Regeneratable particulate filter trap system

Abstract: A particulate filter trap regeneration system and control mechanism is disclosed including a downstream vent tube section across which a pressure signal is derived as an analog of the exhaust gas stream velocity flowing through the particulate trap. A novel particulate loading parameter formula is disclosed by which the maximum acceptable pressure drop across a loaded particulate trap may be calculated and related to exhaust gas flow through the trap in order to determine when particulate trap regeneration should commence. In one embodiment, a vent-tube equipped with a venturi throat for increasing the accuracy of the pressure signal indicative of exhaust gas stream velocity is disclosed along with representative dimension parameters.

Description: This invention relates to an apparatus for controlling the operation of a system for regenerating a particulate filter trap by accurately determining the amount of trapped particulate matter. More particularly, this invention relates to a system for detecting the load of particulate matter within a particulate filter trap to initiate regeneration of the system when the load reaches a pre-set limit. By the year 1991, the particulate emission standards set by the Environmental Protection Agency (EPA) will require all urban busses to emit less than 0,14 g/kWh (0,1 g/hp · hr) of particulate matter. The same standard will apply to heavy duty trucks in 1994. Particulates are defined by the EPA as any matter in the exhaust of an internal combustion engine, other than condensed water, which is capable of being collected by a standard filter after dilution with ambient air at a temperature of 52 °C (125°F). Included in this definition are agglomerated carbon particles, absorbed hydrocarbons, including known carcinogens, and sulfates. These particulates are very small in size, with a mass median diameter in the range of 0,1-1,0 µ and are extremely light weight. Particulate filter traps have been developed which are effective to remove a sufficient quantity of the particulates from the exhaust gas of a typical diesel engine for a truck or bus to bring the exhaust emission into compliance with the EPA regulations. During normal operations of a typical vehicle engine, approximately 0,54 m³ (20 ft³) of particulate matter must be trapped per 160.000 km (100.000 mil) of vehicle operation. Obviously this particulate matter cannot be stored within the vehicle. Therefore successful long term operation of a particulate trap-based exhaust aftertreatment system (EAS) requires some method for removal of the trapped particulates. One method which has proven to be successful has been to provide means to burn off the trapped particles to regenerate the filter (e.g. Mogaka et a., "Performance and Regeneration Characteristics of a Cellular Ceramic Diesel Particulate Trap," SAE Paper No. 82 0272, published February 22-26, 1982). The regeneration process is typically initiated by a control system and is carried out by the delivery of heat to the inlet of the particulate trap at a temperature in excess of 650°C (1.200°F). The process results in oxidation of the filtered carbonaceous particulates in a manner that restores the trap's "clean" flow restriction but unavoidably produces temperature gradients and resultant thermal stresses in the particulate trap. The magnitude of these stresses must be controlled to a level that will not result in fatigue failure of the filter within its designated operating life. A number of factors influence the magnitude of the stresses such as regeneration gas flow rate, oxygen concentration, and trap inlet temperature distribution, all of which are determined by physical characteristics of the system design and hence are "fixed". The single most important, non-fixed factor in determining the magnitude of these stresses, and hence the life of the system is, the mass of particulates that is allowed to accumulate in the trap before the control system actively initiates the regeneration process. Should a trap be allowed to become excessively loaded with particulates, it can be predicted that, upon regeneration by burn off, deleterious thermal stress fatigue will result. One solution to the problem would be to burn off the trapped particulates at very frequent intervals but such a technique would be wasteful of the fuel needed to promote the burn off, and be partially self defeating of the ultimate purpose of particulate emission reduction since during burn off, the engine exhaust gases may be in some systems released to the atmosphere without filtration. Obviously, a need exists for determining as accurately as possible the mass of particles actually trapped but this need must be weighed against the expense and complexity of the sensing means used to make the determination. It can thus be seen that the means of determining the mass of particulates in the trap and therefore the means of deciding "when" to regenerate is by far the most crucial aspect of the control system. Fundamental to the design of a control system is the choice of physical parameters which are to be sensed to determine trap "loading" which in turn is dependent on the selection of a quantifiable parameter representing the degree to which a filter is loaded with particles. One approach has been to define