System for treating exhaust gas

Abstract

A system for treating exhaust gas from an engine is disclosed. The system may include a housing having an inlet port and an outlet port and defining a flow path therebetween. A fluid treatment element may be arranged in the flow path and configured to treat exhaust gas. A conduit may be fluidly connected with at least one of the housing ports and may have first and second tubular portions. The first portion may have a first cross-section with an inner diameter, and the second portion may have a generally elongated second cross-section with an inner width and an inner length. The inner length of the second cross-section of the conduit may be smaller than the inner diameter of the first cross-section of the conduit, and the inner width of the second cross-section of the conduit may be greater than the inner diameter of the first cross-section of the conduit.

Description

TECHNICAL FIELD

This disclosure relates generally to a system for treating gas and, more particularly, to a system for effectively and efficiently treating exhaust gas from an engine.

BACKGROUND

Exhaust treatment systems for treating exhaust gas from an engine are typically mounted downstream from an engine and may include a diesel particulate filter or some other exhaust treatment element arranged within the flow path of exhaust gas. The exhaust gas is typically forced through the exhaust treatment element to positively impact the exhaust gas, for example by reducing the amount of particulate matter or NOx introduced into atmosphere as a result of engine operation.

Exhaust treatment systems may be designed for (i) maximum positive effect on engine exhaust gas and (ii) minimal negative impact on engine performance. For example, exhaust treatment systems may be designed with diffuser elements and/or various complex geometries intended to better distribute exhaust flow across the face of an exhaust treatment element while minimally impacting exhaust flow resistance.

U.S. Pat. No. 6,712,869 to Cheng et al. discloses an exhaust aftertreatment device with a flow diffuser positioned downstream of an engine and upstream of an aftertreatment element. The diffuser of the '869 patent is intended to de-focus centralized velocity force flow against the aftertreatment element and even out an exhaust flow profile across the aftertreatment element. The disclosed design of the '869 patent is intended to enable a space-efficient and flow-efficient aftertreatment construction.

It may be desirable to use an improved exhaust treatment system that effectively impacts exhaust gas while minimally impacting engine performance. Moreover, it may be desirable to use an improved exhaust treatment system that accomplishes desired performance characteristics in a cost-effective and practically manufacturable manner.

The present disclosure is directed, at least in part, to various embodiments that may achieve desirable impact on aftertreatment effectiveness while improving one or more aspects of prior systems.

SUMMARY

In one aspect, a system for treating exhaust gas from an engine is disclosed. The system may include a housing having an inlet port and an outlet port and defining a flow path between the inlet port and the outlet port. The system may also include a fluid treatment element arranged in the flow path of the housing and configured to treat exhaust gas. A conduit may be fluidly connected with at least one of the housing ports and may have first and second tubular portions. The first portion may have a first cross-section with an inner diameter, and the second portion may have a generally elongated second cross-section with an inner width and an inner length. The inner length of the second cross-section of the conduit may be smaller than the inner diameter of the first cross-section of the conduit, and the inner width of the second cross-section of the conduit may be greater than the inner diameter of the first cross-section of the conduit.

It is to be understood that both the foregoing general description and the following detailed description are exemplary and explanatory only and are not restrictive of inventive scope, as claimed.

BRIEF DESCRIPTION OF THE DRAWINGS

The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate exemplary embodiments or features of the disclosure and, together with the description, help explain principles of the disclosure. In the drawings,

FIG. 1 is a partial diagrammatic sectioned front view of an exhaust treatment system;

FIG. 2 is a partial diagrammatic perspective view of a portion of the exhaust treatment system of FIG. 1;

FIG. 3 is a partial top plan view of the exhaust treatment system of FIG. 1;

FIG. 4 is a partial diagrammatic view of a conduit of FIG. 1;

FIG. 5 is a partial top view of the conduit of FIG. 4;

FIG. 6 is a partial side view of the conduit of FIG. 4;

FIG. 7 is a partial diagrammatic sectioned front view of an alternative exhaust treatment system;

FIG. 8 is a partial diagrammatic sectioned front view of another alternative exhaust treatment system; and

FIG. 9 is a partial diagrammatic sectioned front view of yet another alternative exhaust treatment system.

Although the drawings depict exemplary embodiments or features of the present disclosure, the drawings are not necessarily to scale, and certain features may be exaggerated in order to provide better illustration or explanation. The exemplifications set out herein illustrate exemplary embodiments or features, and such exemplifications are not to be construed as limiting the inventive scope in any manner.

