METHOD OF REDUCING TURBINE WHEEL HIGH CYCLE FATIGUE IN SECTOR-DIVIDED DUAL VOLUTE TURBOCHARGERS

Abstract

High cycle fatigue (HCF) in a turbine wheel of a sector-divided dual volute turbocharger, particularly a turbocharger where the tongue-to-blade gap is as small as from 1-3% of the wheel diameter, is reduced, by locally increasing the volute cross-sectional area just upstream of the tongues. Thereby, it becomes possible to reduce the force function of the exhaust gas pressure onto the turbine wheel blades. Modifying how the pressure presents itself to the wheel reduces blade excitation and, ultimately, HCF of turbine wheels. In another aspect of the invention, the angle of the tongues are modified to direct the exhaust more directly onto the turbine wheel than conventional tongues. It is surprising that this approach not only accomplishes the desired result, but does this without significant loss of turbine stage efficiency.

Claims

1. A turbine housing comprising a cavity for a turbine wheel, the cavity defining a turbine wheel axis of rotation, and at least first and second inlet volutes each comprising: a volute passage spiraling radially inwards about the turbine axis from a first end to a second end and having a flow axis; a tongue projecting between a radially outer portion of the second end of the volute passage and the cavity, the tongue terminating at a distal tongue tip, wherein for each volute when A is a flow-path cross-sectional area of a volute in mm.sup.2 taken normal to the flow axis, and R is a distance from a centroid of a volute cross-section of the volute to the turbine wheel axis of rotation in mm, the volute is configured so that when A/R is plotted on a graph having a horizontal axis representing an angular position θ in a circumferential direction of the volute and a vertical axis representing a ratio A/R of the flow-path cross-sectional area A to the distance R: a maximum A/R in a plane containing the turbine axis and the tongue tip is plotted as 100% at angular position θ.sub.max A/R of 0°, the volute length is plotted as a point on the horizontal axis, with the total of all volute lengths equaling 360°, a straight line is drawn from θ.sub.max A/R to the point representing volute length, a vertical line is drawn at volute length minus 10% of volute length, on this vertical line A/R of the volute is increased 2.5% to 20% over the A/R at the straight line.

2. The turbine housing of claim 1, wherein at θ.sub.max A/R minus 20° the A/R is 4-18% greater than the straight line.

3. The turbine housing of claim 1, wherein at θ.sub.max A/R minus 20° the A/R is 5-15% greater than the straight line.

4. A turbine housing comprising a cavity for a turbine wheel, the cavity defining a turbine wheel axis of rotation, and at least first and second inlet volutes each comprising: a volute passage spiraling radially inwards about the turbine axis from a first end to a second end and having a flow axis; a tongue projecting between a radially outer portion of the second end of the volute passage and the cavity, the tongue terminating at a distal tongue tip, wherein for each volute when A is a flow-path cross-sectional area of a volute in mm.sup.2 taken normal to the flow axis, and R is a distance from a centroid of a volute cross-section of the volute to the turbine wheel axis of rotation in mm, the volute is configured so that when A/R is plotted on a graph having a horizontal axis representing an angular position θ in a circumferential direction of the volute and a vertical axis representing a ratio A/R of the flow-path cross-sectional area A to the distance R: a maximum A/R in a plane containing the turbine axis and the tongue tip is plotted as 100% at angular position θ.sub.max A/R of 0°, the volute length is plotted as a point on the horizontal axis, with the total of all volute lengths equaling 360°, a straight line is drawn from θ.sub.max A/R to the point representing volute length, at the θ at which the straight line crosses 10% of maximum A/R, a vertical line is drawn, and the A/R on this vertical line is made 2.5-20% of maximum A/R greater than at the straight line.

5. The turbine housing of claim 1, wherein at the θ at which the straight line crosses 10% of maximum A/R, the A/R is 4-18% greater than the straight line.

6. The turbine housing of claim 1, wherein at the θ at which the straight line crosses 10% of maximum A/R, the A/R is 5-15% greater than the straight line.

