140 so as to limit the wear on the vane levers 153.

[0070] The present disclosure provides ways to equalize the magnitude of the vane moments of each of the vanes 130, 140 in single volute and dual volute entryway systems 30 in which the number of spacers 400 is less than or equal to one-half of the vanes 130, 140 and in which the magnitude of each of the vane moments is greater than zero. By achieving equalized and positive vane moment magnitudes at each of the vanes 130, 140, vane lever 153 wear associated with the contacting of the open drive surface 159A and the closed drive surface159B and a respective portion of the inner surface 202 of the openings 201 in the adjustment ring 199 are minimized and equalized. In addition, such equalization and positive vane moment magnitudes allow the exhaust gas to rotate the turbine blades efficiently and effectively 45 at a given vane 130, 140 open, intermediate or closed position as desired.

[0071] To achieve this equalized and positive vane moment magnitudes (sometimes simply referred to as vane moments), the present disclosure provides modifications or alterations on one or both of the vane rings 100, 100A, 100B, or on one or more of the vanes 130, 140, that reduces the vane moment on the respective vane 130, 140, and in particular reduces the vane moment on vane 130’ or 140’ not including a spacer 400, with the resultant vane moment being equalized relative to the vane moments of the other vanes 130 140 in the entry way system 30 that include spacers 400 associated therewith.

[0072] In certain embodiments, the modification or alteration described above includes modifying the vane ring surface 102 of one, or both, of the annular disks 101, 101 A, 101B of the vane rings 100, 100A, 100B to include a bypass depression 500 extending within the vane ring surface 102A of the vane ring 100, 100 A, 100B. More in particular, the modification described above includes modifying the vane ring surface 102 A of one, or both, of the annular disks 101, 101A, 101B of the vane rings 100, 100A, 100B to include a bypass depression 500 positioned along the annular disk 101, 101 A, 101B at a position adjacent to the corresponding vane 130 or 140 associated therewith and extending within the vane ring surface 102 A of the vane ring 100, 100 A, 100B.

[0073] In certain of these embodiments, the vane ring surface 102A of annular disk 101, 101 A, 10 IB of vane ring 100, 100 A 100B has been modified to include a bypass depression 500 positioned along the annular disk 101, 101 A, 101B at a position adjacent to the corresponding vane 130’ or 140’ associated therewith and extending within the vane ringsurface 102A of the vane ring 100B adjacent to the vane 130’ 140’ when the vane 130’ 140’ is in the closed position.

[0074] In one exemplary embodiment as illustrated in FIGS. 10-15, the vane ring surface 102A of annular disk 101B of vane ring 100B has been modified to include a bypass depression 500 positioned along the annular disk 101B at a position adjacent to the length x of the corresponding vane 130’ or 140’ between the vane pivot point VPP and the leading edge 132 or 142 and extending within the vane ring surface 102A of the vane ring 100B adjacent to the vane 130’ 140’ when the vane 130’ 140’ is in the closed position.

[0075] As also shown in FIGS. 10-15, the width W1 of the bypass depression 500 (see FIG. 10), measured in a direction parallel to a length of the associated one 130’ or 140’ of the plurality of vanes 130, 140 when the associated one 130 or 140 of the plurality of vanes 130, 140 is in the closed position, is less than or equal to the length x (see FIG. 9) of the associated one 130 or 140 of the plurality of vanes 130, 140 as measured from a vane pivot point VPP to the leading edge 1 2 or 142 of the associated one 130 or 140 of the plurality of vanes 1 0, 140, and wherein the bypass depression 500 is disposed entirely beneath the length x of the associated one 130 or 140 of the plurality of vanes 130, 140 between the vane pivot point VPP and the leading edge 132 or 142 when the associated one 130 or 140 of the plurality of vanes 130, 140 is in the closed position.

[0076] In addition, in the embodiments as shown in FIGS 10-15, the width WW1 of the bypass depression 500, measured in a direction along the annular disk 101, 101 A, 101B normal to the length x of the vane 130, 140 in the closed position (see FIG. 10), may extend to a position adjacent to, but spaced from, the inner circumferential edge 104 of the respective vane disk 100, 100A, 100B and / or may extend to a position adjacent to, but spaced from the outer circumferential edge 106 of the respective vane disk 100, 100A, 100B.

[0077] While FIGS. 10-15 illustrate the bypass depression 500 positioned along the annular disk 101 A at a position adjacent to the length x of the corresponding vane 130’ or 140’ between the vane pivot point VPP and the leading edge 132 or 142 and extending within the vane ring surface 102A of the vane ring 100B adjacent to the vane 130’ 140’ when the vane 130’ 140’ is in the closed position, in other embodiments the bypass depression 500 may be positioned along the annular disk 101 A at a position adjacent to the length y of the corresponding vane 130’ or 140’ between the vane pivot point VPP and the trailing edge 134 or 144 and extending within the vane ring surface 102A of the vane ring 100B adjacent to the vane 130’ 140’ when the vane 130’ 140’is in the closed position. Even further, is still other related embodiments, a pair of bypass depressions 500 may be included, with a first one of the pair of bypass depressions positioned adjacent to the length x of the vane 130’ or 140’ as described above, and with the second one of the pair of depressions 500 positioned adjacent to the length y as described abovel30’ or 140’.

[0078] In still further related embodiments, one or more additional bypass depressions 500 may alternatively be positioned at any other desirable location and extending within the vane surface 102 A of the vane ring 100 A with the same parameters as described above. In yet still further embodiments, the one or more additional bypass depressions 500 may be positioned at any other desirable location and extending within the vane surface 102 A of the vane ring 100A in conjunction with the bypass depressions 500 positioned at the locations as described above and extending within the vane surface 102 A of the vane ring 100B.

[0079] In each of these respective embodiments, the annular disk 101, 101A, 101B of the respective vane ring 100, 100A, 100B within the respective bypass depression(s) 500 defines a vane ring surface 102A’. This vane ring surface 102A’ is positioned further from the vane surface 225A of the adjacent side surface 225 of the vane 130’, 140’ than the remainder of the vane ring surface 102A not contained within the bypass depression. Accordingly, a vaneclearance distance VCD, defined between the vane ring surface 102A’ and the vane surface225A of the adjacent side surface 225, is greater than the corresponding clearance distance CD, defined between the vane ring surface 102A and the vane surface 225A of the adjacent side surface 225.

[0080] In certain embodiments, such as shown in FIGS. 10 and 11, the bypass depression 500 is in the form of a sphere, and hence is further defined as a spherical bypass depression 500A. In this embodiment, the vane ring surface 102A’ defined within the spherical bypass depression 500A, is curved and defines an apex 504, which also defines the depth DI of the spherical bypass depression 500A beneath the vane ring surface 102A. In addition, the intersection of the vane ring surface 102A’ of the spherical bypass depression 500A and the vane ring surface 102 A defines a circular edge 506. In addition, the vane clearance distance VCD is defined between the vane ring surface 102A’ corresponding to the apex 514, and the vane surface 225 A of the adjacent side surface 225.

[0081] In certain embodiments, such as shown in FIGS. 12 and 13, the bypass depression 500 is in the form of an ellipsoid, and hence is further defined as ellipsoid bypass depression 500B. In this embodiment, the vane ring surface 102A’ defined within the ellipsoid bypass depression 500B, is curved and defines an apex 514, which also defines the depth D2 of the ellipsoid bypass depression 500B beneath the vane ring surface 102A. In addition, the intersection of the vane ring surface 102A’ of the ellipsoid bypass depression 500B and the vane ring surface 102A defines an elliptical edge 516. The elliptical edge 516 includes a major width MW along its major length and a minor width MMW defined normal to the major width MW. In certain embodiments, such as shown in FIGS. 12 and 13, the major width MW is positioned to align parallel with, or substantially parallel with, the mean chord length ML of the vane 130’ or 140’ when the vane 130’ or 140’ is moved to the closed position. In other embodiments, the minor width MMW is positioned to align parallel with, or substantiallyparallel with, the mean chord length ML of the vane 130’ or 140’ when the vane 130’ or 140’ is moved to the closed position. In still other embodiments, the major width MW and the minor width are respectively positioned to align transverse with the mean chord length ML of the vane 130’ or 140’ when the vane 130’ or 140’ is moved to the closed position.