a dimensionless parameter (M) equal to the ratio of the dimensionless pressure drop (pressure drop divided by the kinetic pressure, 1/2 ρ V²) across a loaded trap to that across a clean trap at the same Reynolds number, i. e. wherein V = flow rate of exhaust gas stream ρ = gas Density Obviously, M = 1 for a clean trap and is greater than 1 for a loaded trap. See pages 70 and 71 Magaka et al, supra. Measurement of the pressure drop across a loaded trap is fairly straight forward but direct measurement of the pressure drop across the same filter trap, having no particulates trapped therein but operating under identical flow conditions, is not possible and must be derived indirectly. One theoretical approach for estimating the clean, dimensionless pressure drop is disclosed in the Magaka et al, page 87, supra as follows: wherein k and x = empirically derived constants Re = Reynolds number based on mass flow rate and fluid viscosity Direct measurement of these physical quantities are difficult so that indirect measurements have been used based on the speed density law using engine displacement, RPM, intake manifold pressure and temperature and engine volumetric efficiency information. The starting point of the present invention is the publication "Development of a ceramic particulate trap for urban buses" from G.M. Cornetti et al., IVECO Engineering, Torino, Italy. As may be obtained from this prior art a regeneratable particulate filter trap system for a Diesel engine comprises regeneration means for the particulate filter, means for measuring quantities related to the clogging of the filter by particulates and means for processing measured quantities in order to periodically activate regeneration means each time the clogging level exceeds a given threshold. The means for measuring quantities related to the clogging of the filter are formed by a first pressure difference sensor which is installed across the filter and a second pressure difference sensor which is installed between the outlet of the filter and a venturi device installed downstream the filter. This apparatus also comprises a by-pass passage through which the gas stream is directed, when the filter is regenerated by the regeneration means. US - A - 4,492,079 discloses an apparatus for detecting degree of clogging in a particle trapping member of an internal combustion engine. It comprises a particle-trapping-apparatus which is installed in series downstream of an internal combustion engine. Downstream of this particle-trapping-apparatus an exhaust pipe and a conventional muffler making up a flow resistor are disposed in the exhaust gas flow parts. Two pressure sensing means are installed on both sides of the particle-trapping-apparatus for producing a pressure differential signal indicating the pressure drop across the particle-trapping-apparatus. Since all pressure sensing means operate with the atmospheric pressure as a reference and since downstream of the muffler the pressure is the atmospheric pressure, the second pressure signal implies the pressure drop across the pipe and muffler. All signals are detected by a computer which generates a regeneration starting signal, if the pressure drop across the particle-trapping-apparatus indicates that the clogging in the particle-trapping member has exceeded a predetermined threshold. The particle filter trap disclosed by DE - A - 39 00 155 comprises a particle filter trap combined with regenerating means. The exhaust gas from an internal combustion engine is directed through the particle filter trap and the pressure difference measured by two pressure sensing means is evaluated by computer means. If a certain pressure drop indicating the particle filter trap being loaded up to a predetermined threshold is reached a control signal for starting the regeneration process is produced by the computer means. For regenerating the particle filter trap the regenerating means are activated and a large fraction of the exhaust gas is directed through by-pass means while a fraction of about 10% of the whole exhaust gas is still directed through the particle filter trap, so that burnt particulate matter is transported out of the filter. Further attempts have been made to simplify the number of actual physical measurements required in a particulate regeneration control system such as disclosed in US - A - 4,608,640. This patent utilizes the pressure drop across the filter trap and a variable limit determined as a function of the inlet trap pressure. This approach ignores gas viscosity variation which is quite large over the normal operating range of a diesel engine. Similarly flawed approaches are disclosed in US - A - 4,630,438, US - A - 4,603,550, and US - A - 4,567,725. In another patent US - A - 4,610,138, the pressure ratio across the trap is used as an indication of trap loading. While possibly of greater utility, this approach is still an incomplete picture of the true relationship between the flow parameters and mass loading. The US - A - 4,492,079 plots trap differential pressure vs. trap outlet pressure in a system that does not simply discharge the trap into the atmosphere but rather flows the discharge through a length of pipe and then through a muffler. In effect, this uses the piping and muffler downstream of the trap as a flowmeter without any means for