Description

BRIEF DESCRIPTION OF THE SEVERAL VIEWS OF THE DRAWINGS

[0022] The present disclosure will hereinafter be described in conjunction with the following drawing figures, wherein like numerals denote like elements, and wherein:

[0023] FIG. 1 shows an in-line four cylinder internal combustion engine with exhaust flow separation maintained through exhaust manifolds to a pulse driven sector-divided dual volute turbine housing with linearly decreasing A/R;

[0024] FIG. 2 shows a turbine wheel with an exaggerated vibration at the blade leading edge and wheel backwall;

[0025] FIG. 3 shows measurement of A, centroid and R;

[0026] FIG. 4 is a plot of A/R decreasing linearly according to prior art;

[0027] FIG. 5 is a plot of A/R decreasing linearly according to prior art and decreasing concavely according to prior art;

[0028] FIG. 6 shows a prior art dual volute turbine housing with axis of rotation of wheel, volute centroids and radius measured between the two;

[0029] FIG. 7 shows the inventive modification of the volute in the vicinity of the tongue compared to a standard volute;

[0030] FIG. 8 is a plot of A/R vs θ for an inventive dual volute turbine housing; and

[0031] FIG. 9 illustrates the initial step in the process of modifying the design of a turbine.

DETAILED DESCRIPTION OF THE INVENTION

[0032] In the following one particular dual volute turbine wheel and turbine housing will be discussed in greater particularity for illustrative purposes as it relates to one particular design, but it will be apparent that the invention is applicable to alternative engine configurations, wheel families and turbine housings.

[0033] As diagrammatically illustrated in FIG. 1, the invention relates to reduction of HCF in a turbine wheel (2) in a sector-divided turbine housing (4) (two-scroll, two-tongue) for an exhaust-gas turbocharger system (1) as illustrated in FIG. 1. In this illustrative embodiment, the engine (8) has four cylinders (C.sub.1, C.sub.2, C.sub.3, C.sub.4), which release pulses of exhaust gas into a dual exhaust manifold (7). In a typical in-line four-cylinder engine, the firing order is 1-3-4-2, meaning that the first cylinder C.sub.1 combusts first, then the third cylinder C.sub.3 combusts second, then the fourth cylinder C.sub.4 combusts third, and the second cylinder C.sub.2 combusts fourth. Two cylinders (C.sub.1, C.sub.4) are fluidically coupled to a first exhaust manifold pipe (9), and two cylinders (C.sub.2, C.sub.3) are fluidically coupled to a second exhaust manifold (10). The exhaust manifolds have flanges (11, 13) via which they are coupled to turbocharger turbine housing flange (13) with maintenance of continuity of separate exhaust flow channels and thus separation of exhaust pulses (15). By fluidically coupling the first and fourth cylinders (C.sub.1, C.sub.4) together and coupling the second and third cylinders (C.sub.2, C.sub.3) together, the exhaust pulses released from each cylinder are separated by a maximum amount for the configuration. Stated differently, after the exhaust pulse from the first cylinder C.sub.1 enters the first exhaust manifold pipe (9), there is a pause before the exhaust pulse from the fourth cylinder C.sub.4 enters the first exhaust manifold (9) because the exhaust pulse from the third cylinder C.sub.3 first enters the second exhaust manifold (10). Likewise, after the exhaust pulse from the fourth cylinder C.sub.4 enters the first exhaust manifold pipe (9), there is a pause before the exhaust pulse from the first cylinder C.sub.1 enters the first exhaust manifold (9) because the exhaust pulse from the second cylinder C.sub.2 first enters the second exhaust manifold (10). These pauses result in separation between pulse energies in the exhaust manifolds (9, 10) such that interference between adjacent exhaust pulses in a manifold is reduced. The pulses from the third and fourth cylinders (C3, C4) are similarly separated. The turbine housing (4) has at least two symmetric or asymmetric flow channels (5, 6) that are fluidically substantially separate and can be flowed through by the exhaust gas. The two manifolds preferably deliver opposite and equal firing pulsations (15) to improve turbine efficiency and reduce manifold complexity. A turbine wheel (2) that is rotatably accommodated in the turbine housing (4) can be driven by the exhaust gas impinging on the of the turbine wheel having outer diameter (14). Twin-scroll turbo systems may have higher backpressure at low rpm (which may help turbo spool-up) and lower backpres sure at high rpm (which may help top-end performance).

