阅读说明：本技术 带倾斜扩压器的离心式压缩机 (Centrifugal compressor with inclined diffuser ) 是由 C·王 于 2019-05-08 设计创作，主要内容包括：一种压缩机,包括压缩机叶轮,该压缩机叶轮构造成当进气沿压缩机叶轮流动时围绕旋转轴线旋转。压缩机叶轮包括进口导风轮和出口导风轮。压缩机叶轮在进口导风轮处限定第一叶轮端并且在出口导风轮处限定第二叶轮端。第二叶轮端沿径向轴线而延伸。该压缩机还包括包封压缩机叶轮的压缩机壳体。压缩机壳体限定压缩机蜗壳。压缩机壳体部分地限定与压缩机蜗壳流体连通的扩压器。扩压器沿扩压器轴线而伸长。扩压器轴线相对于旋转轴线而倾斜。扩压器轴线相对于径向轴线而倾斜,以使从扩压器流动至压缩机蜗壳的进气的湍流最小化。(A compressor includes a compressor wheel configured to rotate about an axis of rotation as intake air flows along the compressor wheel, the compressor wheel including an inlet inducer and an outlet inducer.)

1, a centrifugal compressor comprising:

a compressor wheel configured to rotate about an axis of rotation as intake air flows along the compressor wheel, wherein the compressor wheel includes an inlet inducer and an outlet inducer, the compressor wheel defining an th impeller end at the inlet inducer and a second impeller end at the outlet inducer, the second impeller end extending along a radial axis, and the radial axis being perpendicular to the axis of rotation, and

a compressor housing enclosing the compressor impeller, wherein the compressor housing defines a compressor volute, the compressor housing partially defines a diffuser in fluid communication with the compressor volute, the diffuser configured to convert kinetic energy of the intake air to static pressure, the diffuser elongated along a diffuser axis, the diffuser axis inclined with respect to the rotational axis, the diffuser axis inclined with respect to the radial axis to minimize turbulence of the intake air flowing from the diffuser to the compressor volute.

2. The centrifugal compressor of claim 1, further comprising a center housing, wherein the compressor housing includes an th diffuser wall, the center housing includes a second diffuser wall, the th and second diffuser walls collectively define the diffuser, and each of the th and second diffuser walls is inclined relative to the radial axis.

3. The centrifugal compressor of claim 2, wherein the th diffuser wall and the second diffuser wall are parallel to each other.

4. The centrifugal compressor of claim 3, wherein each of the -th diffuser wall and the second diffuser wall is entirely linear.

5. The centrifugal compressor according to claim 4, wherein the diffuser defines a diffuser inlet and a diffuser outlet, the diffuser outlet in direct fluid communication with the compressor volute, the outlet inducer being closer to the diffuser inlet than the diffuser outlet, the outlet inducer being spaced from the inlet inducer in a direction , the direction being parallel to the axis of rotation, the entire diffuser wall being parallel to the diffuser axis, and the entire second diffuser wall being parallel to the diffuser axis.

6. The centrifugal compressor according to claim 5, wherein a distance is defined from the impeller end to the diffuser outlet, a second distance is defined from the impeller end to the diffuser inlet, and the distance is greater than the second distance to minimize turbulence of intake air flowing from the diffuser to the compressor volute.

7. The centrifugal compressor according to claim 6, wherein the diffuser includes a diffuser clip closer to the outlet inducer than the compressor volute, the diffuser clip defining the diffuser inlet, the diffuser clip partially defined by a diffuser wall portion of the second diffuser wall, and the entire diffuser wall portion of the second diffuser wall being parallel to the diffuser axis to minimize turbulence of intake air flowing from the compressor impeller to the diffuser.

8. The centrifugal compressor of claim 7, wherein the diffuser clip is defined in part by a sloped wall directly connected to the -th diffuser wall, and the sloped wall is sloped relative to the -th diffuser wall to facilitate flow of intake air from the compressor wheel to the diffuser.

9. The centrifugal compressor according to claim 8, wherein the diffuser clip has a tapered shape such that a clip width of the diffuser clip decreases in a second direction, the second direction being perpendicular to the th direction and the second direction being parallel to the radial axis, the diffuser inlet has a maximum inlet width, the diffuser outlet has a maximum outlet width, and the maximum inlet width is greater than the maximum outlet width to facilitate flow of intake air from the compressor wheel to the diffuser.

10. The centrifugal compressor according to claim 9, wherein the compressor housing defines a volute wall and the volute wall defines the compressor volute, the volute wall includes a volute wall portion proximate the second diffuser wall, the second diffuser wall includes a diffuser wall portion proximate the volute wall, and the volute wall portion is spaced from the diffuser wall portion in the direction to allow intake air to flow from the diffuser to the compressor volute without interruption.