accounting for temperature effects. This is therefore extremely installation specific and very cumbersome to implement. Another approach has been to construct a physical analogue of a clean filter such as disclosed in US - A - 4,544,388 wherein an open channel, honeycomb structure is placed upstream of the actual filter. This honeycomb structure is said to have a porosity which is much larger than the filter trap so that none of the particulates will become entrapped. While simple in concept, physical analogs of the type disclosed in US - A - 4,544,388 suffer a number of disadvantages. For example, the large porosity necessary to insure that no particles become entrapped inherently causes the structure to be an inaccurate analog of the filter trap. Moreover, placement of the analog structure upstream of the actual filter trap renders the system susceptible to serious error should an exhaust leak occur anywhere between the analog structure and the downstream side of the filter trap. The accuracy of the determination of each pressure drop is a crucial point for the accuracy of the whole regeneration system. A need therefore exists for a simple, inexpensive, yet highly accurate and reliable particulate trap regeneration control system which overcomes the prior art deficiencies noted above. The primary object of this invention is to overcome the deficiencies of the prior art by providing apparatus for determining when to regenerate a particulate filter trap which is simple, inexpensive, yet highly accurate and reliable. According to the present invention, this object is achieved by an apparatus with all features of claim 1. As the flow rate sensing means is located downstream of the particulate filter trap the system is insensitive to exhaust gas leaks upstream of the particulate filter. Another improvement is achieved with an apparatus for determining when to regenerate a particulate filter trap which is used to collect particulates from an exhaust gas stream whenever the particulate filter trap reaches the predetermined limit defined by the formula of claim 15. By the structure of claim 7 a highly accurate differential pressure signal can be derived across the entire operating range of a typical diesel engine. In particular, the tube includes a venturi throat of a high recovery type according to claim 8. Other and more specific details may be obtained from the dependent claims and may further be appreciated by reference to the following Brief Description of the Drawings and Detailed Description of the Invention. Figure 1 is a schematic illustration of an integral bypass trap incorporating a particulate filter and including apparatus for regenerating the particulate filter trap designed in accordance with the subject invention. Figure 2 is a partially cutaway cross-sectional view of the integral bypass trap shown in Figure 1 and operating in a particulate trapping mode. Figure 3 is a partially cutaway cross-sectional view of the integral bypass trap illustrated in Figure 1 operating in a bypass mode. Figure 4 is a schematic illustration of a digital electronic computer arranged to receive pressure signals from the integral bypass trap and to generate therefrom a control signal for initiating regeneration of the particulate trap in accordance with a control law which forms part of the subject invention. Figure 5 is a partially cutaway cross-sectional view of the integral bypass trap illustrated in Figure 1 and incorporating an alternative embodiment of the tube to produce a more accurate differential pressure signal over the entire range of engine operating conditions. Figure 6 is a cross-sectional view of the vent tube used in the integral bypass trap shown in Figure 5. Referring initially to Figure 1, an overall schematic view of an integral bypass trap system 10 incorporating the subject invention is illustrated. An integral bypass trap 12 is shown connected at one end to an engine exhaust passage 14 and connected at the other end to an exhaust outlet passage 16. As will be explained more fully herein below, the integral bypass trap 12 includes a particulate filter trap adapted to receive the exhaust gases supplied through the engine exhaust passage 14 during the normal particulate trapping mode of operation. A honeycomb ceramic filter trap (such as illustrated in US-A-4,960,449) is preferred but other suitably designed filtering medium can be employed if it can efficiently capture diesel particulates and is stable in the engine exhaust environment and regeneration environment. Upon exiting the trap, the exhaust gases are directed to the exhaust outlet passage 16 via tubes (not illustrated) which will be described more fully hereinafter. Upon a determination that the particulate trap has reached a particulate loading limit, a bypass valve 18 is actuated to cause the exhaust gases supplied by passage 14 to be diverted around the loaded particulate filter trap and directed to the exhaust outlet passage 16 through either an alternate trap/tube set or through a noise control passage (muffler). Operation of the bypass valve 18 is controlled by an electronic control module 20 arranged to receive three separate pressure signals from the integral bypass trap 12. As explained more fully hereinbelow, the pressure signals indicate the pressure drop across the particulate filter