the subject matter of the present disclosure is now described by way of example and with reference to certain illustrated embodiments . components that may be substantially the same in two or more embodiments are identified coordinately and are described with minimal repetition . it will be noted , however , that components identified coordinately in different embodiments of the present disclosure may be at least partly different . it will be further noted that the drawings included in this disclosure are schematic . views of the illustrated embodiments are generally not drawn to scale ; aspect ratios , feature size , and numbers of features may be purposely distorted to make selected features or relationships easier to see fig1 shows aspects of an example system 10 comprising soot filter 12 as further described hereinafter . the system includes engine 14 , in which a plurality of combustion chambers 16 are each coupled to intake manifold 18 and to exhaust manifold 20 . in the combustion chambers , combustion may be initiated and sustained via spark ignition and / or compression ignition in any variant . further , the engine may be configured to consume any of a variety of fuels : gasoline , alcohols , diesel , biodiesel , compressed natural gas , etc . the fuel may be supplied to the combustion chambers via direct injection , port injection , or any combination thereof . system 10 is configured to supply compressed air to engine 14 . air enters the system via air cleaner 22 and flows through to compressor 24 . the compressor may be virtually any type of air compressor — a supercharger compressor or electrically driven compressor , for example . in the embodiment shown in fig1 , the compressor is a turbocharger compressor mechanically coupled to turbine 26 , the turbine driven by exhaust from exhaust manifold 20 . after compression , the intake air is cooled in intercooler 28 en route to throttle valve 30 . the intercooler may be any suitable heat exchanger configured to cool the intake air for desirable combustion properties . in the illustrated embodiment , by - pass valve 32 is arranged so that the intake air pressure upstream of the throttle may be reduced , as desired , by routing compressed intake air back to the turbocharger inlet . as noted above , exhaust from exhaust manifold 20 flows to turbine 26 to drive the turbine . when reduced turbine torque is desired , some exhaust may be directed instead through waste gate 34 , by - passing the turbine . the combined flow from the turbine and the waste gate then flows through a plurality of exhaust - aftertreatment devices 36 , which include soot filter 12 . the number , nature , and arrangement of the exhaust - aftertreatment devices varies in the different embodiments of the present disclosure . in general , the exhaust - aftertreatment devices will include at least one catalyst configured to reduce a concentration of a pollutant in the exhaust flow . in one example , a catalyst may be configured to trap nitrogen oxides ( nox ) from the exhaust flow when the exhaust flow is lean and to reduce the trapped nox when the exhaust flow is rich . in other examples , a catalyst may be configured to disproportionate nox , or , to selectively reduce nox with the aid of a reducing agent . in other examples , a catalyst may be configured to oxidize residual hydrocarbons and / or carbon monoxide in the exhaust flow . different catalysts having any such functionality may be arranged in wash coats or elsewhere in the exhaust - aftertreatment devices , either separately or together . in some embodiments , soot filter 12 may be installed at an upstream position in the plurality of exhaust - aftertreatment devices 36 . the soot filter may be installed in the upstream position if it can be regenerated without periodic high - temperature discharge that could degrade downstream exhaust - system components such as the catalysts described above . in one embodiment , the soot filter may be continuously regenerated by engine exhaust , viz ., regenerated under operating conditions of the engine that result in exhaust gas above a first , relatively low , minimum regeneration temperature ( e . g ., without post injections , etc . )— in contrast to a periodic regeneration phase where extra heat and / or uncombusted fuel is provided in the exhaust flow to raise exhaust temperature above a relatively high minimum regeneration temperature . continuing in fig1 , part of the exhaust flowing from exhaust - aftertreatment devices 36 may be released into the atmosphere via a silencer , tail pipe , etc . however , the balance of the exhaust enters egr conduit 38 and flows to egr cooler 40 . the egr cooler may be any suitable heat exchanger configured to cool the exhaust to temperatures suitable for mixing into the intake air . the particular embodiment shown in fig1 includes venturi device 42 configured to suction the exhaust from egr conduit 38 and to mix the exhaust into the intake air . the amount of exhaust available for mixing is regulated by egr valve 44 . accordingly a mixture of fresh intake air and exhaust is provided to the inlet of compressor 24 , where it is compressed , and after cooling , supplied upstream of throttle valve 30 . in some embodiments , some or all of throttle valve 30 , by - pass valve 32 , waste gate 34 , and egr valve 44 may be electronically controlled valves configured to close and open at the command of an electronic control system . further , one or more of these valves maybe continuously adjustable . accordingly , fig1 shows electronic control system 46 , which may be any electronic control system of the vehicle in which system 10 is installed . the electronic control system may be operatively coupled to each of the