DETAILED DESCRIPTION

Reference will now be made in detail to specific embodiments or features, examples of which are illustrated in the accompanying drawings. Generally, the same or corresponding reference numbers will be used throughout the drawings to refer to the same or corresponding parts. It should be appreciated that the terms width and length as used herein do not necessarily mean shortest dimension or longest dimension, respectively, and are merely used in conjunction with the drawings and the explanations herein to help describe and compare various relative dimensions of an embodiment. It should also be appreciated that the term diameter used herein does not necessarily connote a circular cross-section.

Referring now to FIG. 1, an exhaust treatment system 10 configured for treating exhaust gas from an engine is shown. The system may generally include a housing 12, a fluid treatment element 16 arranged within the housing 12, and inlet and outlet conduits 20a, 20c for communicating exhaust gas to and from the housing 12.

The housing 12 may generally define a longitudinal axis A1, along which the length of the housing 12 may generally extend. In one embodiment, the housing 12 may be formed from one or more generally cylindrical housing members 28a, 28b, 28c having generally tubular walls 36a, 36b, 36c that may cooperate to define a flow path 24 within the housing 12 extending generally along or generally parallel to the longitudinal axis A1. It should be appreciated that exhaust gas may flow in various directions at specific locations within the housing 12, and that the general resulting flow path 24 of exhaust gas through the housing 12 may be in a direction generally along or generally parallel to the longitudinal axis A1, i.e., away from the inlet conduit 20a and toward the outlet conduit 20c. The tubular walls 36a, 36b, 36c may each have an internal diameter D1, D2, D3 (FIG. 3) extending generally transverse to the flow path 24. The housing members 28a, 28b, 28c may be detachable from one another so that access to an interior portion of the housing 12 may be obtained, for example to service the system 10.

The housing 12 may have a first opening 30a (FIG. 3) through the generally tubular wall 36a to form an inlet port 32a and may have a second opening 30c through the generally tubular wall 36c to form an outlet port 32c. Thus, exhaust gas may be received into housing 12 through the inlet port 32a and may be discharged from housing 12 through the outlet port 32c. Between the inlet port 32a and the outlet port 32c, exhaust gas may flow along the generally longitudinal flow path 24 away from the inlet port 32a and toward the outlet port 32c. Since a fluid treatment element 16 may be arranged within the housing 12 and in the flow path 24, exhaust gas may be forced through the fluid treatment element 16 as it passes through the housing 12.

As best seen in FIG. 3, the first and second openings 30a, 30c forming the inlet port 32a and the outlet port 32c may be generally elongated. Each opening 30a, 30c may have a length L1, L2 (for example measured in a direction generally parallel with the longitudinal axis A1) and may have a width W1, W2 (for example measured in a direction generally parallel with an internal diameter D1 of the housing 12) greater than the respective length L1, L2. In one embodiment, the opening 30a may have a width W1 greater than or equal to 50 percent of the inner diameter D1 of the tubular wall 36a of the housing 12. For example, the width W1 may be greater than or equal to 60 percent of the inner diameter D1 of the tubular wall 36a of the housing 12. In another embodiment the width W1 may be greater than or equal to 70 percent of the inner diameter D1 of the tubular wall 36a of the housing 12. In one example, the width W1 could be approximately 175 mm, while the inner diameter D1 of the tubular wall 36a of the housing could be approximately 245 mm, so that the width W1 would be approximately equal to 71 percent of the inner diameter D1 of the tubular wall 36a of the housing. It yet another embodiment, the width W1 may be greater than or equal to 80 percent of the inner diameter D1 of the tubular wall 36a of the housing 12.

It should be appreciated that in some embodiments the openings 30a, 30c may have the same or substantially the same configuration. Alternatively, the openings 30a, 30c may have similar or substantially different configurations. For example, opening 30c may be the same width as, wider, or narrower than opening 30a and may be the same length as, longer, or shorter than opening 30a.

As referenced above, the fluid treatment element 16 may be arranged in the flow path 24 of the housing 12 and may be configured to treat exhaust gas from an engine. For example, the fluid treatment element 16 may be a filter element configured to remove particulate matter from exhaust gas. The element 16 may further or alternatively be a catalyzed substrate for catalyzing NOx. Further or alternatively, the element 16 may be any type of element for treating exhaust gas from an engine, for example by removing, storing, oxidizing, or otherwise interacting with exhaust gas to accomplish or help accomplish a desired impact on the exhaust gas or a constituent thereof.