Technical Field

The present application relates to centrifugal compressors with canted diffusers.

Background

A typical turbocharger assembly includes a turbine in fluid communication with the exhaust gas and a compressor in fluid communication with the intake air, the portion of the energy contained in the exhaust gas acts to turn or rotate a turbine wheel disposed inside the turbine assembly.

Disclosure of Invention

The present disclosure describes centrifugal compressors with diffusers that are angled with respect to the pure radial outlet flow direction.

In embodiments, a centrifugal compressor includes a compressor wheel configured to rotate about an axis of rotation as intake air flows along the compressor wheel, the compressor wheel including an inlet inducer (inducer) and an outlet inducer (reducer), the compressor wheel defining a wheel end at the inlet inducer and a second wheel end at the outlet inducer, the second wheel end extending along a radial axis, the radial axis being perpendicular to the axis of rotation.

The centrifugal compressor may also include a center housing, the compressor housing including a diffuser wall, the center housing including a second diffuser wall, the diffuser wall and the second diffuser wall collectively defining a diffuser, and each of the diffuser wall and the second diffuser wall being sloped with respect to a radial axis, the diffuser wall and the second diffuser wall being parallel to each other, the diffuser wall and each of the second diffuser wall being substantially linear, defining a diffuser inlet and a diffuser outlet, the diffuser outlet being in direct fluid communication with the compressor volute.

The diffuser includes a diffuser clip that is closer to the outlet inducer than the compressor volute, the diffuser clip defining a diffuser inlet, the diffuser clip partially defined by a diffuser wall of the second diffuser wall, the entire diffuser wall of the second diffuser wall being parallel to the diffuser axis to minimize turbulence of the intake air flowing from the compressor impeller to the diffuser.

The compressor housing defines a scroll wall and the scroll wall defines a compressor scroll, the scroll wall including a scroll wall portion proximate the second diffuser wall, the second diffuser wall including a diffuser wall portion proximate the scroll wall portion, the scroll wall portion being spaced from the diffuser wall portion in a direction to allow intake air to flow from the diffuser to the compressor scroll without interruption.

The present disclosure also describes turbocharger assemblies including a compressor configured to pressurize intake air as described above.

The present disclosure also describes a vehicle system including an engine including an intake manifold and an exhaust manifold.

The above features and advantages and other features and advantages of the present disclosure are readily apparent from the following detailed description of the best modes for carrying out the disclosure when taken in connection with the accompanying drawings.

Drawings

FIG. 1 is a schematic illustration of a vehicle including an internal combustion engine and a turbocharger assembly;

FIG. 2 is a schematic perspective view of the turbocharger assembly of FIG. 1;

FIG. 3 is a schematic cross-sectional side view of the turbocharger of FIG. 1;

FIG. 4 is an enlarged schematic cross-sectional side view of the turbocharger of FIG. 1 taken about area A of FIG. 3;

fig. 5 is a schematic enlarged sectional side view of the turbocharger of fig. 1 taken about area B of fig. 4.

Detailed Description

Those skilled in the art will recognize that directional descriptions (e.g., above, below, upward, downward, top, bottom, left, right, vertical, horizontal, etc.) are used for the figures descriptively to the accompanying drawings to aid the reader's understanding, and do not represent limitations on the scope of the disclosure (e.g., limitations on position, orientation, or use, etc.) defined by the appended claims.

Referring to the drawings, wherein like reference numbers represent like or corresponding parts throughout the several views; the vehicle system 8 includes an internal combustion engine 10, the internal combustion engine 10 configured to power a transmission (not shown). As non-limiting examples, the vehicle system 8 may be a motor vehicle, marine vessel, aerospace vehicle, robot, farm equipment, or other movable platform.

The internal combustion engine 10 may be a compression ignition or spark ignition internal combustion engine. Internal combustion engine 10 includes an engine block 12 defining a plurality of cylinders 14. Although four cylinders 14 are shown in FIG. 1, the internal combustion engine 10 may include more or fewer cylinders 14. An intake manifold 16 and an exhaust manifold 18 are mounted to the internal combustion engine 10. The intake manifold 16 functions to deliver intake air 20 (e.g., air or recirculated exhaust gas) to the cylinders 14 of the internal combustion engine 10. Cylinder 14 at least partially defines a variable volume combustion chamber operable to combust an intake air 20 containing fuel (not shown). Products of combustion or exhaust 22 are exhausted from the cylinders 14 into the exhaust manifold 18.