[0034] The multiple volutes (5, 6) channel the exhaust gas so that it is introduced generally evenly along the outer diameter (14) of the turbine wheel (2) and expands in the turbine wheel whereby the turbine wheel may convert the exhaust gas into rotational mechanical energy. The pressure and temperature drop is converted into kinetic energy.

[0035] From an energy extraction perspective, it is desirable to keep the gap between tongues (16, 17) and turbine wheel as small as possible. However, as each blade of the rotating turbine wheel passes close to the flow obstruction formed by the tongues (16, 17), pressure variations impart an excitation to the blade, causing the blade to vibrate, in the way a tuning fork will vibrate when struck. If the tongues (16, 17) are positioned closer to the turbine wheel, the pressure variations increase, resulting in a greater excitation and therefore greater vibration of the blade. Moreover, with two tongues, each blade will experience two of these excitations per revolution.

[0036] As illustrated in FIG. 2, in such a turbocharger with sector-divided dual volute turbine housing, when aerodynamic forces act on the turbine blades (20), the blades are deflected from their static shape, being bent backwards and forwards. The accumulation of vibrational energy without an adequate dissipation mechanism can lead to increasing amplitude of vibration. Repeated bending or deflection leads to material fatigue, cracking and an ultimate fracture, referred to as high cycle fatigue (HCF) failures. HCF is characterized by low amplitude high frequency elastic strains. HCF is a type of fatigue caused by small elastic strains under a high number of cycles before failure occurs.

[0037] Particularly in “pulse turbocharging”, the turbine wheel experiences an axial push-back as it redirects pulse energy. This can help introduce excitation into the turbine wheel backwall (21). The turbine and turbine wheels according to the present invention are specifically designed to harness pulse energy and convert it to rotational velocity. Thus, the conversion of pressure and velocity from the exhaust gas for a pulse flow turbine wheel in a divided turbine housing is greater than the conversion of pressure and velocity from a steady state exhaust flow to the turbine wheel velocity.

[0038] The present invention is based on the discovery that “inflating” the volume of the volute passage just upstream of the tongue—a modification that might be expected to produce an increased pressure differential at the tongue—actually results in a reduction in the force function of the exhaust gas pressure onto the turbine wheel blades in the vicinity of the tongues results, and thus a decrease in excitation of the blades.

[0039] The basic terminology used to define the present invention will now be discussed in greater detail.

[0040] While technically the term “volute” may refer to either a physical structure of a component of the turbine housing, or the space within the structure through which exhaust gas flows, the term “volute” or “volute passage” as used herein will refer to the space within the structure.

[0041] For simplicity the term “A/R” is first explained using a single volute turbine housing as shown in FIG. 3. Building on the single volute explanation, the invention will then be explained as regards to a dual volute turbine housing as shown in in FIG. 6.

[0042] In FIG. 3 a prior art turbine housing mates fluidically to an exhaust pipe at a turbine foot. The turbine housing foot is usually of a standard design as it mates to exhaust manifolds of many engines. The foot can be located at any angle to, or position relative to, the snail-shell like “volute”. The transition from the foot gas passage 25 to the volute is executed in a manner which provides the best aerodynamic and mechanical compromise. A cross section through the passage where the foot passage transitions into the volute is shown as “A”. The turbine housing includes a cavity adapted to house a turbine wheel 2 rotatable about an axis of rotation 22. The volute includes a volute passage spiraling radially inwards about the turbine axis from a first end to a second end. The volute is designed to deliver exhaust flow from the engine in a uniform manner from the volute to a vortex centered on the turbine wheel axis. The volute passage ends at a tongue terminating at a tongue tip. The volute passage and tongue tip cooperatively define an inlet area feeding exhaust gas to the blades of the turbine wheel.