[0082] In addition, the vane clearance distance VCD is defined between the vane ring surface 102A’ corresponding to the apex 514 and the vane surface 225 A of the adjacent side surface 225.

[0083] In certain embodiments, such as shown in FIGS. 14 and 15, the bypass depression 500 is in the form of a cylinder, and hence is further defined as a cylindrical bypass depression 500C. In this embodiment, the vane ring surface 102A’ is a circular shaped bottom surface 224 defined within the spherical bypass depression 500A that defines a depth D3 of the cylindrical bypass depression 500A beneath the vane ring surface 102 A. In addition, the intersection of the vane ring surface 102A’ of the cylindrical bypass depression 500A and the vane ring surface 102A defines a circular edge 526. In addition, the vane clearance distance VCD is defined between the vane ring surface 102A’ corresponding to the circular shaped bottom surface 224, and the vane surface 225A of the adjacent side surface 225.

[0084] In addition, the vane clearance distance VCD is defined between the vane ring surface 102 A’ corresponding to the bottom surface 224 of the cylindrical bypass depression 500A, and the vane surface 225A of the adjacent side surface 225.

[0085] In each of the embodiments of FIGS. 10-15, the depth DI, D2, D3 of the respective bypass depression 500A, 500B, 500C may vary between greater than 0% and less than 100% of the thickness of the respective annular disk 101B, with the increased depth DI, D2, D3 allowing more exhaust gas to flow between the vane 130’ , 140’ and the vane ring surface 102A’ when the respective vane 130’, 140’ is in the closed position, or even in certain intermediate positions, which in turn alters the vane moment of the vane 130’, 140’ associated with therespective bypass depression 500A, 500B, 500C. In certain embodiments, the depth DI, D2,D3 of the respective bypass depression 500A, 500B, 500C is between 0.1% and 25% of the thickness of the annular disk 101B. While not shown, the depth of a respective bypass depression 500 located in alternative locations on the annular disk 101B, or the depth of a respective bypass depression 500 located in alternative locations on the annular disk 101 A, may vary in accordance to the embodiments illustrated in FIGS. 10-15.

[0086] In still further embodiments, as an alternative or in addition to adding the bypass depression 500 as illustrated in representative embodiments of FIGS. 10-15 or as described above, one or more of the vanes 130 or 140 of the plurality of vanes 130, 140, and in particular vane 130’ or 140’, can be modified to reduce the vane moment of the respective one vane 130, 130’ or 140, 140’.

[0087] In certain embodiments, such as shown in FIG. 16, a vane surface 252A defined along an opposing adjacent side 252 of one vane 130 or 140 (shown in FIG. 16 as vane 130’ or 140’) of the plurality of vanes 130, 140 and extending between the vane pivot point VPP and the leading edge 132, 142 is tapered. In these embodiments, a vane clearance distance CD1 defined between the vane surface 252A of the associated vane 130, 130’ or 140, 140’ of the plurality of vanes 130, 140 and the vane ring surface 102A, 102A’ of the vane ring 100 increases in a direction from the vane pivot point VPP to the leading edge 132 or 142 of the associated one vane 130, 130’ or 140, 140’ of the plurality of vanes 130, 140.

[0088] In the embodiment of FIG. 16, the degree of tapering, measured as an angle a between a plane defining the vane surface 102A of the respective annular disk 101 (shown in FIG. 16 as annular disk 101 A) and a plane defined by the tapered vane surface 252A may vary between greater than 0 degrees and less than 90 degrees. In certain embodiments, the angle a varies between greater than 0 degrees and 30 degrees. Notably, increasing the angle a allows more exhaust gas to flow between the vane 130’, 140’ and the vane ring surface 102, 102A’when the respective vane 130’, 140’ is in the closed position, or even in certain intermediate positions, which in turn alters the vane moment of the vane 130’, 140’ having the tapering.

[0089] While the embodiment of FIG. 16 illustrates a tapered vane surface 252A associated with the annular disk 101 A of the vane ring 100A, in other embodiments a tapered vane surface 250A (shown in phantom in FIG. 16) may also be formed, or alternatively be formed, on the adjacent side 250 of the one vane 130, 130’ or 140, 140’ extending between the vane pivot point VPP and the leading edge 132 or 142 associated with the annular disk 10 IB of the vane ring 100B.

[0090] Even still further, in additional alternative embodiments, the tapered vane surface may be formed on the adjacent side 250, and / or the opposing adjacent side 252, of the respective one vane 130, 130’ or 140, 140’ and extend between the vane pivot point VPP and the respective trailing edge 134, 144. In still further related embodiments, first tapered surfaces 250A, 252A may be formed on the adjacent side 250 and opposing adjacent side 252 of the vane 130, 130’, 140, 140’ extending between the vane pivot point VPP and the leading edge 132, 142, while second tapered surfaces may be formed on the adjacent side 250 and opposing adjacent side 252 of the vane 130, 130’, 140, 140’ extending between the vane pivot point VPP and the trailing edge 134, 144.

[0091] In certain embodiments, such as shown in FIG. 17, a vane surface 250A defined along the opposing adjacent side 252 of one vane 130, 130’, 140, 140’ of the plurality of vanes 130, 140 and extending between the vane pivot point VPP and the leading edge 132, 142 is chamfered so as to form a recessed slot 255 with the opposing adjacent side 252 further defining a slot surface 260 A. In these embodiments, the clearance distance CD2 between the slot surface 260A of the opposing adjacent side 252 of the associated vane 130, 130’ or 140, 140’ and the vane ring surface 102 of the vane ring 100 (shown in FIG. 17 as vane ring 100B) isincreased as compared to the vane clearance distance of another one vane of the plurality of vanes 130, 140 that does not include the recessed slot 520 on the adjacent side 250.

[0092] Similar to the embodiment of FIG. 16, various alternative configurations for the location of the recessed slot 255 along the vane 130, 130’, 140, 140’ are contemplated. For example, while the embodiment of FIG. 17 illustrates the recessed slot 255 formed in the opposing adjacent side 252 of the vane 130’, 140’ associated with the annular disk 101 A of the vane ring 100A, in other embodiments a recessed slot 257 (shown in phantom in FIG. 16) may also be formed, or alternatively be formed, on the adjacent side 250 of the one vane 130, 130’ or 140, 140’ extending between the vane pivot point VPP and the leading edge 132 or 142 associated with the annular disk 101B of the vane ring 100B.

[0093] Even still further, in additional alternative embodiments, the recessed slot may be formed on the adjacent side 250, and / or the opposing adjacent side 252, of the respective one vane 130, 130’ or 140, 140’ and extending between the vane pivot point VPP and the respective trailing edge 134, 144. In still further related embodiments, the recessed slots 257, 255 may be formed on the adjacent side 250 and opposing adjacent side 252 of the vane 130, 130’, 140, 140’ extending between the vane pivot point VPP and the leading edge 132, 142, while additional recessed slots may be formed on the adjacent side 250 and opposing adjacent side 252 of the vane 130, 130’, 140, 140’ extending between the vane pivot point VPP and the trailing edge 134, 144.

[0094] The depth D5 of the recessed slot 255, measured between planes defining the original vane surface 250A and the slot surface 260A (and the corresponding depth of the recessed slot 257 or any recessed slot), may vary between greater than 0% and less than 100% of the thickness of the vane 130, 130’, 140, 140’ measured between the adjacent side 250 and the opposing adjacent side 252. In certain embodiments, the depth D5 varies from between 0.1% and 25%. Notably increasing the depth D5 allows more exhaust gas to flow between theslot surface 260 A and the adjacent vane ring surface 102 A of the annular disk 101B of vane ring 100B is in the closed position, or even in certain intermediate positions, which in turn alters the vane moment associated with the vane 130’, 140’ in the closed or intermediate positions during operation of the entryway system 30.