The internal combustion engine 10 also includes a turbocharger assembly 24, the turbocharger assembly 24 including a turbine 26, a centrifugal compressor 28, and a center housing 30, the turbine 26 including a turbine wheel 32 rotatable within the turbine 26, similarly, the compressor 28 including a compressor wheel 34 rotatable within the compressor 28, the center housing 30 supporting a shaft 36, the shaft 36 operatively interconnecting the turbine wheel 32 and the compressor wheel 34, the turbine wheel 32 thus rotating in unison with the compressor wheel 34 , the compressor 28 disposed in fluid communication with an inlet conduit 38, the inlet conduit 38 operatively directing the intake air 20 into the turbocharger assembly 24, the compressor 28 also disposed in fluid communication with the intake manifold 16 to direct the intake air 20 into the intake manifold 16, the turbine 26 further disposed in fluid communication with the exhaust manifold 18 to receive the exhaust gas 22 from the exhaust manifold 18, the exhaust gas 22 flowing from an outlet 40 to an exhaust gas discharge conduit 42 for subsequent release to the atmosphere.

The internal combustion engine 10 may include an Exhaust Gas Recirculation (EGR) system 44 the EGR system 44 includes a valve 46, the valve 46 operable to selectively and variably communicate portion 48 of the exhaust gas 22 into passage 50 for subsequent introduction into the inlet conduit 38 the portion 48 of the exhaust gas 22 may be introduced into the passage 50 at a location upstream or downstream of the turbine 26 the EGR system 44 may be used to reduce certain exhaust constituents, such as oxides of nitrogen.

In operation of the internal combustion engine 10, exhaust gas 22 is discharged from the cylinders 14 into the exhaust manifold 18, the exhaust gas 22 is delivered into the turbine housing 52, a portion of the energy contained in the exhaust gas 22 in the turbine housing 52 is used to rotate or spin the turbine wheel 32, then, the exhaust gas 22 is delivered to the exhaust discharge conduit 42, the turbine wheel 32 is caused to rotate or spin because the shaft 36 interconnects the compressor wheel 34 and the turbine wheel 32, the rotation of the compressor wheel 34 causes the intake air 20 to be directed into the compressor 28, the intake air 20 is pressurized in the compressor 28 and directed into the intake manifold 16 for introduction into the cylinders 14. by increasing the pressure inside the intake manifold 16, the density of the intake air 20 is increased.

Referring to fig. 2 and 3, an exemplary embodiment of the turbocharger assembly 24 includes a turbine 26, the turbine 26 in turn including a turbine housing 52. The turbine housing 52 may be coupled to the center housing 30 using any suitable coupling 104 (e.g., a clamp). The turbine housing 52 defines a turbine scroll or volute 54, the turbine scroll or volute 54 being operable to direct the exhaust gas 22 radially inward toward the turbine wheel 32 to effect rotation of the turbine wheel 32. The turbine 26 may also include a variable geometry mechanism (not shown) operable to vary the flow pattern of the exhaust gas 22 (FIG. 1) from the turbine volute 54 to the turbine wheel 32. The flow of the exhaust gas 22 (FIG. 1) along the turbine wheel 32 causes the turbine wheel 32 to rotate or spin. Because the shaft 36 is coupled to the turbine wheel 32, rotation of the turbine wheel 32 also causes the shaft 36 to rotate. Rotation of the shaft 36 correspondingly drives rotation of the compressor wheel 34 of the compressor 28.

Referring to fig. 3 and 4, the compressor 28 includes a compressor housing 63, the compressor housing 63 defining an inlet 62, the inlet 62 operable to direct the intake air 20 axially toward the compressor wheel 34. The center housing 30 is disposed between the turbine housing 52 and the compressor housing 63. The compressor housing 63 defines a compressor cavity 65 and a compressor volute 68, the compressor cavity 65 being disposed in fluid communication with the inlet 62, the compressor volute 68 operable to direct pressurized intake air 20 radially outward toward the intake manifold 16 (fig. 1). The compressor housing 63 encloses the compressor wheel 34.

Compressor wheel 34 is disposed within compressor cavity 65 and includes an inlet inducer 80, an outlet inducer 82, and a plurality of compressor blades 86 disposed along inlet inducer 80 and outlet inducer 82, outlet inducer 82 is spaced from inlet inducer 80 in a th direction FD compressor wheel 34 includes a wheel end 108 at inlet inducer 80 and a second wheel end 110 at outlet inducer 82 wheel end 108 is disposed further from turbine wheel 32 than second wheel end 110, second wheel end 110 extends along a radial axis RX (FIG. 4). radial axis RX is perpendicular to rotational axis R. direction FD is parallel to rotational axis R. radial axis is parallel to second direction SD.. second direction SD is perpendicular to 36 direction FD.