trap, the pressure drop across the downstream tubes. and the absolute pressure of the tube inlet. Gas temperature measurements are also made at the inlet and outlet to the particulate filter trap to produce temperature signals T₁ and T₂. By means of a loading parameter formula constituting a portion of the subject invention, the pressure signals and temperature signals are employed to determine when to initiate filter trap regeneration hereinbelow. Referring more specifically to Figure 1, the pressure upstream of the particulate filter trap P₁ and the pressure downstream of the particulate filter trap P₂ is sensed and a signal thereof is sent to electronic control module 20 via signal lines 22 and 24, respectively. Third pressure signal, P₃, indicative of the pressure in the tube section of the integral bypass filter trap is sensed and a signal indicative thereof is transmitted to the electronic control module 20 via signal line 26. Pressure signals P₁, P₂ and P₃ may be fluidic or may be converted via a pressure transducer (not illustrated) into an electrical signal indicative of the corresponding pressure. As indicated by dashed lines 21, signals P₁, P₂ and P₃ may be electronically or fluidically converted into a trap differential pressure signal P₁-P₂ by a trap differential pressure sensing means 21a, into a vent differential pressure signal represented by the pressure drop, P₂-P₃ in the tube by a vent differential pressure sensing means 21b, and into an absolute pressure signal P₂ at the tube inlet by an absolute pressure sensing means 21c. The temperature, T₁ and T₂, of the gas at the inlet and outlet of the particulate filter trap are measured and converted into electrical signals supplied to the electronic control module 20 via lines 25 and 27, respectively. The exact manner by which these signals are used by the electronic control module 20 to determine the need for trap regeneration will be described in detail below. When the electronic control module 20 determines that the particulate trap loading has reached a predetermined limit, a regeneration control signal is produced and forwarded to a pneumatic valve and regulator control 28 via signal line 30 the effect of which is to bypass engine exhaust around the loaded trap and initiate operation of a burner 32. As a result of burner operation, high temperature gas is caused to flow through the particulate filter trap of sufficient volume and temperature to commence and sustain burn-off of the particulates within the filter trap. The burner 32 includes a blower 34 for providing a flow of air to the burner system. The pneumatic valve and regulator control 28 also supplies air to a fuel-burner atomizer 38 through supply conduit 40 and controls the burner isolation valve 36 through conduit 42. Bypass valve 18 is moved from its normal operating mode into its bypass mode via actuator 44 controlled by the pneumatic valve and regulator control 28 through conduit 46. A source of pressurized air for regulator control 28 is provided from the pressurized air tank 48 with which over the road vehicles, such as trucks, are typically equipped. Fuel is supplied to the fuel-burner atomizer 38 from the fuel tank 50 by means of a fuel pump 52 and a fuel line 54. A control valve 56 is operated by regulator control 28 through conduit 58. The electronic control module 20 operates blower 34 by actuating a relay 60 via conductor 62. The coil 64, adapted to the burner, is actuated through conductor 66 by the electronic control module 20. The fuel pump is energized via conductor 68. Finally, with respect to Figure 1, a series of status and warning lights 70 are provided for the convenience of the operator and are actuated by the electronic control module 20 via electrical conductor 72. In order to determine whether the burnoff of particulates is proceeding within defined limits, temperature measurements are made both upstream and downstream of the particulate trap and signals representative thereof are transmitted to the electronic control module 20 via signal lines 74 and 76, respectively. Reference is now made to Figure 2 which discloses in more detail the internal configuration of the integral bypass trap and associated bypass valve 18 designed in accordance with the subject invention. In particular, Figure 2 shows that the integral bypass trap 12 includes an outer housing 78 having an inlet 80 at one end and an outlet 82 at the other. Adjacent the inlet 80 is a monolithic ceramic particulate trap 84 or other filter medium suitably designed for diesel particulate filtration. This trap may be manufactured in accordance with the teaching contained in US-A-4,960,449 incorporated herein by reference. Trap inlet 84 is connected to housing inlet 80 through an inlet header 86 and is adapted to receive the entire exhaust gas flow, represented by arrows 88 so long as the bypass valve 18 is operating in its trapping mode as illustrated in Figure 2. An exhaust header 90 is designed to direct the gas exiting from trap 84 into a tube section 92 of the integral bypass trap 12. tube section 92 includes at least one (preferably two) tube(s) 94 mounted to receive the exhaust gas from header 90 and direct the exhaust gas toward outlet 82 of the housing 78. As will be explained more fully hereinbelow, the pressure drop through tube 94, if properly