[0095] In still further embodiments, and in addition to including the bypass depression 500A, 500B, 500C as in FIGS. 10-15 or inclusion of the tapered vane surface 250A, 252A in the various configurations of FIG. 16 or inclusion of the recessed slot 255, 257 in the various configurations of FIG. 17, one or more of the vanes 130, 140 may be shortened between the vane pivot point VPP and the leading edge 132, 142 or trailing edge 134, 144. A shortened vane 130, 130’, 140, 140’ (not including either the tapering or recessed slot) extending between the vane pivot point VPP and the leading edge 132, 142 is illustrated in FIG. 18, with the shortened leading edge 132, 142 represented as 132’, 142’ and the corresponding length of the othervanes 130, 140 illustrated with the lengthened leading edge 132, 142 (shown in phantom).

[0096] The shortening of the respective vane 130, 130’, 140, 140’, allows more exhaust gas to flow between the shortened vane 130’, 140’ and the respective adjacent vane 130 or 140 when the respective vane 130’, 140’ is in the closed position, or even in certain intermediate positions, which in turn alters the vane moment associated with the vane 130’, 140’ in the closed or intermediate positions during operation of the entryway system 30.

[0097] Referring next to FIG. 19, in addition to manipulating the vane moment of the respective vane 130, 130’, 140, 140’ by providing a bypass depression 500 as illustrated in FIGS. 10-15 or by tapering the vane surfaces 250 or 252 as illustrated in FIG. 16 or through the inclusion of a recessed slot as illustrated in FIG. 17 or through the use of a shorted vane as in FIG. 18, the subject disclosure also contemplates altering the shape of the open drive surface 159A or closed drive surface 159B to more closely conform to the shape of the inner surface 202 of the opening 201 in the adjustment ring 199. In particular, the shape of the open drivesurface 159A or closed drive surface 159B is rounded to conform to the corresponding rounded shape of the inner surface 202 more closely. In this way, when the open drive surface 159A contacts a first portion the inner surface 202 of the opening 201 when the vanes 130, 130’, 140, 140’ are moved to the open position, a larger portion of the surface area defined by the open drive surface 159A is brought into contact with the corresponding larger portion of surface area of the inner surface 202, thus distributing the force between the vane lever 153 and the adjustment ring 199. Similarly, when the closed drive surface 159B contacts another portion the inner surface 202 of the opening 201 when the vanes 130, 130’, 140, 140’ are moved to the closed position, a larger portion of the surface area defined by the closed drive surface 159B is brought into contact with the corresponding larger portion of the surface area of the inner surface 202, thus distributing the force between the vane lever 153 and the adjustment ring 199. Increasing the distribution of force proportionally limits the wear of the respective open and closed drive surface 159A, 159B of the vane lever 153. When used in combination with the manipulation of the vane moments of the vanes 130, 140 as described in FIGS. 10-18 above, and in particular of the vanes 130’, 140’ not including a spacer 400 positioned adjacent to the leading edge 132, 142 or trailing edge 134, 144, the wear on the open and closed drive surface 159A, 159B of the vane lever 153 associated with the vanes 130’, 140’ is equalized to correspond to the wear on the open and closed drive surface 159A, 159B of the vane levers 153 associated with the other vanes 130, 140, including a spacer 400 positioned adjacent to the leading edge 132, 142 or trailing edge 134, 144. This in turn may increase the life of the vane pack 80, and the life of the turbocharger 32 and entryway system 30.

[0098] Referring back to FIG. 1, in certain embodiments, the system 30 also includes a controller 146 that is coupled to turbocharger 32 and / or to the internal combustion engine 34 that controls the various other components of the turbocharger 32 and / or internal combustion engine 34. The controller 146 may include one or more processors, or microprocessors, forprocessing instructions stored in memory 150 to control various functions on the turbocharger32 related to the introduction of the exhaust gas within the turbine housing interior 40 through the first and second volutes 54, 56. Such instructions may be any of the functions, algorithms or techniques described herein performed by the controller 146. Additionally, or alternatively, the controller 146 may include one or more microcontrollers, field programmable gate arrays, systems on a chip, discrete circuitry, and / or other suitable hardware, software, or firmware that is capable of carrying out the functions described herein. In some embodiments, the controller 146 is an engine control unit (ECU) that controls the various other components of the turbocharger 32 and / or internal combustion engine 34. In embodiments where the controller 146 is the engine control unit, the controller 146 is separate from the turbocharger 32. In other words, the controller 146 is a separate component that is not included on or in the turbocharger 32. In other embodiments, the controller 146 is discrete from the ECU. For example, the controller 146 may be included on or in the turbocharger 32. In other words, the controller 146 is a component included on or in the turbocharger 32. With reference to FIG. 1 , the system 30 may include the turbocharger 32, the internal combustion engine 34, and the controller 146. Typically, the system 30 also includes at least one sensor 148.

[0099] Referring next to FIGS. 20 and 21, two graphs are provided which compare the magnitude of the vane moments for each vane 130, 130’, 140, 140’ on a thirteen vane single volute entryway system 30 with various manipulations in accordance with the subject disclosure.

[0100] First, in FIG. 20, a thirteen vane single volute entryway system is compared having four spacers and six spacers (corresponding to the embodiment illustrated in FIGS. 2-4 having six spacers 400). As shown, the addition of the two additional spacers functioned to decrease the magnitude of the vane moments (shown as the diamond plot) of each of vanes 1 and 3-13 (which correspond to the vanes 130, 140 having a spacer 400 positioned adjacent to either aleading edge 132, 142 or trailing edge 134, 144) to essentially the same magnitudes, while the single vane 2 (which corresponds to vane 130 or 140’ not having a spacer 400 positioned adjacent to either a leading edge 132, 142 or trailing edge 134, 144) remained at a higher magnitudes. By contrast, the thirteen vane single volute entryway system having four spacers had higher magnitudes (as shown by the square plot) associated with vanes 2, 3, 6, 9 and 12). FIG. 20 thus confirms the desirability to include extra spacers in a thirteen vane single volute entryway system.

[0101] Referring next to FIG. 21, vane moment magnitude graphs were compared for thirteen vane single volute entryway systems having the six spacers in which no further manipulation was performed (represented by the square plot) and corresponding to FIGS. 2-4, where the recessed slot 255, 257 was included on vane 2 (i.e., vane 130’ or 140’) corresponding to FIG. 17 (represented by the diamond plot), where the spherical bypass depression 500A was provided on annular disk 101B of vane ring 100B at a position corresponding to the position beneath the vane 130’, 140’ between the vane pivot point VPP and the trailing edge 134, 144 as shown in FIG. 16 (represented by the triangle plot), and where the cylindrical bypass depression 500C was provided on annular disk 101B of vane ring 100B at a position corresponding to the position beneath the vane 130’, 140’ between the vane pivot point VPP and the leading edge 132, 142 as shown in FIG. 18 (represented by the circle plot). In each of these plots, the magnitude of the vane moment was reduced at vane 2 by the introduction of the recessed slot 255, 257, or by the spherical or cylindrical bypass depressions 500A, 500C, as compared to thirteen vane single volute entryway systems having the six spacers in which no further manipulation was performed.