The inlet conduit 20a may be configured and arranged to communicate exhaust gas with the inlet port 32a of the housing 12. The inlet conduit 20a may be rigidly fluidly connected with the inlet port 32a, for example via a welded connection between the conduit 20a and the tubular wall 36a around the circumference of the inlet port 32a. In the embodiment of FIG. 1, the inlet conduit 20a is connected with the tubular wall 36a proximate the opening 30a and is configured and arranged generally transverse to the longitudinal axis A1 of the tubular wall 36a so that a flow path 40a of exhaust gas through the inlet port 32a is generally transverse to the longitudinal axis A1 of the housing 12 and the tubular wall 36a.

The inlet conduit 20a may generally define a longitudinal axis A2a and may form a flow path 40a arranged generally along the longitudinal axis A2a. The longitudinal axis A2a may extend in a direction generally transverse to the first longitudinal flow path 24, for example so that exhaust gas transmitted through the inlet conduit 20a into the housing 12 substantially changes direction to flow generally along the flow path 24.

The inlet conduit 20a may include first and second tubular portions 44a, 48a arranged generally along the longitudinal axis A2a of the inlet conduit 20a. The first tubular portion 44a may have a generally circular cross-section 46a with an inner diameter D4a (FIG. 5) (for example measured in a direction generally parallel with the first longitudinal axis A1 of the housing 12) and an associated cross-sectional area through which exhaust gas may flow. The inner diameter D4a may have a centerpoint C4a dividing the inner diameter D4a in half.

The second tubular portion 48a may be arranged proximate the inlet port 32a of the housing 12 and may have a generally elongated cross-section 50a proximate the inlet port 32a. The cross section 50a of the second tubular portion 48a may have an inner diameter or length L3a (FIGS. 1 and 6), for example measured in a direction generally parallel with the first longitudinal axis A1 of the housing 12. As shown in the embodiment of FIG. 1, the inner diameter L3 of the cross section 50a of the second tubular portion 48a may be shorter than the inner diameter D4a of the cross-section 46a of the first tubular portion 44a. The inner diameter L3 may have a centerpoint C3a dividing the inner diameter L3a in half.

As shown in FIG. 6, the centerpoint C4a of the inner diameter D4a of the cross-section 46a may be offset from the centerpoint C3a of the inner diameter L3a of the cross-section 50a by an offset amount Za (for example measured in a direction generally parallel to the first longitudinal axis A1 of the housing 12). In one embodiment, the offset amount Za may be equal to or greater than 5 percent of the inner diameter D4a. In another embodiment, the offset amount Za may be larger, for example equal to or greater than about 20 percent of the inner diameter D4a. In one example embodiment, the inner diameter D4a may be approximately 120 mm, the inner diameter L3a may be approximately 75 mm, and the offset amount may be approximately 24 mm. In this example, the offset amount Za is about 20 percent of the inner diameter D4a.

The cross section 50a of the second tubular portion 48a may have an internal width W3a (FIG. 4), for example measured in a direction generally perpendicular to the inner diameter L3. The internal width W3a of the cross section 50a may be greater than the inner diameter L3 of the cross section 50a such that the cross section 50a has an elongated configuration. The internal width W3a of the cross section 50a may also be greater than the inner diameter D4 of the cross section 46a of the first tubular portion 44a. In one embodiment, the internal width W3a of the cross section 50a may be equal to or greater than 50 percent of the inner diameter D1 of the tubular wall 36a of the housing 12. For example, the internal width W3a of the cross section 50a may be equal to or greater than 60 percent of the inner diameter D1 of the tubular wall 36a of the housing 12. In another embodiment, the internal width W3a of the cross section 50a may be equal to or greater than 70 percent of the inner diameter D1 of the tubular wall 36a of the housing 12. In one example, the internal width W3a could be approximately 175 mm, while the inner diameter D1 of the tubular wall 36a of the housing 12 could be approximately 245 mm, so that the internal width W3a of the cross section 50a would be approximately equal to 71 percent of the inner diameter D1 of the tubular wall 36a of the housing 12. In yet another embodiment, the internal width W3a of the cross section 50a may be equal to or greater than 80 percent of the inner diameter D1 of the tubular wall 36a of the housing 12.