formed, can be used to determine the flow rate of exhaust gas stream 88 through trap 84. Using the tubes, which are located downstream of particulate trap 84, has particular utility because it renders the system insensitive to exhaust gas leaks that may occur at or upstream of outlet header 90. The pressure drop across particulate trap 84 may be sensed via pressure sensing taps 96 and 98 communicating respectively with the interiors of inlet header 86 and exhaust header 90, respectively. When the electronic control module 20 (Fig. 1) ascertains via receipt of pressure signals P₁, P₂ and P₃, and temperature signals T₁ and T₂ that trap regeneration is desirable, a regeneration control signal is generated, as explained above, which has the effect of moving bypass valve 18 from its trapping mode as shown in Figure 2 to its bypass mode as shown in Figure 3. When so adjusted, the exhaust gas stream 88 is caused to flow through a bypass passage 100 which is fluidically isolated from the exhaust gas passage flowing through inlet header 86, particulate trap 84, and outlet header 90. Exhaust bypass passage 100 directs the exhaust gas stream through a muffler section 102 which operates to suppress engine noise prior to the exhaust gas stream reaching housing outlet 82. Muffler section 102 is mounted internally within housing 78 adjacent to tubes 94. To understand more thoroughly the theoretical basis for the subject invention, reference is now made to Figure 4 which discloses schematically a digital electronic computer means 104 forming part of the electronic control module 20 which is programmed to implement the novel control system of the subject invention. In particular, the control scheme which forms an important part of the subject invention is based upon the discovery that the dimensionless loading parameter defined in the prior art as the pressure drop across a loaded particulate trap divided by the pressure drop across an identical, clean trap under the same flow conditions can be more accurately determined by means of the following formula: wherein L = a dimensionless trap loading parameter representative of the mass loading of particulates in the filter trap ΔP = differential pressure across the loaded trap V T = volume flow rate (or velocity) of the exhaust gas stream at the trap inlet C, D = predetermined constants empirically derived. Because the direct measure of volume flow rate V T of exhaust gas at the inlet of the particulate trap is quite difficult, the present invention includes the concept of determining first the volume flow rate through the venturi tube which is then corrected for the pressure and temperature differences that exist between the venturi inlet and the trap inlet. Accordingly, as illustrated in Fig. 4, five measured parameters are necessary to implement the subject invention, namely (1) trap differential pressure (P1-P2) (2) venturi differential presssure (inlet-to-throat) (P2-P3) (3) venturi inlet absolute pressure P2 (4) trap inlet temperature T1 (5) trap outlet temperature T2 Note: The point of measurement of the absolute pressure (3) is irrelevant since knowledge of absolute pressure at any of the three points plus the two differentials provides knowledge of the absolute pressure at any of the three points The gas volume flow rate for a venturi is given as: where K v = venturi calibration constant DP v = venturi differential pressure (P2-P3) T v = venturi inlet absolute temperature (T2) P v = venturi inlet absolute pressure (P2) The gas volume flow rate at the trap inlet, which is "V T " as used in the "L" equation, is determined by correcting for the pressure and temperature difference between trap outlet (venturi inlet) and trap inlet: where P1 is computed from the absolute pressure at the trap outlet plus the differential pressure across the trap: P1 = P2 + (P1-P2) As is now apparent, tube section 92 (and the associated sensors for determining the pressure drop P₂-P₃ and the absolute pressure and temperature at the tube inlet) constitutes a downstream flow rate sensing means for determining the exhaust gas flow rate at a point downstream of the particulate trap. This downstream flow rate can then be corrected for differences in pressure and temperature to provide a signal representative of gas flow rate at the inlet of the particulate trap. For a given particulate filter trap, constants C and D of the formula for the dimensionless trap loading parameter L can be determined empirically in the following manner. Two identically formed traps are placed in series in the exhaust gas stream of an internal combustion engine. The engine is operated over a wide range of operating conditions to establish data points and a wide range of fluid flow rate and temperature combinations at which the formula C · V D can be equated with the measured pressure drop across the downstream filter which is assumed to be operating in its clean condition. once the values for C and D are established for a given filter design and installation, it becomes possible to compute a pressure drop limit at any given measured flow rate through the filter which would be indicative that the mass of trapped particulates within the filter had reached a predetermined limit as defined by the above formula for the dimensionless trap loading parameter L. In accordance with good programming