[0102] Embodiments for the disclosure can also be described with reference to the following numbered clauses, with specific features laid out in the dependent clauses:I. An entry way system comprising:a turbocharger for receiving exhaust gas from an internal combustion engine and for delivering compressed air to the internal combustion engine, said turbocharger comprising: a turbine housing comprising a turbine housing interior adapted to receive a turbine wheel having a plurality of equally spaced turbine blades, said turbine housing defining a turbine housing outlet in fluid communication with said turbine housing interior, and one or more volutes adapted for fluid communication with the internal combustion engine and said turbine housing interior for delivering exhaust gas from the internal combustion engine to said turbine housing interior; and a vane pack coupled to said turbocharger, said vane pack comprising: a vane ring disposed in said turbine housing interior and around said turbine wheel, said vane ring comprising an annular disk including a vane ring surface disposed between an inner circumferential ring and an outer circumferential ring with said inner circumferential ring defining an orifice for receiving said turbine wheel, said vane ring surface including a plurality of vanes rotatably disposed thereon in a spaced apart manner along said vane ring surface with each of said vanes rotatable between an open position and a closed position including one or more intermediate positions, and a plurality of spacers disposed in a spaced apart manner on said vane ring surface and positioned circumferentially outward relative to each of said plurality of vanes with each respective one of said plurality of spacers positioned adjacent to a leading edge or a trailing edge of a corresponding respective one of said plurality of vanes and with each one of said plurality of spacers separated from an adjacent one of said plurality of spacers by at least at least one of said plurality of vanes, wherein a vane clearance distance defined between any portion of an adjacent side of a first one of said plurality of vanes and said vane ring surface of said vane ring is greater than avane clearance distance defined between any portion of an adjacent side of a second one of said plurality of vanes and said vane ring surface of said vane ring so as to manipulate a vane moment associated with said first one of said plurality of vanes that occurs during the operation of the entry way system.II. The entryway system of clause I wherein a vane clearance distance defined between any portion of an adjacent side of a third one of said plurality of vanes and said first vane ring surface of said first vane ring is greater than said vane clearance distance between any portion of an adjacent side of said second one of said plurality of vanes and said first vane ring surface of said first vane ring.III. The entryway system of clause I or clause II, wherein said first one of said plurality of vanes corresponds to a single vane of said plurality of vanes that does not include a respective one of said plurality of spacers disposed adjacent to said leading edge or disposed adjacent to said trailing edge.IV. The entryway system of clause III, wherein said second one of said plurality of vanes corresponds to another single vane of said plurality of vanes that includes a respective one of said plurality of spacers disposed adjacent to said leading edge or disposed adjacent to said trailing edge.V. The entryway system of any one of clause I-III, wherein said second one of said plurality of vanes corresponds to a single vane of said plurality of vanes that does not include a respective one of said plurality of spacers disposed adjacent to said leading edge or disposed adjacent to said trailing edge.VI. The entryway system of any one of clauses I-V, wherein a vane clearance distance between any portion of an adjacent side of one or more additional vanes of said plurality of vanes and said vane ring surface of said vane ring is greater than said vane clearance distancebetween any portion of an adjacent side of said second one of said plurality of vanes and said vane ring surface of said vane ring.VII. The entryway system of any one of clauses I- VI, wherein a number of said plurality of spacers is equal to or less than one-half of the number of said plurality of vanes.VIII. The entry way system of any one of clauses I- VII, wherein said vane ring includes a bypass depression extending within said vane ring surface of said vane ring.IX. The entryway system of clause VIII, wherein said bypass depression is a spherical bypass depression.X. The entry way system of clause VIII, wherein said bypass depression is an ellipsoid bypass depression.XI. The entry way system of clause VIII, wherein said bypass depression is a cylindrical bypass depression.XII. The entryway system of any one of clauses VIII-XI, wherein said bypass depression is disposed adjacent to and beneath said adjacent side of said first one of said plurality of vanes when said first one of said plurality of vanes is in said closed position.XIII. The entryway system of clause XII, wherein a width of said bypass depression extending within said vane ring surface of said vane ring, measured in a direction parallel to a length of said first one of said plurality of vanes when said first one of said vanes is in said closed position, is less than or equal to said length of said first one of said plurality of vanes as measured from a vane pivot point to a leading edge of said first one of said plurality of vanes, and wherein said bypass depression is disposed entirely beneath said length of said first one of said plurality of vanes between said vane pivot point and said leading edge when said first one of said plurality of vanes is in said closed position.XIV. The entryway system of clause XII, wherein a width of said bypass depression extending within said vane ring surface of said vane ring, measured in a direction parallel to a length of said first one of said plurality of vanes when said first one of said vanes is in said closed position, is less than or equal to said length of said first one of said plurality of vanes as measured from a vane pivot point to a trailing edge of said first one of said plurality of vanes, and wherein said bypass depression is disposed entirely beneath said length of said first one of said plurality of vanes between said vane pivot point and said trailing edge when said first one of said plurality of vanes is in said closed position.XV. The entryway system of any one of clauses I-XIV, wherein a vane surface defined along said adjacent side of said first one of said plurality of vanes and extending between a vane pivot point and a leading edge is tapered such that said vane clearance distance between said adjacent side of said first one of said plurality of vanes and said vane ring surface of said vane ring increases in a direction from said vane pivot point to said leading edge of said first one of said plurality of vanes.XVI. The entryway system of any one of clauses I-XIV, wherein a vane surface defined along said adjacent side of said first one of said plurality of vanes and extending between a vane pivot point and a trailing edge is tapered such that said vane clearance distance between said adjacent side of said first one of said plurality of vanes and said vane ring surface of said vane ring increases in a direction from said vane pivot point to said trailing edge of said first one of said plurality of vanes.XVII. The entryway system of any one of clauses I-XIV, wherein a vane surface defined along said adjacent side of said first one of said plurality of vanes and extending between a vane pivot point and a leading edge is chamfered to create a recessed slot in said first one of said plurality of vanes between said vane pivot point and said leading edge.XVIII. The entryway system of any one of clauses I-XIV, wherein a vane surface defined along said adjacent side of said first one of said plurality of vanes and extending between a vane pivot point and a trailing edge is chamfered to create a recessed slot in said first one of said plurality of vanes between said vane pivot point and said trailing edge.XIX. The entryway system of any one of clauses I-XVII, wherein a length of said first one of said plurality of vanes, as measured between a vane pivot point and a leading edge of said first one of said plurality of vanes, is shorter than a length of said second one of said plurality of vanes, as measured between a vane pivot point and a leading edge of said second one of said plurality of vanes.XX. The entryway system of any one of clauses I- XVIII, wherein said vane pack further comprises an additional vane ring with said plurality of vanes and said plurality of spacers disposed between said vane ring and said additional vane ring, wherein a vane clearance distance between any portion of an opposing adjacent side of said first one of said plurality of vanes and said vane ring surface of said additional vane ring is greater than a vane clearance distance between any portion of an adjacent side of said second one of said plurality of vanes and said vane ring surface of said additional vane ring.XXL The entry way system of clause XX, wherein a vane ring surface of said additional vane ring includes at least one bypass depression extending within said vane surface of said additional vane ring.XXII. The entryway system of clause XX or clause XXI, wherein a vane surface defined along said opposing adjacent side of said first one of said plurality of vanes and extending between a vane pivot point and a leading edge is tapered such that said vane clearance distance between said opposing adjacent side of said first one of said plurality of vanes and said vane ring surface of said additional vane ring increases in a direction from said vane pivot point to said leading edge of said first one of said plurality of vanes.XXIII. The entryway system of clause XX or clause XXI, wherein a vane surface defined along said opposing adjacent side of said first one of said plurality of vanes and extending between a vane pivot point and a trailing edge is tapered such that said vane clearance distance between said opposing adjacent side of said first one of said plurality of vanes and said vane ring surface of said additional vane ring increases in a direction from said vane pivot point to said trailing edge of said first one of said plurality of vanes.XXIV. The entryway system of clause XX or clause XXI, wherein a vane surface defined along said opposing adjacent side of said first one of said plurality of vanes and extending between a vane pivot point and a leading edge is chamfered to create a recessed slot in said first one of said plurality of vanes between said vane pivot point and said leading edge.XXV. The entryway system of clause XX or clause XXI, wherein a vane surface defined along said opposing adjacent side of said first one of said plurality of vanes and extending between a vane pivot point and a trailing edge is chamfered to create a recessed slot in said first one of said plurality of vanes between said vane pivot point and said trailing edge.XXVI. The entryway system of any one of clauses XX-XXV, wherein a length of said first one of said plurality of vanes, as measured between a vane pivot point and a leading edge of said first one of said plurality of vanes, is shorter than a length of said second one of said plurality of vanes, as measured between a vane pivot point and a leading edge of said second one of said plurality of vanes.XXV II. The entryway system of any one of clauses XX-XXV1, wherein said vane pack further comprises: an adjustment ring positioned adjacent to said one of said additional vane ring such that said additional vane ring is positioned between said first vane ring and said adjustment ring, said adjustment ring including a plurality of spaced apart retention slots; anda plurality of vane levers, with a respective one of said plurality of vane levers including a body portion and a rampart extending transverse from said body portion, said body portion coupled to a corresponding one of said plurality of vanes and said rampart coupled within a respective one of said spaced apart retention slots to limit a radial motion of said adjustment ring, wherein each one of said plurality of vane levers moves in rolling and sliding contact with said adjustment ring as said plurality of vanes move between said open position and said closed position.XXVII. A vane pack for use in conjunction with a turbocharger in an entryway system, said vane pack comprising: a first vane ring disposed in said turbine housing interior and around said turbine wheel, said first vane ring comprising an annular disk including a first vane ring surface disposed between an inner circumferential ring and an outer circumferential ring with said inner circumferential ring defining an orifice for receiving said turbine wheel; a second vane ring disposed in said turbine housing interior and around said turbine wheel, said second vane ring comprising an annular disk including a second vane ring surface disposed between an inner circumferential ring and an outer circumferential ring with said inner circumferential ring defining an orifice for receiving said turbine wheel, said second vane ring surface spaced from said first vane to define an interior therebetween; a plurality of vanes rotatably disposed in said interior in a spaced apart manner along said first vane ring surface and said second vane ring surface with each of said vanes rotatable between an open position and a closed position including one or more intermediate positions; and a plurality of spacers disposed in a spaced apart manner along said first vane ring surface and said second vane ring surface and positioned circumferentially outward relative to each of said plurality of vanes with each respective one of said plurality of spacers positionedadjacent to a leading edge or a trailing edge of a corresponding respective one of said plurality of vanes and with each one of said plurality of spacers separated from an adjacent one of said plurality of spacers by at least at least one of said plurality of vanes, wherein a vane clearance distance between any portion of an adjacent side of a first one of said plurality of vanes and said first vane ring surface of said first vane ring is greater than a vane clearance distance between any portion of an adjacent side of a second one of said plurality of vanes and said first vane ring surface of said first vane ring so as to manipulate a vane moment associated with said first one of said plurality of vanes having said vane clearance distance that occurs during the operation of the entryway system.XXVIII. The vane pack of clause XXVII, wherein a vane clearance distance between any portion of an adjacent side of a third one of said plurality of vanes and said first vane ring surface of said first vane ring is greater than said second clearance distance between any portion of an adjacent side of said second one of said plurality of vanes and said first vane ring surface of said first vane ring.XXIX. The vane pack of clause XXVII or clause XXVIII, wherein a vane clearance distance between any portion of an opposing adjacent side of a first one of said plurality of vanes and said second vane ring surface of said second vane ring is greater than a vane clearance distance between any portion of an opposing adjacent side of a second one of said plurality of vanes and said second vane ring surface of said second vane ring.XXX. The vane pack of any one of clauses XXV1I-XXIX further comprising: an adjustment ring positioned adjacent to said second vane ring such that said second vane ring is positioned between said first vane ring and said adjustment ring, said adjustment ring including a plurality of spaced apart retention slots; and a plurality of vane levers, with a respective one of said plurality of vane levers including a body portion and a rampart extending transverse from said body portion, said body portioncoupled to a corresponding one of said plurality of vanes