[0043] The widely used term A/R when used to define a turbine housing represents the ratio of the area at volute inlet slice “A” divided by R, the distance from the centroid of the shaded flow area 23 (in mm.sup.2) to the turbine wheel axis of rotation 22 (in mm). For example, a section of volute having an area of 509.27 mm.sup.2 and a radius of 48.5 would have an A/R of 509.27/48.5=10.5. The formula could alternatively be written A/R/D or A/(RD) taking turbine wheel diameter into account; however, when discussing only one particular wheel diameter, reference need only be made to A/R, it is simple to then divide that value by the wheel diameter to reach the nondimensionalized version of the value.

[0044] In order to keep flow attached to the volute walls and to keep the shape of the volute appropriate to the function of the volute, an A/R schedule for the turbine housing of FIG. 3 is plotted, as shown in FIG. 4, to ensure that there exist no inappropriate changes in section. According to the conventional understanding, the cross-sectional area of the volute is at a maximum at the inlet radially outward of the tongue measured normal or perpendicular to the direction of flow, and should gradually and continuously decrease until it becomes minimal (considering the small space provided between tongue and turbine wheel to prevent contact) as the tongue terminates near the wheel. The tongue projects between, and acts to partition, the second end of the volute passage from a part of the inlet or foot passage immediately radially adjacent thereto. The tongue terminates in a longitudinally distal tip, which is conventionally positioned radially adjacent to the turbine wheel to provide minimal clearance therewith, and acts to direct working fluid in the second end of the passage into the turbine wheel. As exhaust gas running along the volute passage passes the tip of the tongue there is a sudden increase in the area of the passage and the shape of that area (since the tongue no longer occupies any space in the passage). This leads to a sudden change in the A/R as shown in the left part of the graph (see FIG. 4, dark line). Thereafter, A/R decreases linearly around the turbine axis. That is, with increasing angular displacement from the tongue, A/R decreases directly proportionately.

[0045] FIG. 5 shows an A/R with a concave distribution according to prior art U.S. Pat. Nos. 10,378,369 and 10,781,704. A is a flow-path cross-sectional area of the scroll part (volute), and R is a distance from a centroid of a flow-path cross-section of the scroll part to a rotational axis of the turbine rotor blade. The scroll part is configured so that a first graph, having a horizontal axis (abscissa) representing an angular position θ in a circumferential direction of the scroll part and a vertical axis (ordinate) representing ratio A/R of the flow-path cross-sectional area A to the distance R, at least partially has a concave distribution.

[0046] FIG. 6 illustrates a dual volute turbine housing with foot passages 26, 27 transitioning to volutes 5, 6 with a maximum volute area A radially outward of tongue tips 16, 17. Each area A has a centroid. With increasing angular displacement from the volute inlet, the volute cross sectional area can be calculated, and from this, the centroid. One of the centroids 28 of volute 5 is shown in FIG. 6, and the distance from the axis of rotation 22 of the turbine wheel 2 to the centroid 28 is the radius R. One of the centroids 29 of volute 6 is shown, and the distance from the axis of rotation 22 of the turbine wheel 2 to the centroid 29 is the radius R. Since the decrease in A/R is linear, the illustrated turbine has conventional volutes 6, 7.