The cross sectional area of the cross section 50a of the second tubular portion 48a may be greater than the cross sectional area of the cross section 46a of the first tubular portion 44a. A cross-sectional area ratio AR may be defined by the cross-sectional area of the cross section 50a divided by the cross-sectional area of the cross section 46a. In one embodiment, the cross-sectional area ratio AR may be equal to or greater than about 1.1. In another embodiment, the cross-sectional area ratio AR may be equal to or greater than about 1.2. In another embodiment, the cross-sectional area ratio AR may be equal to or greater than about 1.5. In a further embodiment, the cross-sectional area ratio AR may be in the range of about 1.6 to 1.8, for example about 1.7. Controlling the cross-sectional area ratio AR helps control backpressure on the engine as well as velocity of exhaust flowing into the housing 12. The cross-sectional area ratio AR also helps control flow distribution into the housing 12 and toward the treatment element 16.

As indicated in FIG. 1, in one embodiment the dimensions, arrangements, features, and configurations of the outlet conduit 20c (e.g., A2c, C4c, D4c, L3c, W3c, Zc, 40c, 44c, 46c, 48c, and 50c, etc.) may be substantially identical to those of the inlet conduit 20a described above. FIG. 1 shows an embodiment in which the outlet conduit 20c is rotated 180 degrees compared with the orientation of the inlet conduit 20a and attached to the outlet port 32c in substantially the same way as the inlet conduit 20a is arranged and connected with the inlet port 32a. Of course, alternative embodiments may be dimensioned, arranged, or configured differently.

The outlet conduit 20c may be configured and arranged to communicate exhaust gas with the outlet port 32c of the housing 12. The outlet conduit 20c may be rigidly fluidly connected with the outlet port 32c, for example via a welded connection between the conduit 20c and the tubular wall 36c around the circumference of the outlet port 32c. In the embodiment of FIG. 1, the outlet conduit 20c is connected with the tubular wall 36c proximate the opening 30c and is configured and arranged generally transverse to the longitudinal axis A1 of the tubular wall 36c so that a flow path 40c of exhaust gas through the outlet port 32c is generally transverse to the longitudinal axis A1 of the housing 12 and the tubular wall 36c.

The outlet conduit 20c may generally define a longitudinal axis A2c and may form a flow path 40c arranged generally along the longitudinal axis A2c. The longitudinal axis A2c may extend in a direction generally transverse to the first longitudinal flow path 24, for example so that exhaust gas transmitted from the housing 12 into the outlet conduit 20c substantially changes direction to flow generally along the flow path 40c.

The outlet conduit 20c may include first and second tubular portions 44c, 48c arranged generally along the longitudinal axis A2c of the outlet conduit 20c. The first tubular portion 44c may have a generally circular cross-section 46c with an inner diameter D4c (measured in a direction generally parallel with the first longitudinal axis A1 of the housing 12) and an associated cross-sectional area through which exhaust gas may flow. The inner diameter D4c may have a centerpoint C4c dividing the inner diameter D4c in half.

The second tubular portion 48c may be arranged proximate the outlet port 32c of the housing 12 and may have a generally elongated cross-section 50c proximate the outlet port 32c. The cross section 50c of the second tubular portion 48c may have an inner diameter or length L3c, for example measured in a direction generally parallel with the first longitudinal axis A1 of the housing 12. As shown in the embodiment of FIG. 1, the inner diameter L3c of the cross section 50c of the second tubular portion 48c may be shorter than the inner diameter D4c of the cross-section 46c of the first tubular portion 44c. The inner diameter L3c may have a centerpoint C3c dividing the inner diameter L3c in half.

The centerpoint C4c of the inner diameter D4c of the cross-section 46c may be offset from the centerpoint C3c of the inner diameter L3c of the cross-section 50c by an offset amount Zc, for example measured in a direction generally parallel to the first longitudinal axis A1 of the housing 12. In one example embodiment, the inner diameter D4c could be approximately 120 mm, the inner diameter L3c could be approximately 75 mm, and the offset amount could be approximately 24 mm.