and said rampart coupled within a respective one of said spaced apart retention slots to limit a radial motion of said adjustment ring, wherein each one of said plurality of vane levers moves in rolling and sliding contact with said adjustment ring as said plurality of vanes move between said open position and said closed position.XXXI. The vane pack of any one of clauses XXVII-XXX, wherein said first one of said plurality of vanes corresponds to a single vane of said plurality of vanes that does not include a respective one of said plurality of spacers disposed adjacent to said leading edge or disposed adjacent to said trailing edge.XXXII. The vane pack of any one of clauses XXVII- XXXI, wherein said second one of said plurality of vanes corresponds to another single vane of said plurality of vanes that includes a respective one of said plurality of spacers disposed adjacent to said leading edge or disposed adjacent to said trailing edge.XXXIII. The vane pack of any one of clauses XXVII-XXXI, wherein said second one of said plurality of vanes corresponds to another single vane of said plurality of vanes that does not include a respective one of said plurality of spacers disposed adjacent to said leading edge or disposed adjacent to said trailing edge.XXXIV. The vane pack of any one of clauses XXVII-XXXIII, wherein a number of said plurality of spacers is equal to or less than one-half of the number of said plurality of vanes.XXXV. The vane pack of any one of clauses XXVII-XXXIV, wherein said first vane ring includes a bypass depression extending within said first vane ring surface of said first vane ring.XXXVI. The vane pack of clause XXXV, wherein said bypass depression is a spherical bypass depression.XXXVII. The vane pack of clause XXXV, wherein said bypass depression is an ellipsoid bypass depression.XXXVIII. The vane pack of clause XXXV, wherein said bypass depression is a cylindrical bypass depression.XXXIX. The vane pack of any one of clauses XXXV-XXXVII, wherein said bypass depression within said vane ring surface of said first vane ring is disposed adjacent to said adjacent side of said first one of said plurality of vanes when said first one of said plurality of vanes is in said closed position.XL. The vane pack of any one of clauses XXXV-XXXIX, wherein a width of said bypass depression extending within said vane ring surface of said first vane ring, measured in a direction parallel to a length of said first one of said plurality of vanes when said first one of said vanes is in said closed position, is less than or equal to said length of said first one of said plurality of vanes as measured from a vane pivot point to a leading edge of said first one of said plurality of vanes, and wherein said bypass depression is disposed entirely beneath said length of said first one of said plurality of vanes between said vane pivot point and said leading edge when said first one of said plurality of vanes is in said closed position.XLI. The vane pack of any one of clauses XXXV-XXXIX, wherein a width of said bypass depression extending within said vane ring surface of said first vane ring, measured in a direction parallel to a length of said first one of said plurality of vanes when said first one ofsaid vanes is in said closed position, is less than or equal to said length of said first one of said plurality of vanes as measured from a vane pivot point to a trailing edge of said first one of said plurality of vanes, and wherein said bypass depression is disposed entirely beneath said length of said first one of said plurality of vanes between said vane pivot point and said trailing edge when said first one of said plurality of vanes is in said closed position.XLII. The vane pack of any one of clauses XXXV-XLI, wherein a vane surface defined along said adjacent side of said first one of said plurality of vanes and extending between a vane pivot point and a leading edge is tapered such that said vane clearance distance between said adjacent side of said first one of said plurality of vanes and said vane ring surface of said first vane ring increases in a direction from said vane pivot point to said leading edge of said first one of said plurality of vanes.XLIII. The vane pack of any one of clauses XXXV- XLII, wherein a vane surface defined along said adjacent side of said first one of said plurality of vanes and extending between a vane pivot point and a trailing edge is tapered such that said vane clearance distance between said adjacent side of said first one of said plurality of vanes and said first vane ring surface of said first vane ring increases in a direction from said vane pivot point to said trailing edge of said first one of said plurality of vanes.XLIV. The vane pack of any one of clauses XXXV-XLI, wherein a vane surface defined along said adjacent side of said first one of said plurality of vanes and extending between a vane pivot point and a leading edge is chamfered to create a recessed slot in said first one of said plurality of vanes between said vane pivot point and said leading edge.XLV. The vane pack of any one of clauses XXXV-XLII, wherein a vane surface defined along said adjacent side of said first one of said plurality of vanes and extendingbetween a vane pivot point and a trailing edge is chamfered to create a recessed slot in said first one of said plurality of vanes between said vane pivot point and said trailing edge.XLVI. The vane pack of any one of clauses XXXV-XLV, wherein a length of said first one of said plurality of vanes, as measured between a vane pivot point and a leading edge of said first one of said plurality of vanes, is shorter than a length of said second one of said plurality of vanes, as measured between a vane pivot point and a leading edge of said second one of said plurality of vanes.XLVII. The vane pack of any one of clauses XXXV-XLVI, wherein said second vane ring includes at least one bypass depression extending within said vane ring surface of said second vane ring.XLVIII. The vane pack of clause XLVII, wherein a vane surface defined along an opposing adjacent side of said first one of said plurality of vanes and extending between a vane pivot point and a leading edge is tapered such that said clearance distance between said opposing adjacent side of said first one of said plurality of vanes and said vane ring surface of said second vane ring increases in a direction from said vane pivot point to said leading edge of said first one of said plurality of vanes.XLIX. The vane pack of clause XLVII or clause XLVIII, wherein a surface defined along an opposing adjacent side of said first one of said plurality of vanes and extending between a vane pivot point and a trailing edge is tapered such that said clearance distance between said opposing adjacent side of said first one of said plurality of vanes and said vane ring surface of said second vane ring increases in a direction from said vane pivot point to said trailing edge of said first one of said plurality of vanes.L. The vane pack of any one of clauses XLVILXLIX, wherein a surface defined along an opposing adjacent side of said first one of said plurality of vanes and extending between avane pivot point and a leading edge is chamfered to create a recessed slot in said first one of said plurality of vanes between said vane pivot point and said leading edge.LI. The vane pack of any one of clauses XLVILXLIX, wherein a surface defined along an opposing adjacent side of said first one of said plurality of vanes and extending between a vane pivot point and a trailing edge is chamfered to create a recessed slot in said first one of said plurality of vanes between said vane pivot point and said trailing edge.LII. The vane pack of any one of clauses XL VILLI, wherein a length of said first one of said plurality of vanes, as measured between a vane pivot point and a leading edge of said first one of said plurality of vanes, is shorter than a length of said second one of said plurality of vanes, as measured between a vane pivot point and a leading edge of said second one of said plurality of vanes.Lili. The vane pack of any one of clauses XLVII-LII, wherein a length of said first one of said plurality of vanes, as measured between a vane pivot point and a trailing edge of said first one of said plurality of vanes, is shorter than a length of said second one of said plurality of vanes, as measured between a vane pivot point and a trailing edge of said second one of said plurality of vanes.LIV. A method for reducing wear on the body portion of a vane lever of a vane pack in an entryway system during operation of the entryway system, the entryway system comprising: a turbocharger for receiving exhaust gas from an internal combustion engine and for delivering compressed air to the internal combustion engine, the turbocharger comprising: a turbine housing comprising a turbine housing interior adapted to receive a turbine wheel having a plurality of equally spaced turbine blades, theturbine housing defining a turbine housing outlet in fluid communication with turbine housing interior, and one or more volutes adapted for fluid communication with the internal combustion engine and the turbine housing interior for delivering exhaust gas from the internal combustion engine to the turbine housing interior; a vane pack coupled to the turbocharger, the vane pack comprising: a vane ring disposed in the turbine housing interior and around the turbine wheel, the vane ring comprising an annular disk including a vane ring surface disposed between an inner circumferential ring and an outer circumferential ring with the inner circumferential ring defining an orifice for receiving the turbine wheel, the vane ring surface including the plurality of vanes rotatably disposed thereon in a spaced apart manner along the vane ring surface with each of the vanes rotatable between an open position and a closed position including one or more intermediate positions; and a plurality of spacers disposed in a spaced apart manner on the vane ring surface and positioned circumferentially outward relative to each of the plurality of vanes with each respective one of the plurality of spacers positioned adjacent to a leading edge or a trailing edge of a corresponding respective one of the plurality of vanes and with each one of the plurality of spacers separated from an adjacent one of the plurality of spacers by at least at least one of the plurality of vanes, an adjustment ring positioned adjacent to the second vane ring such that the second vane ring is positioned between the first vane ring and the adjustment ring, the adjustment ring including a plurality of spaced apart retention slots, anda plurality of vane levers, with a respective one of the plurality of vane levers including the body portion and a rampart extending transverse from the body portion, the body portion coupled to a corresponding one of the plurality of vanes and the rampart coupled within a respective one of the spaced apart retention slots to limit a radial motion of the adjustment ring, wherein each one of the plurality of vane levers moves in rolling and sliding contact with the adjustment ring as the plurality of vanes move between the open position and the closed position; said method comprising: manipulating a vane moment associated with a first one of the plurality of vanes by increasing a vane clearance distance between any portion of an adjacent side of the first one of the plurality of vanes and the vane ring surface of the vane ring such that the vane clearance distance is greater than a vane clearance distance between any portion of an adjacent side of a second one of the plurality of vanes and the vane ring surface of the vane ring.LV. The method of clause LIV, wherein said step of manipulating vane moment associated with a first one of the plurality of vanes comprises introducing a bypass depression extending within the vane surface of the vane ring at a location adjacent to and beneath the adjacent side of the first one of said plurality of vanes when the first one of the plurality of vanes is in the closed position.LVI. The method of clause LIV or clause LV, wherein the bypass depression is a spherical bypass depression.LVII. The method of clause LIV or clause LV, wherein the bypass depression is an ellipsoid bypass depression.LVIII. The method of clause LIV or clause LV, wherein the bypass depression is a cylindrical bypass depression.LVIX. The method of any one of clauses LV-LVIII, wherein a width of the bypass depression, measured in a direction parallel to a length of the first one of the plurality of vanes when the first one of said vanes is in the closed position, is less than or equal to the length of the first one of the plurality of vanes as measured from a vane pivot point to a leading edge of the first one of the plurality of vanes, and wherein the bypass depression is disposed entirely beneath the length of the first one of the plurality of vanes between the vane pivot point and the leading edge when the first one of the plurality of vanes is in the closed position.LVX. The method of any one of clauses LV-LVIII, wherein a width of the bypass depression, measured in a direction parallel to a length of the first one of the plurality of vanes when the first one of said vanes is in the closed position, is less than or equal to the length of the first one of the plurality of vanes as measured from a vane pivot point to a trailing edge of the first one of the plurality of vanes, and wherein the bypass depression is disposed entirely beneath the length of the first one of the plurality of vanes between the vane pivot point and the trailing edge when the first one of the plurality of vanes is in the closed position.LVXI. The method of any one of clauses LIV-LVX, wherein said step of manipulating vane moment associated with a first one of the plurality of vanes comprises tapering a surface defined along the adjacent side of the first one of the plurality of vanes extending between a vane pivot point and a leading edge such that the vane clearance distance between the adjacent side of the first one of the plurality of vanes and the vane ring surface of the vane ring increases in a direction from the vane pivot point to the leading edge of the first one of the plurality of vanes.LVXII. The method of any one of clauses LIV-LVXI, wherein said step of manipulating vane moment associated with a first one of the plurality of vanes comprises tapering a surface defined along the adjacent side of the first one of the plurality of vanes extending between a vane pivot point and a trailing edge such that the vane clearance distance between the adjacent side of the first one of the plurality of vanes and the vane ring surface of the vane ring increases in a direction from the vane pivot point to the trailing edge of the first one of the plurality of vanes.LVXIII. The method of any one of clauses LIV-LVXI, wherein said step of manipulating vane moment associated with a first one of the plurality of vanes comprises chamfering a surface defined along the adjacent side of the first one of the plurality of vanes extending between a vane pivot point and a leading edge to form a recessed slot.LVXIX. The method of any one of clauses LIV-LVXI, wherein said step of manipulating vane moment associated with a first one of the plurality of vanes comprises chamfering a surface defined along the adjacent side of the first one of the plurality of vanes extending between a vane pivot point and a trailing edge to form a recessed slot.LVXX. The method of any one of clauses LIV-LVXIX, wherein said step of manipulating vane moment associated with a first one of the plurality of vanes comprises reducing a length of the first one of the plurality of vanes, as measured between a vane pivot point and a leading edge of the first one of the plurality of vanes.LVXX1. The method of any one of clauses LIV-LVXIX, wherein said step of manipulating vane moment associated with a first one of the plurality of vanes comprises reducing a length of the first one of the plurality of vanes, as measured between a vane pivot point and a trailing edge of the first one of the plurality of vanes.