[0047] According to the present invention as illustrated in FIG. 7, the terminal part of the volute just upstream of the tongue is “inflated” compared to a conventional volute. FIG. 7 illustrates superimposed tongues and outer boundaries of a standard volute 30 and four inventive volutes 31, 32, 33 and 34 just upstream of the tongue. It is apparent that the distance of the outer wall of the standard volute 30 decreases gradually and continuously from the right side of this illustration all the way to line T which is the radial through the tip of the tongue 16. Dual volutes are frequently asymmetric, e.g., one volute extends 175° and the other extends 185° around the turbine wheel. For volute in which A/R decreases linearly, for a 175° volute this would mean a 10% change in A/R for every 10% of change in volute, i.e., every 17.5°. Drawing a straight line from maximum A/R of 100% (10.5 A/R in the Examples) to a minimum A/R at the tongue and continuing the line as an imaginary line to 175° at which the volute ends and the value corresponds to 0% of maximum A/R. At a position at which A/R of the imaginary line would be 10% of maximum A/R, θ would be 10% of total volute angle upstream of 175°, or 175° minus 17.5°, or 157.5°. See FIG. 9 showing the process of designing a 175° volute. At 157.5° (total volute arc minus 10% of arc), represented by vertical dash line, this line intersects the hypothetical straight line (linear progression A/R) at 10% of maximum A/R (10% of 10.5 A/R in the examples would be 1.05 A/R). Also shown in FIG. 9 is inventive convex reference shape for curve at 157.5° representing standard A/R+2.5% of maximum A/R, or 12.5% of total maximum A/R, in this example A/R 1.31. Also shown in FIG. 9 is inventive convex reference shape for curve at 157.5° representing standard A/R+20% of maximum A/R, or 30% of total maximum A/R, in this example A/R 3.15.

[0048] According to the invention, two key parameters can be varied: 1) the amount of local A/R increase compared to standard (preferably 2.5-20% increase in A/R as a percentage of total A/R at the throat), and 2) the angle at which the A/R starts to decline, i.e., the angle at which the tongue approaches the wheel. Of course, the physical appearance of such an A/R is manifest in the novel shape of the volute wall, the volute being “inflated” just upstream of the tongue.

[0049] According to the invention, A/R is increased at least 2.5%, and increased as much as 20%, over the straight line A/R, at a θ determined one of two ways. In FIGS. 7 and 8 A/R is illustrated increased from an additional 2.5% over straight line (so 12.5% maximum A/R) to an additional 10% (so 20% maximum A/R). An increase of 20% is possible but not shown (so 30% maximum A/R).

[0050] First, calculate maximum A of the flow-path cross-sectional area of the volute in mm.sup.2 taken normal to the flow axis. Determine R, the distance from a centroid of a volute cross-section of the volute to the turbine wheel axis of rotation in mm. Plot A/R on a graph having a horizontal axis representing displacement from an angular position θ in a circumferential direction of the volute and a vertical axis representing a ratio A/R of the flow-path cross-sectional area. Plot a maximum A/R in a plane containing the turbine axis and the tongue tip as 100% at angular position θ.sub.max A/R of 0°. Plot the minimal A/R at which the tongue tip is closest to the cavity for the turbine wheel at θ.sub.max A/R, draw a straight line from θ.sub.max A/R through θ.sub.max A/R and continue the line to 0% A/R, which is the hypothetical end of the volute, e.g., 175° in the examples (which is theoretical not actual because the tongue does not actually touch the wheel).

[0051] Subtract 10% of the volute length)(17.5°) from the total volute length)(175°) and mark this θ (157.5° in the examples). At the volute length minus 10% draw a vertical line. This vertical line will intersect the standard line at 10% maximum A/R. On this vertical line, increase total A/R by 2.5 to 20%.

[0052] The second way to determine where to plot the point determinative of the inventive curve is to draw the standard line as explained above, then determine the θ at which the straight line crosses 10% of maximum A/R, and at this θ increase the A/R by 2.5-20% of maximum A/R. The result will be the same.

[0053] For additional explanation as to design of turbocharger turbine housing volutes, reference is made to U.S. Pat. Nos. 8,585,355 and 10,301,952, the disclosures of which are incorporated herein by reference.

[0054] The invention will now be explained using illustrative concrete embodiments. The invention is in no way limited to these examples.