electronically controlled valves and configured to command their opening , closure , and / or adjustment as needed to enact suitable control functions . to this end , the electronic control system may be operatively coupled also to various sensors arranged throughout the illustrated system - temperature sensors , pedal - position sensors , pressure sensors , etc . it will be understood that system 10 represents one of numerous contemplated engine - system embodiments that include a soot filter as further described below . other embodiments may differ from the illustrated system by omission of certain components - egr components , turbocharger components , etc ., and / or by inclusion of other components not shown in fig1 . fig2 schematically shows exterior configurations of soot filter 12 in two example embodiments . in particular , the drawing shows box - shaped soot filter 12 a and cylindrical soot filter 12 b . the box - shaped soot filter includes inlet 48 a and outlet 50 a , which may be rectangular , or may otherwise include at least one straight , peripheral edge . likewise , the cylindrical soot filter includes inlet 48 b and outlet 50 b , which may have a wholly or partly rounded periphery . in both illustrated embodiments , the length of the soot filter from the inlet to the outlet is denoted fl . it will be understood that soot filters of numerous other exterior configurations are embraced by the present disclosure . fig3 shows aspects of box - shaped soot filter 12 a in one example embodiment . in particular , the drawing shows a first corrugated layer 52 having a plurality of straight , parallel ridges ( e . g ., ridge 54 ) extending from inlet 48 a to outlet 50 a and aligned in first direction a . the drawing also shows second corrugated layer 56 having a plurality of straight , parallel ridges ( e . g ., ridge 58 ) extending from the inlet to the outlet and aligned in a second direction b oblique to first direction a . as further shown in fig3 , the ridges of the first corrugated layer and the ridges of the second corrugated layer are each angled obliquely along the entire path from the inlet to the outlet . thus , the illustrated embodiment provides no flow channel along the shortest ( straight ) path from the inlet to the outlet . in the embodiment shown in fig3 , first corrugated layer 52 and second corrugated layer 56 are stackable , and accordingly , the first corrugated layer is shown stacked upon the second corrugated layer . it will be understood that the first and second corrugated layers shown in the drawing may be among a plurality of staked layers arranged in box - shaped soot filter 12 a . thus , the first corrugated layer may be among a first series of corrugated layers having ridges aligned in the first direction , and the second corrugated layer may be among a second series of corrugated layers having ridges aligned in the second direction . accordingly , each corrugated layer of the first series may be stacked directly upon a corrugated layer of the second series . in the embodiment shown in fig3 , the first and second corrugated layers are stackable because the ridges of each layer are aligned against two parallel planes spaced apart by the ridge height h . accordingly , the box - shaped soot filter may include a plurality of corrugated layers stacked upon each other such that all the ridges are aligned against mutually parallel planes . in other embodiments , however , the corrugated layers may be stackable even though the ridges are not aligned against mutually parallel planes ( vide infra ). in some embodiments , the various corrugated layers of box - shaped soot filter 12 a may be formed from metal sheets bent to provide the desired corrugated substrate . in other embodiments , the corrugated layers may be formed from any other suitable heat - resistant material , formed by molding , extrusion , or any other suitable process . after the desired corrugated substrate is formed , a catalytic wash coat may applied to the corrugated layers via spray coating , dip - coating , electrolysis , or any other suitable process . the catalytic wash coat may comprise an oxidation catalyst that enables oxidation of soot by engine exhaust at suitably low temperatures , including normal exhaust temperatures of a diesel engine . accordingly , the wash coat may comprise a dpf wash coat . for purposes of illustration , various metrics of box - shaped soot filter 12 a are identified in fig3 . these include ridge height h , channel length cl , channel pitch p , radius of ridge curvature r , and layer offset angle θ , which is the angle between a ray aligned in direction a and an intersecting ray aligned in direction b . in addition , the open frontal area per channel ofa is defined , as shown in fig3 , as the shaded area between the first and second corrugated surfaces in the plane of the inlet . in embodiments where the inlet is oriented oblique to the direction of inlet flow , ofa may be defined as the geometric projection of the shaded area between the two corrugated surfaces in a plane normal to the direction of inlet flow . it will be understood that the drawing in fig3 , provided by way of example , places no particular restriction on directions a or b . accordingly various ranges of the layer offset angle θ are embraced by the present disclosure . in one embodiment , for example θ may be any angle between 10 and 80 degrees . in another embodiment , θ may be any angle between 30 and 60 degrees . fig4 shows a graph representing the changing hydraulic area for exhaust gas flow as a function of distance through box - shaped soot filter 12 a . the graph includes , at 60 , a plot of the hydraulic area versus distance from inlet 48 a along the length direction of the