The cross section 50c of the second tubular portion 48c may have an internal width W3c, for example measured in a direction generally perpendicular to the inner diameter L3c. The internal width W3c of the cross section 50c may be greater than the inner diameter L3 of the cross section 50c such that the cross section 50c has an elongated configuration. The internal width W3c of the cross section 50c may also be greater than the inner diameter D4c of the cross section 46c of the first tubular portion 44c. In one embodiment, the internal width W3c of the cross section 50c may be equal to or greater than 50 percent of the inner diameter D3 of the tubular wall 36c of the housing 12. For example, the internal width W3c of the cross section 50c may be equal to or greater than 60 percent of the inner diameter D3 of the tubular wall 36c of the housing 12. In another embodiment, the internal width W3c of the cross section 50c may be equal to or greater than 70 percent of the inner diameter D3 of the tubular wall 36c of the housing 12. In one example, the internal width W3c could be approximately 175 mm, while the inner diameter D3 of the tubular wall 36c of the housing 12 could be approximately 245 mm, so that the internal width W3c of the cross section 50c would be approximately equal to 71 percent of the inner diameter D3 of the tubular wall 36c of the housing 12. In yet another embodiment, the internal width W3c of the cross section 50c may be equal to or greater than 80 percent of the inner diameter D3 of the tubular wall 36c of the housing 12.

The cross sectional area of the cross section 50c of the second tubular portion 48c may be greater than the cross sectional area of the cross section 46c of the first tubular portion 44c. A cross-sectional area ratio AR may be defined by the cross-sectional area of the cross section 50c divided by the cross-sectional area of the cross section 46c. In one embodiment, the cross-sectional area ratio AR may be equal to or greater than about 1.1. In another embodiment, the cross-sectional area ratio AR may be equal to or greater than about 1.2. In another embodiment, the cross-sectional area ratio AR may be equal to or greater than about 1.5. In a further embodiment, the cross-sectional area ratio AR may be in the range of about 1.6 to 1.8, for example about 1.7. Controlling the cross-sectional area ratio AR helps control backpressure on the engine. The cross-sectional area ratio AR also helps control flow distribution through the housing 12.

In one embodiment, the centerpoints C4a, C4c of the cross sections 46a, 46c may be separated by a first separation distance D7a measured in a direction generally parallel to the first longitudinal axis A1 of the housing 12. The centerpoints L3a, L3c of the cross sections 50a, 50c may be separated by a second separation distance D9a measured in a direction generally parallel to the first longitudinal axis A1 of the housing 12.

As illustrated in FIGS. 1 and 7-9, by varying configurations of the inlet and outlet conduits 20a, 20c, such as by selective orientation (e.g., rotation) of each or both conduit(s) during assembly, the distances D7, D9 may be managed as desired, for example to accommodate differing desired arrangements and differing exhaust system connection points. In FIG. 1, for example, the inlet conduit 20a and the outlet conduit 20c are arranged to minimize the separation distance D7a. Thus, the configuration shown in FIG. 1 may be used if the housing 12 is to be connected with an engine exhaust system with a minimal distance D7a between exhaust line connections (e.g., connection of engine exhaust supply to the inlet conduit 20a, and connection of outlet conduit 20c to an exhaust line for managing exhaust gas exiting the housing 12). More specifically, the embodiment of FIG. 1 shows an arrangement wherein the centerpoints C4a, C4c of the inner diameters D4a, D4c are separated by a first distance D7a measured in a direction generally parallel to the longitudinal axis A1 of the housing 12, and the centerpoints C3a, C3c of the inner diameters L3a, L3c are separated by a second distance D9a measured in a direction generally parallel to the longitudinal axis A1 of the housing 12, and the second distance D9a is greater than the first distance D7a.

Conversely, FIG. 9 shows the inlet conduit 20a and the outlet conduit 20c both turned 180 degrees (compared to the configuration in FIG. 1) in order to maximize the separation distance D7d between exhaust line connections, while maintaining the same separation distance D9a and D9d in both FIGS. 1 and 9. More specifically, the embodiment of FIG. 9 shows an arrangement wherein the centerpoints C4a, C4c of the inner diameters D4a, D4c are separated by a first distance D7d measured in a direction generally parallel to the longitudinal axis A1 of the housing 12, and the centerpoints C3a, C3c of the inner diameters L3a, L3c are separated by a second distance D9d measured in a direction generally parallel to the longitudinal axis A1 of the housing 12, and the second distance D9d is less than the first distance D7d.