practice and to simplify computer operation, a look-up table can be preprogrammed into the digital electronic computer means 104. By means of a look-up table, a plurality of stored, predetermined limit values are established wherein the values represent the maximum allowable differential pressure drop in the exhaust stream as it passes through the particulate filter trap at corresponding exhaust gas stream fluid flow rates. Such a look-up table means 106 is illustrated in Figure 4 and is accessed at periodic intervals by controller 108 utilizing the calculated value for V T as determined from the five measurement parameters referred to above. Controller 108 also calculates the difference between P₁ and P₂ representative of the pressure drop across the particulate trap 84. Both the retrieved signal and the pressure drop across the particulate trap are forwarded to a comparator 110. When the pressure differential across the filter trap exceeds the retrieved limit, comparator 110 operates as a control signal generating means to generate a regeneration control signal to implement the trap regeneration mode of operation described above with reference to Figures 1, 2 and 3. Referring now to Figure 5, an alternative embodiment of the vent tube structure illustrated in Figures 2 and 3 is disclosed. In particular, Figure 5 shows a cross-sectional view of a tube having a high recovery venturi throat mounted therein. This arrangement has been found to provide a more accurate pressure signal representative of exhaust gas stream flow velocity. In particular, the use of a venturi throat improves significantly the accuracy of the pressure drop signal at low engine speed and load and thereby allows the regeneration system to operate safely at a higher dimensionless loading parameter L than would otherwise be possible. Turning now to Figure 6, the venturi throat is shown in an enlarged view and is shown to be mounted at the inlet end of a vent tube 94'. In order to provide a high recovery venturi throat, the inlet converging section 112a should have a truncated conical shape with a vertex angle between 19 and 23 degrees and an outlet diverging section 112b having a truncated conical shape with a vertex angle between 5 and 15 degrees. Ideally, the vent tube 94' is sized in accordance with the operating characteristics of the associated internal combustion engine to produce a sufficiently accurate differential pressure signal to allow the control signal generating means to determine accurately mass loading of particulates within the particulate filter trap. The tube should achieve this result while also minimizing the overall exhaust stream flow path restriction. In a typical installation a pair of tubes may be provided in parallel to handle all of the exhaust gas stream exiting the particulate filter. Such an arrangement will typically require a diameter c in the range of approximately 7,6 to 10,2 cm (3 to 4 inches), e. g. 8,9 cm (3.50 inches), a length e of approximately 38,1 to 63,5 cm (15-25 inches), e. g. 50.8 cm (20 inches), and a venturi inside throat diameter a of approximately 7,0 cm (2.75 inches) or less and a venturi throat length b of approximately 7,0 cm (2.75 inches) or less. With the construction shown in Figure 6, a ring piezometer is formed by the tube 94' and the venturi 112, allowing the venturi throat pressure (P₃) to be transmitted to pressure tap 118. As illustrated in Figure 6, the tube 94' is both axially and radially constrained by baffle 114 at the inlet end of the tube and is only radially constrained by baffle 116 at its outlet end in order to permit thermal contraction and expansion of the length of the tube. When so constrained, mounting of the venturi throat near the inlet end has the added advantage of minimizing the thermally induced strain on pressure tap 118. Positioning of the venturi throat at the inlet end of tube 94' also has the added advantage of minimizing losses to the tube since the conical inlet of the venturi is positioned in the airstream flow that would otherwise typically separate from the inside wall of the tube. For example, see the theoretical explanation contained in the Mogaka et al. paper, page 85, supra. The subject invention has been described with reference to an assembly in which the trap is contained in an integral housing which also includes the tube section and bypass/muffler section. Other packaging arrangements are possible and, under certain circumstances, more desirable. For example, the single housing may include a second trap and venturi section if no unfiltered exhaust gas can be allowed to escape. The same venturi section can serve both traps. Alternatively, entirely separate housings may be provided for the traps alone or for both the traps and the venturi sections. The subject invention would find particular application to over the road trucks and buses equipped with diesel engines and subject to restricted particulate emissions control requirements and regulations. The subject invention would also find application wherever it becomes desirable to employ a trap regeneration system for an exhaust gas particulate filter trap adapted to trap exhaust gas particulates failing in the range of particulate material which can be removed by a monolithic ceramic filter trap or other suitably designed filtering medium.