Example 1 12.5%

[0055]

TABLE-US-00001 A/R Θ (Θ) A (Θ) rs (Θ) [°] [mm] [mm.sup.2] [mm] 0.00 10.50 509.27 48.50 10.98 9.87 470.71 47.69 21.97 9.24 432.95 46.86 32.95 8.61 396.03 46.01 43.93 7.98 359.95 45.12 54.91 7.35 324.74 44.20 65.90 6.72 290.44 43.25 76.88 6.09 257.06 42.24 88.16 5.44 223.27 41.06 99.44 4.79 190.72 39.81 110.71 4.14 159.53 38.51 121.99 3.50 129.81 37.14 133.27 2.85 101.74 35.73 144.55 2.20 75.47 34.30 155.82 1.55 51.11 32.92 158.87 1.38 44.86 32.57 161.91 1.07 34.29 31.96 164.96 0.69 21.59 31.24 168.00 0.31 9.46 30.55 175.00 10.50 509.27 48.50 186.67 9.87 470.71 47.69 198.34 9.24 432.95 46.86 210.01 8.61 396.03 46.01 221.68 7.98 359.95 45.12 233.35 7.35 324.74 44.20 245.02 6.72 290.44 43.25 256.69 6.09 257.06 42.24 268.67 5.44 223.27 41.06 280.65 4.79 190.72 39.81 292.63 4.14 159.53 38.51 304.61 3.50 129.81 37.14 316.60 2.85 101.74 35.73 328.58 2.20 75.47 34.30 340.56 1.55 51.11 32.92 343.67 1.38 45.10 32.58 346.78 1.09 34.85 32.00 349.89 0.70 21.86 31.26 353.00 0.31 9.46 30.55

Example 2 15%

[0056]

TABLE-US-00002 A/R Θ (Θ) A (Θ) rs (Θ) [°] [mm] [mm.sup.2] [mm] 0.00 10.50 509.27 48.50 10.98 9.87 470.71 47.69 21.97 9.24 432.95 46.86 32.95 8.61 396.03 46.01 43.93 7.98 359.95 45.12 54.91 7.35 324.75 44.20 65.90 6.72 290.44 43.25 76.88 6.09 257.07 42.24 88.16 5.44 223.38 41.06 99.44 4.79 190.93 39.82 110.71 4.15 159.83 38.52 121.99 3.50 130.19 37.16 133.27 2.86 102.18 35.75 144.55 2.21 75.96 34.33 155.82 1.55 51.11 32.92 158.87 1.24 40.10 32.30 161.91 0.93 29.50 31.69 164.96 0.62 19.29 31.11 168.00 0.31 9.46 30.55 175.00 10.50 509.27 48.50 187.01 9.87 470.71 47.69 199.02 9.24 432.95 46.86 211.04 8.61 396.03 46.01 223.05 7.98 359.95 45.12 235.06 7.35 324.75 44.20 247.07 6.72 290.44 43.25 259.09 6.09 257.07 42.24 271.38 5.44 223.39 41.06 283.67 4.79 190.94 39.82 295.97 4.15 159.84 38.52 308.26 3.50 130.20 37.16 320.56 2.86 102.19 35.75 332.85 2.21 75.98 34.33 345.14 1.55 51.11 32.92 347.11 1.24 40.10 32.30 349.07 0.93 29.50 31.69 351.04 0.62 19.29 31.11 353.00 0.31 9.46 30.55

Example 3 17.5%

[0057]