box - shaped soot filter ( e . g ., straight through from the inlet to the outlet ). for exhaust gas flow in this direction , the maximum hydraulic area is found at the inlet and follows a periodic function . as the exhaust gas flows through the filter from the inlet to the outlet , the hydraulic area is reduced and reaches zero at each of a series of stagger points labeled s . as the exhaust gas continues to the outlet , the hydraulic area then increases and reaches a maximum value at every half - way point between two adjacent stagger points . fig4 also shows , at 62 , a plot of hydraulic area versus distance along any given flow channel , in direction a or b . the hydraulic area for flow in this direction is also maximum at inlet 48 a and follows a periodic function , decreasing to one half the maximum value at each of a series of half - stagger points labeled hs . as the exhaust gas continues to the outlet , the hydraulic area then increases and reaches a maximum at every half - way point between two adjacent half - stagger points . based on the characteristics illustrated in fig4 , the exhaust flow rate within box - shaped soot filter 12 a can never be constant , either in the length direction or in the direction of any given channel . when the exhaust gas flowing through a channel encounters a reduced hydraulic area , it tends to cross over into a channel of larger hydraulic area . this behavior gives rise to a complex flow pattern having an elongated flow path , as shown in fig5 . the elongated flow path , together with a longer residence time for engine exhaust passing through the filter , may give rise to more efficient particle trapping relative to soot filters that lack the inventive structure of oblique , corrugated layers , as described herein . further , it will be evident from fig4 that the number of stagger points and the number of half - stagger points experienced by the exhaust flow increases with increasing filter length fl and with increasing layer offset angle θ . thus , the flow path and the residence time may be adjusted by varying either or both of these parameters to suit particular engine systems and applications . fig5 illustrates aspects of a pattern of exhaust flow through box - shaped soot filter 12 a in one example scenario . as exhaust gas flows through the channel inlet along a channel direction ( a or b ), the decreasing hydraulic area of the channel in the vicinity of a half - stagger point causes the exhaust gas to flow over the ridges of neighboring channels . similarly , exhaust flow in the length direction of the box - shaped soot filter is forced to go around each stagger point , thereby deviating from the length direction and increasing the effective path length through the filter . the flow characteristics represented in fig4 and 5 illustrate that as engine exhaust passed through box - shaped soot filter 12 a , a first exhaust flow may pass through the soot filter in a first direction ( direction a or b ) while the cross - sectional area of the first exhaust flow varies periodically over a first area range ( e . g ., between ofa / 2 and ofa ). meanwhile , a second exhaust flow may pass through the soot filter in a second direction ( e . g ., the length direction of the soot filter , which is oblique to the first direction ), while the cross - sectional area of the second exhaust flow varies over a second range ( e . g ., between zero and ofa ). further , a third exhaust flow may be diverted from the first exhaust flow in a region of the soot filter where the cross - sectional area of the first exhaust flow is reduced relative to ofa . by crossing over a corrugation ridge and into a neighboring flow channel , the third exhaust flow may continue through the soot filter in the first direction . flowing engine exhaust through the soot filter in this manner provides an advantageously longer net path through the filter and longer residence time in the soot filter , which by inference increases the efficiency of particle trapping . fig6 schematically shows inlet 48 a of box - shaped soot filter 12 a and inlet 48 b of cylindrical soot filter 12 b . the basic arrangement of corrugated layers of the cylindrical soot filter may be substantially the same as described above in the context of the box - shaped soot filter . in addition , the factors affecting the hydraulic areas in the flow channels may be substantially as described above . however , certain differences result from the different configurations of the two illustrated embodiments . in the cylindrical soot filter , for instance , the ridges of each corrugated layer are aligned to concentric shells instead of mutually parallel planes . accordingly , a first and second series of corrugated layers may be arranged concentrically , and each corrugated layer of the first series may be arranged directly over a corrugated layer of the second series . further , while the channels of the box - shaped filter may all be of the same size and shape , the size and shape of the channels in the cylindrical soot filter vary with distance from the central axis . in particular , the ridge pitch p , defined hereinabove , may increases outward from the central axis so that ridges of adjacent layers may be kept in registry with each other at the inlet . finally , it will be understood that the articles , systems and methods described herein are exemplary in nature , and that these specific embodiments or examples are not to be considered in a limiting sense , because numerous variations are contemplated . accordingly , the present disclosure includes all novel and non - obvious combinations and sub - combinations of the various systems and methods disclosed herein , as well as any and all equivalents thereof .