[0103] The disclosure has been described in an illustrative manner, and it is to be understood that the terminology which has been used is intended to be in the nature of wordsof description rather than of limitation. Many modifications and variations of the subject disclosure are possible in light of the above teachings, and the disclosure may be practiced otherwise than as specifically described.

Claims

CLAIMSWhat is claimed is:

1. An entryway system comprising: a turbocharger for receiving exhaust gas from an internal combustion engine and for delivering compressed air to the internal combustion engine, said turbocharger comprising: a turbine housing comprising a turbine housing interior adapted to receive a turbine wheel having a plurality of equally spaced turbine blades, said turbine housing defining a turbine housing outlet in fluid communication with said turbine housing interior, and one or more volutes adapted for fluid communication with the internal combustion engine and said turbine housing interior for delivering exhaust gas from the internal combustion engine to said turbine housing interior; and a vane pack coupled to said turbocharger, said vane pack comprising: a vane ring disposed in said turbine housing interior and around said turbine wheel, said vane ring comprising an annular disk including a vane ring surface disposed between an inner circumferential ring and an outer circumferential ring with said inner circumferential ring defining an orifice for receiving said turbine wheel, said vane ring surface including a plurality of vanes rotatably disposed thereon in a spaced apart manner along said vane ring surface with each of said vanes rotatable between an open position and a closed position including one or more intermediate positions, and a plurality of spacers disposed in a spaced apart manner on said vane ring surface and positioned circumferentially outward relative to each of said plurality of vanes with each respective one of said plurality of spacers positioned adjacent to a leading edge or a trailing edge of a corresponding respective one of said plurality ofvanes and with each one of said plurality of spacers separated from an adjacent one of said plurality of spacers by at least at least one of said plurality of vanes, wherein a vane clearance distance defined between any portion of an adjacent side of a first one of said plurality of vanes and said vane ring surface of said vane ring is greater than a vane clearance distance defined between any portion of an adjacent side of a second one of said plurality of vanes and said vane ring surface of said vane ring so as to manipulate a vane moment associated with said first one of said plurality of vanes that occurs during the operation of the entryway system.