TABLE-US-00003 A/R Θ (Θ) A (Θ) rs (Θ) [°] [mm] [mm.sup.2] [mm] 0.00 10.50 509.27 48.50 11.64 9.87 470.72 47.69 23.29 9.24 432.98 46.86 34.93 8.61 396.06 46.01 46.58 7.98 360.00 45.12 58.22 7.35 324.80 44.20 69.87 6.72 290.51 43.25 81.51 6.09 257.14 42.25 92.94 5.47 224.83 41.12 104.36 4.85 193.66 39.93 115.79 4.23 163.70 38.69 127.22 3.61 135.08 37.39 138.64 2.99 107.93 36.05 150.07 2.38 82.39 34.69 161.49 1.55 51.11 32.92 163.12 1.24 40.10 32.30 164.75 0.93 29.50 31.69 166.37 0.62 19.29 31.11 168.00 0.31 9.46 30.55 175.00 10.50 509.27 48.50 187.37 9.87 470.72 47.69 199.74 9.24 432.98 46.86 212.12 8.61 396.07 46.01 224.49 7.98 360.00 45.12 236.86 7.35 324.80 44.20 249.23 6.72 290.51 43.25 261.61 6.09 257.15 42.25 273.73 5.47 224.87 41.12 285.86 4.85 193.72 39.93 297.99 4.23 163.80 38.69 310.11 3.62 135.21 37.40 322.24 3.00 108.08 36.06 334.37 2.38 82.56 34.70 346.49 1.55 51.11 32.92 348.12 1.24 40.10 32.30 349.75 0.93 29.50 31.69 351.37 0.62 19.29 31.11 353.00 0.31 9.46 30.55

Example 4 20%

[0058]

TABLE-US-00004 A/R Θ (Θ) A (Θ) rs (Θ) [°] [mm] [mm.sup.2] [mm] 0.00 10.50 509.27 48.50 12.00 9.87 470.73 47.69 24.01 9.24 433.01 46.86 36.01 8.61 396.11 46.01 48.02 7.98 360.05 45.12 60.02 7.35 324.87 44.21 72.02 6.72 290.58 43.25 84.03 6.09 257.23 42.25 95.23 5.50 226.48 41.18 106.43 4.91 196.75 40.05 117.64 4.32 168.12 38.88 128.84 3.74 140.68 37.66 140.04 3.15 114.54 36.39 151.24 2.56 89.83 35.09 162.45 1.55 51.11 32.92 163.84 1.24 40.10 32.30 165.22 0.93 29.50 31.69 166.61 0.62 19.29 31.11 168.00 0.31 9.46 30.55 175.00 10.50 509.27 48.50 187.75 9.87 470.73 47.69 200.51 9.24 433.01 46.86 213.26 8.61 396.11 46.01 226.02 7.98 360.05 45.12 238.77 7.35 324.87 44.21 251.53 6.72 290.59 43.25 264.28 6.09 257.23 42.25 276.16 5.50 226.54 41.18 288.04 4.91 196.86 40.06 299.92 4.33 168.28 38.89 311.80 3.74 140.88 37.67 323.68 3.15 114.78 36.40 335.57 2.57 90.09 35.11 347.45 1.55 51.11 32.92 348.84 1.24 40.10 32.30 350.22 0.93 29.50 31.69 351.61 0.62 19.29 31.11 353.00 0.31 9.46 30.55

Comparative Example Standard

[0059]

TABLE-US-00005 A/R Θ (Θ) A (Θ) rs (Θ) [°] [mm] [mm.sup.2] [mm] 0.00 10.50 509.27 48.50 11.16 9.89 471.99 47.72 22.31 9.28 435.31 46.92 33.47 8.66 399.07 46.08 44.62 8.03 363.20 45.20 55.78 7.40 327.61 44.28 66.93 6.75 292.29 43.30 78.09 6.09 257.27 42.25 88.28 5.47 225.08 41.13 98.46 4.85 193.43 39.92 108.65 4.21 162.50 38.64 118.84 3.56 132.52 37.27 129.03 2.90 103.77 35.83 139.22 2.23 76.54 34.36 149.41 1.55 51.11 32.92 154.05 1.24 40.13 32.30 158.70 0.93 29.54 31.69 163.35 0.62 19.32 31.11 168.00 0.31 9.46 30.55 175.00 10.50 509.27 48.50 186.82 9.89 471.99 47.72 198.64 9.28 435.31 46.92 210.46 8.66 399.07 46.08 222.28 8.03 363.20 45.20 234.10 7.40 327.61 44.28 245.92 6.75 292.29 43.30 257.74 6.09 257.27 42.25 268.53 5.47 225.08 41.13 279.33 4.85 193.43 39.92 290.12 4.21 162.50 38.64 300.91 3.56 132.52 37.27 311.71 2.90 103.77 35.83 322.50 2.23 76.54 34.36 333.30 1.55 51.11 32.92 338.22 1.24 40.13 32.30 343.15 0.93 29.54 31.69 348.07 0.62 19.32 31.11 353.00 0.31 9.46 30.55