Moreover, FIGS. 7 and 8 show alternative arrangements having the same separation distance D7b and D7c while enabling a shift of the housing toward the rightward direction (moving from FIG. 7 to FIG. 8). In FIGS. 7 and 8, the separation distances D7b, D7c are substantially equal to the separation distances D9b, D9c, respectively.

Referring to FIG. 1, the inlet conduit 20a may have substantially the same inner diameter measurements D4a, L3a as the inner diameter measurements D4c, L3c of the outlet conduit 20c. Thus, in one embodiment, the same piece-part may be used to create the inlet conduit 20a and the outlet conduit 20c. By having the ability to vary the rotational arrangements of such piece parts 20a, 20c during assembly, differing connection requirements or housing position requirements may be accommodated by fewer housing 12 configurations, for example to accommodate different OEM truck or machine manufacturing specifications such as desired pierce-point (connection) distances between the inlet conduit 20a and the outlet conduit 20c for connecting an exhaust treatment system 10 to an engine exhaust system.

INDUSTRIAL APPLICABILITY

With at least some of the foregoing arrangements and embodiments discussed herein (e.g., FIG. 1), using an inlet conduit 20a that is formed to have a shorter inner diameter L3a (connecting into the housing 12 at the inlet port 32a) than the inner diameter D4a (connecting, in one embodiment, to an exhaust line from an engine), an axial length of the housing 12 (for example as measured along the longitudinal axis A1) may be minimized while accommodating a relatively large exhaust line (not shown), such as an exhaust line having a connection diameter the same as the inner diameter D4a of the inlet conduit 20a. Similar axial length minimization may be facilitated by using an outlet conduit 20c such as that described hereinabove relative to FIG. 1 for example.

Moreover, it is expected that, in one embodiment, by using an inlet conduit 20a having a relatively wide opening (e.g., as indicated via dimension W3a in FIG. 4 compared with the dimension D4a shown in FIG. 5) for transmitting exhaust gas into the inlet port 32a of the housing 12, distribution of exhaust gas to a fluid treatment element 16 may be more effective since exhaust gas may form a relatively wide fluid path moving from the inlet conduit 20a and into the housing 12, as compared with an inlet conduit 20a having a more narrow opening for transmitting exhaust gas into the inlet port 32a. Thus, exhaust gas being transmitted into the housing 12 from the inlet conduit 20a may be more evenly distributed across the face of an exhaust treatment element 16 held within the housing 12 since the inlet conduit 20a (and the inlet port 32a) facilitates a wider fluid path entering the housing 12. Moreover, positive exhaust flow velocity effects may be achieved with such an arrangement.

Further, it is expected that, in one embodiment, by increasing the cross-sectional area of the inlet conduit 20a from a first cross-sectional area at a first cross-section 46a to a larger (for example wider) cross-sectional area at a second cross-section 48a, backpressure on the engine exhaust line (e.g., downstream of an engine combustion chamber) would be reduced, as compared with an inlet conduit having a relatively constant or decreasing cross-sectional area moving from the first cross-section to the second cross-section and into the inlet port of the housing. Moreover, such backpressure benefits are expected as well by using an outlet conduit 20c with differing first and second cross-sections 48c, 46c such as that described hereinabove relative to FIG. 1 for example.

From the foregoing it will be appreciated that, although specific embodiments have been described herein for purposes of illustration, various modifications or variations may be made without deviating from the spirit or scope of inventive features claimed herein. Other embodiments will be apparent to those skilled in the art from consideration of the specification and figures and practice of the arrangements disclosed herein. It is intended that the specification and disclosed examples be considered as exemplary only, with a true inventive scope and spirit being indicated by the following claims and their equivalents.

Claims

1. A system for treating exhaust gas from an engine, comprising: a housing having an inlet port and an outlet port and defining a first flow path between the inlet port and the outlet port;a fluid treatment element arranged in the first flow path of the housing and configured to treat exhaust gas;a conduit fluidly connected with at least one of the housing ports, the conduit having first and second tubular portions, the first portion having a first cross-section with an inner diameter, the second portion having a generally elongated second cross-section with an inner width and an inner length;wherein the inner length of the second cross-section of the conduit is smaller than the inner diameter of the first cross-section of the conduit, and the inner width of the second cross-section of the conduit is greater than the inner diameter of the first cross-section of the conduit; andwherein the second tubular portion defines a second flow path substantially perpendicular to the first flow path.