Claims: Regeneratable particulate filter trap system for collecting particulates from an exhaust gas stream of an internal combustion engine, comprising: a particulate filter trap (12) located in a housing (78) having an inlet (80) for the exhaust gas stream (88) located upstream of the particulate filter trap (12), having an outlet (82) for the exhaust gas stream (88) located downstream of the particulate filter trap (12), and having at least one tube (94, 94') located downstream of the particulate filter trap (12), this tube (94, 94') directing the exhaust gas stream (88) toward said outlet (82) after it has exited said particulate filter trap (12), regenerative means (32) operable in response to a control signal (30) to regenerate the particulate filter trap (12) by causing the trapped particles to burn away, trap differential pressure sensing means (21a) for generating a trap differential pressure signal (P₁-P₂) indicative of the fluid pressure drop in the exhaust gas stream (88) as it passes through the particulate filter trap (12), flow rate sensing means for generating a signal (P₂-P₃) related to the volume flow rate of the exhaust gas stream (88) downstream of the particulate filter trap (12), said flow rate sensing means including downstream pressure differential sensing means (21b) for generating a differential pressure signal indicative of the fluid pressure drop in the exhaust gas stream occurring as it passes through said at least one tube (94, 94') located downstream of the particulate filter trap (12), control signal generating means (20) connected with said trap differential pressure sensing means (21a) and with said flow rate sensing means for determining the mass loading of particulates within the particulate filter trap (12) and for generating said control signal (30) when the mass loading reaches a predetermined limit, and a by-pass passage (100) arranged so as to extend between said inlet (80) and said outlet (82) in a manner directing the exhaust gas stream (88) around the particulate filter trap (12) when the particulate filter trap (12) is being regenerated, characterized in that said housing (78) includes a plurality of said tubes (94, 94') located downstream of the particulate filter trap (12) this plurality of tubes (94, 94') directing the exhaust gas stream (88) toward said outlet (82) after it has exited said particulate filter trap (12), said tubes (94, 94') being positioned to operate in parallel, and said downstream pressure differential sensing means (21b) includes pressure averaging means for sensing the pressure in each of said tubes (94, 94'), said pressure averaging means generating said downstream differential pressure signal from the average of the pressure signals (P₃) measured in said tubes (94, 94'). System as defined in claim 1, characterized in that said housing (78) includes a muffler means (102) positioned within said by-pass passage (100) adjacent said tubes (94, 94') for suppressing engine noise carried by the exhaust gas stream while said particulate filter trap (12) is being regenerated, said tubes (94, 94') being arranged to direct the exhaust gas stream (88) around said muffler means (100) and through said housing outlet (82) when the exhaust gas stream (88) is passing through the particulate filter trap (12). System as defined in claim 1 or 2, characterized in that said housing (78) includes support baffle means (114, 116) for radially and axially securing at least one of said tubes (94, 94') at its inlet end to said housing (78) and for radially securing said tube (94, 94') at its exit end in a manner to accommodate thermal expansion and contraction in length. System as defined in any of the preceding claims, characterized in that said by-pass passage (100) is arranged to direct the exhaust gas stream (88) around said tubes (94, 94'). System as defined in any of the preceding claims, for use with an internal combustion engine having a normal operating range, characterized in that at least one of said tubes (94, 94') is formed to cause the fluid pressure drop sensed in association with said tube (94, 94') in combination with absolute pressure and temperature measurements to be related predictably to the flow rate of fluid through said tube (94, 94') throughout the entire normal operating range of the internal combustion engine. System as defined in any of the preceding claims, particularly in claim 5, characterized in that said housing (78) includes a pair of said tubes (94, 94') having a diameter in the range of approximately 7,6 - 10,2 cm (3-4 inches) and a length of approximately 38,1 - 63,5 cm (15-25 inches). System as defined in any of the preceding claims, particularly in claim 5, characterized in that at least one of said tubes (94, 94') includes a venturi throat (112) and that said downstream differential pressure sensing means (21b) generates a pressure signal indicative of the fluid pressure drop in the exhaust gas stream (88) as it is flowing through said venturi throat (112). System as defined in claim 7, characterized in that said venturi throat (112) is a high recovery venturi throat (112) with the inlet converging section (112a) having a truncated conical shape with