[0060] See FIGS. 7-9. The Comparative Example (Standard Volute) is plotted as the lowest line and is shown as a straight line between end points. In FIG. 9 only one of the dual volutes is shown. The second volute would have slightly different shape, since a first volute of 175° would be complemented by a second volute of 185° for a total of 360°. approximately the same values, just add 180°. In FIG. 8 both volutes are shown (175° and 185°). The precise shape of the volute is not the most important thing, what is important is that the volute is “inflated” in upstream of the tongue relative to a standard volute. For ease of definition of the increase in A/R, it will be assumed herein that the standard volute A/R, the base line from which the present deviation is calculated, is a straight line. Deviation of the present invention is measured from such a straight line.

[0061] It will be appreciated that the configurations and routines disclosed herein are exemplary in nature, and that these specific embodiments are not to be considered in a limiting sense, because numerous variations are possible. For example, the above technology can be applied to I-4, I-6, V-6, V-12, opposed 4, and other engine types. Moreover, the above-described turbine housing could be used with a two cylinder engine, such as a V-twin or inline two-cylinder engine, wherein exhaust gas pulses from each of the two cylinders is directed to one of the two volutes.

[0062] In at least one embodiment, the above-described turbine configuration may be used with a turbine housing with a volute that is both sector divided and meridonally divided. Stated differently, the turbine housing may be divided into two volutes with circumferentially-spaced tongues and each of the two volutes may be divided transversely by an integral wall. Such a turbine housing would have four divided volutes. Such a turbine housing is described by U.S. Pat. No. 3,218,029 and U.S. Publication No. 2017/0183975 A1. Such a turbine housing may be advantageously applied with a four-cylinder engine such that the exhaust pulses for each cylinder travels through a separate volute. While a four-cylinder engine may be illustrated and discussed for simplicity, the turbine housing could also be used with a six cylinder engine, eight cylinder engine, a twelve cylinder engine, or a sixteen cylinder engine (or any other engine with a total number of cylinders that is an integer multiple of four).

[0063] The above-described turbine could also be used with an internal combustion engine having an uneven number of cylinders, such as a three-cylinder engine or a five-cylinder engine. In such configurations, a greater number of cylinders would exhaust to a first volute than to a second volute. For example, in a three-cylinder engine, cylinders 1 and 2 may exhaust to the first volute (5) and cylinder 3 may exhaust to the second volute (6). Likewise, in a five-cylinder engine, cylinders 1, 3, and 4 may exhaust to the first volute (5) and cylinders 2 and 5 may exhaust to the second volute (6). To accommodate the different volumetric flow rates caused by the different numbers of cylinders exhausting to the two volutes, the two volutes (5, 6) may have different cross-sectional flow areas. In the above-described examples of three and five-cylinder engines, the second volute (6) may have a smaller cross-sectional area than the first volute (5) since less exhaust gas passes through the second volute (6).

[0064] All of the above U.S. patents, U.S. patent application publications, U.S. patent applications, foreign patents, foreign patent applications and non-patent publications referred to in this specification, are incorporated herein by reference in their entirety.

[0065] While particular elements, embodiments and applications of the present invention have been shown and described, it will be understood, of course, that the invention is not limited thereto since modifications may be made by those skilled in the art without departing from the spirit and scope of the present disclosure, particularly in light of the foregoing teachings.