2. The entryway system of claim 1 wherein a vane clearance distance defined between any portion of an adjacent side of a third one of said plurality of vanes and said first vane ring surface of said first vane ring is greater than said vane clearance distance between any portion of an adjacent side of said second one of said plurality of vanes and said first vane ring surface of said first vane ring.

3. The entry way system of claim 1 , wherein said first one of said plurality of vanes corresponds to a single vane of said plurality of vanes that does not include a respective one of said plurality of spacers disposed adjacent to said leading edge or disposed adjacent to said trailing edge.

4. The entryway system of claim 3, wherein said second one of said plurality of vanes corresponds to another single vane of said plurality of vanes that includes a respective one of said plurality of spacers disposed adjacent to said leading edge or disposed adjacent to said trailing edge.

5. The entry way system of claim 1, wherein said second one of said plurality of vanes corresponds to a single vane of said plurality of vanes that does not include a respective one of said plurality of spacers disposed adjacent to said leading edge or disposed adjacent to said trailing edge.

6. The entryway system of claim 3, wherein a vane clearance distance between any portion of an adjacent side of one or more additional vanes of said plurality of vanes and said vane ring surface of said vane ring is greater than said vane clearance distance between any portion of an adjacent side of said second one of said plurality of vanes and said vane ring surface of said vane ring.

7. The entry way system of claim 1, wherein a number of said plurality of spacers is equal to or less than one-half of the number of said plurality of vanes.

8. The entryway system of claim 1, wherein said vane ring includes a bypass depression extending within said vane ring surface of said vane ring.

9. The entryway system of claim 8, wherein said bypass depression is a spherical bypass depression.

10. The entryway system of claim 8, wherein said bypass depression is an ellipsoid bypass depression.1 1 . The entryway system of claim 8, wherein said bypass depression is a cylindrical bypass depression.

12. The entryway system of claim 8, wherein said bypass depression is disposed adjacent to and beneath said adjacent side of said first one of said plurality of vanes when said first one of said plurality of vanes is in said closed position.

13. The entry way system of claim 12, wherein a width of said bypass depression extending within said vane ring surface of said vane ring, measured in a direction parallel to a length of said first one of said plurality of vanes when said first one of said vanes is in said closed position, is less than or equal to said length of said first one of said plurality of vanes as measured from a vane pivot point to a leading edge of said first one of said plurality of vanes, andwherein said bypass depression is disposed entirely beneath said length of said first one of said plurality of vanes between said vane pivot point and said leading edge when said first one of said plurality of vanes is in said closed position.

14. The entryway system of claim 12, wherein a width of said bypass depression extending within said vane ring surface of said vane ring, measured in a direction parallel to a length of said first one of said plurality of vanes when said first one of said vanes is in said closed position, is less than or equal to said length of said first one of said plurality of vanes as measured from a vane pivot point to a trailing edge of said first one of said plurality of vanes, and wherein said bypass depression is disposed entirely beneath said length of said first one of said plurality of vanes between said vane pivot point and said trailing edge when said first one of said plurality of vanes is in said closed position.

15. The entry way system of claim 1, wherein a vane surface defined along said adjacent side of said first one of said plurality of vanes and extending between a vane pivot point and a leading edge is tapered such that said vane clearance distance between said adjacent side of said first one of said plurality of vanes and said vane ring surface of said vane ring increases in a direction from said vane pivot point to said leading edge of said first one of said plurality of vanes.

16. The entry way system of claim 1, wherein a vane surface defined along said adjacent side of said first one of said plurality of vanes and extending between a vane pivot point and a trailing edge is tapered such that said vane clearance distance between said adjacent side of said first one of said plurality of vanes and said vane ring surface of said vane ring increases in a direction from said vane pivot point to said trailing edge of said first one of said plurality of vanes.

17. The entryway system of claim 8, wherein a vane surface defined along said adjacent side of said first one of said plurality of vanes and extending between a vane pivot point and a leading edge is tapered such that said vane clearance distance between any portion of said adjacent side of said first one of said plurality of vanes and said vane ring surface of said vane ring increases in a direction from said vane pivot point to said leading edge of said first one of said plurality of vanes.

18. The entry way system of claim 8, wherein a vane surface defined along said adjacent side of said first one of said plurality of vanes and extending between a vane pivot point and a trailing edge is tapered such that said vane clearance distance between any portion of said adjacent side of said first one of said plurality of vanes and said vane ring surface of said vane ring increases in a direction from said vane pivot point to said trailing edge of said first one of said plurality of vanes.

19. The entryway system of claim 8, wherein a vane surface defined along said adjacent side of said first one of said plurality of vanes and extending between a vane pivot point and a leading edge is chamfered to create a recessed slot in said first one of said plurality of vanes between said vane pivot point and said leading edge.

20. The entryway system of claim 8, wherein a vane surface defined along said adjacent side of said first one of said plurality of vanes and extending between a vane pivot point and a trailing edge is chamfered to create a recessed slot in said first one of said plurality of vanes between said vane pivot point and said trailing edge.

21. The entry way system of claim 8, wherein a length of said first one of said plurality of vanes, as measured between a vane pivot point and a leading edge of said first one of said plurality of vanes, is shorter than a length of said second one of said plurality of vanes, as measured between a vane pivot point and a leading edge of said second one of said plurality of vanes.

22. The entry way system of claim 1, wherein said vane pack further comprises an additional vane ring with said plurality of vanes and said plurality of spacers disposed between said vane ring and said additional vane ring, wherein a vane clearance distance between any portion of an opposing adjacent side of said first one of said plurality of vanes and said vane ring surface of said additional vane ring is greater than a vane clearance distance between any portion of an adjacent side of said second one of said plurality of vanes and said vane ring surface of said additional vane ring.

23. The entry way system of claim 22, wherein a vane ring surface of said additional vane ring includes at least one bypass depression extending within said vane surface of said additional vane ring.

24. The entryway system of claim 22, wherein a vane surface defined along said opposing adjacent side of said first one of said plurality of vanes and extending between a vane pivot point and a leading edge is tapered such that said vane clearance distance between said opposing adjacent side of said first one of said plurality of vanes and said vane ring surface of said additional vane ring increases in a direction from said vane pivot point to said leading edge of said first one of said plurality of vanes.

25. The entry way system of claim 22, wherein a vane surface defined along said opposing adjacent side of said first one of said plurality of vanes and extending between a vane pivot point and a trailing edge is tapered such that said vane clearance distance between said opposing adjacent side of said first one of said plurality of vanes and said vane ring surface of said additional vane ring increases in a direction from said vane pivot point to said trailing edge of said first one of said plurality of vanes.

26. The entryway system of claim 23, wherein a vane surface defined along said opposing adjacent side of said first one of said plurality of vanes and extending between a vane pivot point and a leading edge is tapered such that said vane clearance distance between saidopposing adjacent side of said first one of said plurality of vanes and said vane ring surface of said additional vane ring increases in a direction from said vane pivot point to said leading edge of said first one of said plurality of vanes.

27. The entry way system of claim 23, wherein a vane surface defined along said opposing adjacent side of said first one of said plurality of vanes and extending between a vane pivot point and a trailing edge is tapered such that said vane clearance distance between said opposing adjacent side of said first one of said plurality of vanes and said vane ring surface of said additional vane ring increases in a direction from said vane pivot point to said trailing edge of said first one of said plurality of vanes.