a vertex angle between 19 and 23 degrees and an outlet diverging section (112b) having a truncated conical shape with a vertex angle between 5 and 15 degrees. System as defined in claim 7 or 8, characterized in that the venturi throat (112) has an inside diameter of approximately 7,0 cm (2.75 inches) or less and a length of approximately 7,0 cm (2.75 inches) or less. System as defined in claim 3 and claim 7, 8 or 9, characterized in that said venturi throat (112) is mounted adjacent said inlet end of said tube (94, 94') to minimize stress to pressure sensing means (118) for the tube pressure signal (P₃) induced by thermal expansion and contraction of said tube (94, 94'). System as defined in any of the preceding claims, particularly a combination of claims 6 to 9, characterized in that at least one of said tubes (94, 94') is sized in accordance with the operating characteristics of the associated internal combustion engine to produce a sufficiently accurate differential pressure signal (P₂-P₃) to allow said control signal generating means (20) to determine accurately the mass loading of particulates within the particulate filter trap (12) while minimizing the overall exhaust stream flow path restriction created by said tube (94, 94'). System as defined in any of the preceding claims, characterized in that said control signal generating means (20) includes a digital electronic computer means (104) for using the signal generated by said flow rate sensing means to determine a differential pressure signal limit representative of the pressure drop across the particulate filter trap (12) which would occur should the mass loading of particulates in the filter trap (12) reach said predetermined limit and for generating said control signal (30) when the signal generated by said trap differential pressure sensing means (21a) reaches or surpasses said differential pressure signal limit. System as defined in claim 12, characterized in that there is provided a first temperature sensing means for sensing the temperature of gas at the inlet (80) of the trap (12), said flow rate sensing means includes means for sensing the temperature and absolute pressure of gas entering said flow rate sensing means, and said digital electronic computer means (104) operates to determine the volume flow rate of gas entering the trap (12) by correcting the volume flow rate determined by said flow rate sensing means using the temperature and pressure differences between the gases entering the trap (12) and the flow rate sensing means. System as defined in claim 12 or 13, characterized in that said digital electronic computer means (104) includes look-up table means (106) including a plurality of stored predetermined limit values representing the maximum allowable differential pressure drop in the exhaust stream as it passes through the particulate filter trap (12) at corresponding exhaust gas stream fluid volume flow rates, said look-up table means (106) operating to retrieve one of said limit values dependent upon the level of signal produced by said flow rate sensing means, and comparing means (110) for comparing the retrieved limit value representing the maximum allowable differential pressure drop with the signal generated by said trap differential pressure sensing means (21a) to cause said control signal (30) to be generated when the signal generated by said trap differential pressure sensing means (21a) exceeds said retrieved limit value. System as defined in any of the preceding claims, preferably in claim 12 or 14, characterized in that said predetermined limit is determined by the formula wherein L = a dimensionless trap loading parameter representative of the mass loading of particles in the filter trap, P = differential pressure signal as measured by said trap differential pressure sensing means, V = volume flow rate of the exhaust gas stream at the trap inlet, that constants C and D are empirically derived constants dependent on the flow characteristics of the particulate filter trap (12) and the operating characteristics of the engine to which the apparatus is attached, that said constants C and D are empirically derived by placing identical particulate filter traps (12) of a predetermined design in series in the exhaust gas stream of a particular engine and measuring the pressure drop across the second particulate filter trap (12) at various engine operating and exhaust flow and temperature conditions to empirically derive values representative of the pressure drop across a filter of said predetermined design at the various operating and flow conditions when said filter is clean and using said empirically derived values to calculate said C and D constants based on the assumption that L for a given filter equals the pressure drop across the filter under a particular set of operating and flow conditions divided by the pressure drop across the same filter under the same operating and flow conditions when the filter is clean.

Inventors: HOUGH WALTER JAMES, MILLER PAUL R, HOUGH, WALTER JAMES, MILLER, PAUL R.
Applicants: CUMMINS ENGINE CO INC, CUMMINS ENGINE COMPANY, INC.
Application year: 1990
Main classification: F01N3
IPC codes: F01N3, F01N9, F01N1, F02D41