2. The system of claim 1, wherein the first cross-section is generally circular.

3. The system of claim 1, wherein: the first cross-section of the first portion of the conduit has a first cross-sectional area; andthe second cross-section of the second portion of the conduit has a second cross-sectional area greater than the first cross-sectional area.

4. The system of claim 3, wherein a cross-sectional area ratio is defined by the second cross-sectional area divided by the first cross-sectional area, the cross-sectional area ratio being equal to or greater than about 1.1.

5. The system of claim 4, wherein the cross-sectional area ratio is equal to or greater than about 1.2.

6. The system of claim 5, wherein the cross-sectional area ratio is equal to or greater than about 1.5.

7. The system of claim 6, wherein the cross-sectional area ratio is in the range of about 1.6 to about 1.8.

8. The system of claim 3, wherein: the conduit is an inlet conduit fluidly connected with the inlet port of the housing;an outlet conduit is fluidly connected to the outlet port, the outlet conduit having third and fourth tubular portions, the third portion of the outlet conduit having a third cross-section with an inner diameter, the fourth portion of the outlet conduit having a generally elongated fourth cross-section with an inner width and an inner length;wherein the inner width of the fourth cross-section of the outlet conduit is substantially greater than the inner diameter of the third cross-section of the outlet conduit.

9. A system for treating exhaust gas from an engine, comprising: a housing having an inlet port and an outlet port and defining a flow path between the inlet port and the outlet port;a fluid treatment element arranged in the flow path of the housing and configured to treat exhaust gas;a conduit fluidly connected with at least one of the housing ports, the conduit having first and second tubular portions, the first portion having a first cross-section with an inner diameter, the second portion having a generally elongated second cross-section with an inner width and an inner length;wherein the inner length of the second cross-section of the conduit is smaller than the inner diameter of the first cross-section of the conduit, and the inner width of the second cross-section of the conduit is greater than the inner diameter of the first cross-section of the conduit;wherein the flow path in which the fluid treatment element is arranged is defined at least in part by a tubular wall of the housing, the tubular wall having a substantially circular inner diameter transverse to the flow path; andwherein the width of the second cross-section of the conduit is equal to or greater than about 50 percent of the inner diameter of the tubular wall of the housing.

10. The system of claim 9, wherein the width of the second cross-section of the conduit is equal to or greater than about 70 percent of the inner diameter of the tubular wall of the housing.

11. The system of claim 1, wherein the conduit is an inlet conduit fluidly connected with the inlet port of the housing.

12. The system of claim 11, wherein: an outlet conduit is fluidly connected to the outlet port, the outlet conduit having first and second tubular portions, the first portion of the outlet conduit having a first cross-section with an inner diameter, the second portion of the outlet conduit having a generally elongated second cross-section with an inner width and an inner length;wherein the inner width of the second cross-section of the outlet conduit is substantially greater than the inner diameter of the first cross-section of the outlet conduit.

13. The system of claim 12, wherein the first cross-section of the outlet conduit is generally circular.

14. The system of claim 12, wherein: the first cross-section of the first portion of the outlet conduit has a first outlet cross-sectional area; andthe second cross-section of the second portion of the outlet conduit has a second outlet cross-sectional area greater than the first outlet cross-sectional area.

15. The system of claim 14, wherein a cross-sectional area ratio is defined by the second cross-sectional area of the outlet conduit divided by the first cross-sectional area of the outlet conduit, the cross-sectional area ratio being equal to or greater than about 1.1.

16. The system of claim 15, wherein the cross-sectional area ratio is equal to or greater than about 1.5.

17. The system of claim 16, wherein the cross-sectional area ratio is in the range of about 1.6 to about 1.8.

18. The system of claim 1, wherein: the housing generally defines a longitudinal axis and is formed at least in part by a tubular wall;the inlet port is defined at least in part by an opening in the tubular wall;the conduit is connected with the tubular wall proximate the opening and is configured and arranged generally transverse to the longitudinal axis of the tubular wall so that a flow path of exhaust gas through the inlet port is generally transverse to the longitudinal axis of the tubular wall.

19. The system of claim 18, wherein: the tubular wall has an inner diameter transverse to the longitudinal axis of the housing;the opening in the tubular wall is generally elongated and has a width greater than or equal to 50 percent of the inner diameter of the tubular wall of the housing.

20. The system of claim 19, wherein: the opening in the tubular wall has a width greater than or equal to 70 percent of the inner diameter of the tubular wall of the housing.