28. The entry way system of claim 22, wherein a vane surface defined along said opposing adjacent side of said first one of said plurality of vanes and extending between a vane pivot point and a leading edge is chamfered to create a recessed slot in said first one of said plurality of vanes between said vane pivot point and said leading edge.

29. The entryway system of claim 22, wherein a vane surface defined along said opposing adjacent side of said first one of said plurality of vanes and extending between a vane pivot point and a trailing edge is chamfered to create a recessed slot in said first one of said plurality of vanes between said vane pivot point and said trailing edge.

30. The entryway system of claim 23, wherein a vane surface defined along said opposing adjacent side of said first one of said plurality of vanes and extending between a vane pivot point and a leading edge is chamfered to create a recessed slot in said first one of said plurality of vanes between said vane pivot point and said leading edge.

31. The entryway system of claim 23, wherein a vane surface defined along said opposing adjacent side of said first one of said plurality of vanes and extending between a vane pivot point and a trailing edge is chamfered to create a recessed slot in said first one of said plurality of vanes between said vane pivot point and said trailing edge.

32. The entryway system of claim 23, wherein a length of said first one of said plurality of vanes, as measured between a vane pivot point and a leading edge of said first one of said plurality of vanes, is shorter than a length of said second one of said plurality of vanes, as measured between a vane pivot point and a leading edge of said second one of said plurality of vanes.

33. The entry way system of claim 22, wherein said vane pack further comprises: an adjustment ring positioned adjacent to said one of said additional vane ring such that said additional vane ring is positioned between said first vane ring and said adjustment ring, said adjustment ring including a plurality of spaced apart retention slots; and a plurality of vane levers, with a respective one of said plurality of vane levers including a body portion and a rampart extending transverse from said body portion, said body portion coupled to a corresponding one of said plurality of vanes and said rampart coupled within a respective one of said spaced apart retention slots to limit a radial motion of said adjustment ring, wherein each one of said plurality of vane levers moves in rolling and sliding contact with said adjustment ring as said plurality of vanes move between said open position and said closed position.

34. A vane pack for use in conjunction with a turbocharger in an entryway system, said vane pack comprising: a first vane ring disposed in said turbine housing interior and around said turbine wheel, said first vane ring comprising an annular disk including a first vane ring surface disposed between an inner circumferential ring and an outer circumferential ring with said inner circumferential ring defining an orifice for receiving said turbine wheel; a second vane ring disposed in said turbine housing interior and around said turbine wheel, said second vane ring comprising an annular disk including a second vane ring surface disposed between an inner circumferential ring and an outer circumferential ring with said innercircumferential ring defining an orifice for receiving said turbine wheel, said second vane ring surface spaced from said first vane to define an interior therebetween; a plurality of vanes rotatably disposed in said interior in a spaced apart manner along said first vane ring surface and said second vane ring surface with each of said vanes rotatable between an open position and a closed position including one or more intermediate positions; and a plurality of spacers disposed in a spaced apart manner along said first vane ring surface and said second vane ring surface and positioned circumferentially outward relative to each of said plurality of vanes with each respective one of said plurality of spacers positioned adjacent to a leading edge or a trailing edge of a corresponding respective one of said plurality of vanes and with each one of said plurality of spacers separated from an adjacent one of said plurality of spacers by at least at least one of said plurality of vanes, wherein a vane clearance distance between any portion of an adjacent side of a first one of said plurality of vanes and said first vane ring surface of said first vane ring is greater than a vane clearance distance between any portion of an adjacent side of a second one of said plurality of vanes and said first vane ring surface of said first vane ring so as to manipulate a vane moment associated with said first one of said plurality of vanes having said vane clearance distance that occurs during the operation of the entryway system.

35. A method for reducing wear on the body portion of a vane lever of a vane pack in an entryway system during operation of the entryway system, the entryway system comprising: a turbocharger for receiving exhaust gas from an internal combustion engine and for delivering compressed air to the internal combustion engine, the turbocharger comprising:a turbine housing comprising a turbine housing interior adapted to receive a turbine wheel having a plurality of equally spaced turbine blades, the turbine housing defining a turbine housing outlet in fluid communication with turbine housing interior, and one or more volutes adapted for fluid communication with the internal combustion engine and the turbine housing interior for delivering exhaust gas from the internal combustion engine to the turbine housing interior; a vane pack coupled to the turbocharger, the vane pack comprising: a vane ring disposed in the turbine housing interior and around the turbine wheel, the vane ring comprising an annular disk including a vane ring surface disposed between an inner circumferential ring and an outer circumferential ring with the inner circumferential ring defining an orifice for receiving the turbine wheel, the vane ring surface including the plurality of vanes rotatably disposed thereon in a spaced apart manner along the vane ring surface with each of the vanes rotatable between an open position and a closed position including one or more intermediate positions; and a plurality of spacers disposed in a spaced apart manner on the vane ring surface and positioned circumferentially outward relative to each of the plurality of vanes with each respective one of the plurality of spacers positioned adjacent to a leading edge or a trailing edge of a corresponding respective one of the plurality of vanes and with each one of the plurality of spacers separated from an adjacent one of the plurality of spacers by at least at least one of the plurality of vanes, an adjustment ring positioned adjacent to the second vane ring such that the second vane ring is positioned between the first vane ring and the adjustmentring, the adjustment ring including a plurality of spaced apart retention slots, and a plurality of vane levers, with a respective one of the plurality of vane levers including the body portion and a rampart extending transverse from the body portion, the body portion coupled to a corresponding one of the plurality of vanes and the rampart coupled within a respective one of the spaced apart retention slots to limit a radial motion of the adjustment ring, wherein each one of the plurality of vane levers moves in rolling and sliding contact with the adjustment ring as the plurality of vanes move between the open position and the closed position; said method comprising: manipulating a vane moment associated with a first one of the plurality of vanes by increasing a vane clearance distance between any portion of an adjacent side of the first one of the plurality of vanes and the vane ring surface of the vane ring such that the vane clearance distance is greater than a vane clearance distance between any portion of an adjacent side of a second one of the plurality of vanes and the vane ring surface of the vane ring.

36. The method of claim 35, wherein said step of manipulating vane moment associated with a first one of the plurality of vanes comprises introducing a bypass depression extending within the vane surface of the vane ring at a location adjacent to and beneath the adjacent side of the first one of said plurality of vanes when the first one of the plurality of vanes is in the closed position.

37. The method of claim 35, wherein said step of manipulating vane moment associated with a first one of the plurality of vanes comprises tapering a surface defined along the adjacent side of the first one of the plurality of vanes extending between a vane pivot point and a leading edge such that the vane clearance distance between the adjacent side ofthe first one of the plurality of vanes and the vane ring surface of the vane ring increases in a direction from the vane pivot point to the leading edge of the first one of the plurality of vanes, and / or, wherein said step of manipulating vane moment associated with a first one of the plurality of vanes comprises tapering a surface defined along the adjacent side of the first one of the plurality of vanes extending between a vane pivot point and a trailing edge such that the vane clearance distance between the adjacent side of the first one of the plurality of vanes and the vane ring surface of the vane ring increases in a direction from the vane pivot point to the trailing edge of the first one of the plurality of vanes.

38. The method of claim 35, wherein said step of manipulating vane moment associated with a first one of the plurality of vanes comprises chamfering a surface defined along the adjacent side of the first one of the plurality of vanes extending between a vane pivot point and a leading edge to form a recessed slot, and / or. wherein said step of manipulating vane moment associated with a first one of the plurality of vanes comprises chamfering a surface defined along the adjacent side of the first one of the plurality of vanes extending between a vane pivot point and a trailing edge to form a recessed slot.

39. The method of claim 36, wherein said step of manipulating vane moment associated with a first one of the plurality of vanes comprises reducing a length of the first one of the plurality of vanes, as measured between a vane pivot point and a leading edge of the first one of the plurality of vanes, and / or wherein said step of manipulating vane moment associated with a first one of the plurality of vanes comprises reducing a length of the first one of the plurality of vanes, as measured between a vane pivot point and a trailing edge of the first one of the plurality of vanes.

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