As the compressor wheel 34 rotates, the inlet inducer 80 directs the intake air 20 into the compressor housing 63, once the intake air 20 is inside the compressor housing 63 and the compressor blades 86 direct the flow of the intake air 20 from the inlet inducer 80 toward the outlet inducer 82, as the compressor wheel 34 rotates, the outlet inducer 82 directs the intake air 20 from the compressor wheel 34 to the compressor volute 68 through the diffuser 66 defined by the compressor housing 63. the diffuser 66 converts the kinetic energy of the intake air 20 to static pressure.

Specifically, the cross-sectional dimension of the compressor wheel 34 may increase in the direction FD from the wheel end 108 to the second wheel end 110. the direction FD is parallel to the axis of rotation R.

Referring to fig. 4 and 5, the compressor housing 63 partially defines a diffuser 66. The diffuser 66 is in fluid communication with a compressor volute 68 and is configured to convert kinetic energy of the intake air 20 into static pressure. In addition, the diffuser 66 is elongated along a diffuser axis that is inclined relative to the rotational axis and the diffuser axis is inclined relative to the radial axis RX to minimize turbulence of the intake air flowing from the diffuser to the compressor volute 68.

Compressor housing 63 defines a volute wall 70, volute wall 70 defines a compressor volute 68, compressor housing 63 includes a th diffuser wall 72, center housing 30 includes a second diffuser wall 74, a th diffuser wall 72 and second diffuser wall 74 collectively define a diffuser 66, a th diffuser wall 72 and second diffuser wall 74 each are inclined relative to radial axis RX to minimize turbulence of the intake air 20 flowing through diffuser 66. accordingly, an oblique angle θ is defined from diffuser axis DX to radial axis RX (fig. 5). theta is greater than zero.

Diffuser 66 defines a diffuser inlet 76 and a diffuser outlet 78, diffuser outlet 78 is in direct fluid communication with compressor volute 68, outlet inducer 82 of compressor impeller 34 is closer to diffuser inlet 76 than diffuser outlet 78, the entire diffuser wall 72 is parallel to diffuser axis DX and the entire second diffuser wall 74 is parallel to diffuser axis DX to minimize turbulence of intake air 20 flowing through diffuser 66. FD along direction defines a distance D1 (FIG. 3) from the -th impeller end 108 to the diffuser outlet 78. FD along direction defines a second distance D2 (FIG. 3) from the -th impeller end 108 to the diffuser inlet 76. distance D1 is greater than second distance D2 to minimize turbulence of intake air 20 flowing from diffuser 66 to compressor volute 68.

The diffuser 66 includes a diffuser clip 84, the diffuser clip 84 being closer to the outlet inducer 82 than the compressor volute 68. The diffuser clip 84 defines the diffuser inlet 76 of the diffuser 66. Further, the diffuser clip 84 is partially defined by the diffuser wall portion 88 of the second diffuser wall 74. The entire diffuser wall portion 88 of the second diffuser wall 74 is parallel to the diffuser axis DX to minimize turbulence of the intake air 20 flowing from the compressor wheel 34 to the diffuser 66. The bottom of the diffuser clip 84 is undercut to prevent flow obstruction. Thus, the manufacturing tolerances at the diffuser clip 84 may be greater than for other compressors.

The diffuser clip 84 is defined in part by a slanted wall 90 that is directly connected to the diffuser wall 72 at the slanted wall 90 is slanted with respect to the diffuser wall 72 at to facilitate the flow of the intake air 20 from the compressor wheel 34 to the diffuser 66 the diffuser clip 84 has a tapered shape so that the clip width PW of the diffuser clip 84 decreases in the second direction SD. As described above, the second direction SD is perpendicular to the direction FD, the second direction SD is parallel to the radial axis RX the diffuser inlet 76 has a maximum inlet width MW, and the diffuser outlet 78 has a maximum outlet width OW. the maximum inlet width MW is greater than the maximum outlet width OW to facilitate the flow of the intake air 20 from the compressor wheel 34 to the diffuser 66.

The volute wall 70 includes a volute wall portion 92 proximate the second diffuser wall 74 includes a diffuser wall portion 94 proximate the volute wall portion 92 is spaced from the diffuser wall portion 94 in direction FD of to allow the intake air 20 to flow uninterrupted from the diffuser 66 to the compressor volute 68. in other words, the second diffuser wall 74 is not recessed relative to the volute wall 70 to avoid flow obstruction where the diffuser 66 intersects the volute wall 70.

While the best modes for carrying out the disclosure have been described in detail, those familiar with the art to which this disclosure relates will recognize various alternative designs and embodiments for practicing the disclosure within the scope of the appended claims.