I. Field of the Invention
The present invention relates generally to direct injection internal combustion engines and, more particularly, to a method and apparatus for reducing engine noise, especially at low engine speeds.
II. Description of Related Art
Direct injection internal combustion engines of the type used in automotive vehicles have enjoyed increased popularity due in large part to their fuel economy. In a direct injection engine, the fuel injector is mounted in the engine block and has its fuel injection outlet end open directly to the internal combustion chamber. Consequently, upon activation or opening of the fuel injector, the fuel is injected directly into the internal combustion engine, rather than upstream from the fuel intake valves as in the previously known multi-point fuel injectors.
In order to supply fuel at a sufficiently high pressure to overcome the high pressures of the combustion chambers, these previously known direct injection engines include a high pressure fuel pump having an inlet connected to a fuel source such as the fuel tank, and an outlet open to a fuel rail. The fuel rail, in turn, is fluidly connected to the engine fuel injectors.
The previously known high pressure fuel pumps used with direct injection engines typically include a plunger that is reciprocally driven by a multi-lobe cam. An inlet valve is fluidly disposed in series between the fuel pump inlet and the fuel source while an outlet valve is fluidly connected in series between the fuel pump and the fuel rail. During reciprocal movement of the plunger, the plunger inducts fuel through the fuel inlet valve when the plunger moves in a first direction, and conversely the fuel pump pumps fuel out through the outlet valve to the fuel rail upon movement of the plunger in the opposite direction.
One disadvantage with the previously known direct injection engines, however, is that such engines tend to be noisy, especially at low engine speeds such as less than 1,000 rpm. The engine noise, furthermore, is largely attributable to three separate events.
More specifically, the fuel injectors themselves create noise when activated or opened due to the high pressure fuel injection. This high pressure fuel injection is oftentimes accompanied by noise causing vibration of various engine components.
The opening of the fuel inlet valve in the high pressure fuel pump also creates noise. Similarly, the opening of the outlet valve from the high pressure fuel pump also creates engine noise.
In the previously known direct injection engines, the opening of the fuel inlet valve to the fuel pump, the opening of the fuel outlet valve in the fuel pump, and the opening of the fuel injectors all occur at different crank angles of the engine crankshaft. For example, as shown in
Graphs 10-14 are illustrated as a function of the crank angle 16 of the engine crankshaft and the cam angle 18 of a multi-lobe or triangular cam used to drive the fuel pump plunger. Graph 19 illustrates the angle or position of the fuel pump plunger.
Graph 20 illustrates the total noise produced by the direct injection engine. As can be seen from graph 20, the total noise includes a separate noise peak corresponding to the fuel injector opening, the pump outlet valve opening, and the pump inlet valve opening. This noise, furthermore, is particularly noticeable to occupants of an automotive vehicle at low engine speeds, such as less than 1,000 rpm.
The present invention provides both a method and apparatus which reduces the engine noise of a direct injection engine, especially at low engine speeds.
In brief, the present invention includes a processor which receives an engine speed signal in any conventional fashion, such as from an engine speed sensor or a calculated engine speed from the engine ECU. Whenever the engine speed is greater than a predetermined threshold, e.g. 1,000 rpm, the processor takes no action to reduce engine noise. However, whenever the engine speed is less than the predetermined threshold, the processor output signals to update the cam phase of the high pressure fuel pump cam such that the opening of the fuel inlet valve or the fuel outlet valve coincides with the timing of the fuel injectors of the engine.
For example, in the preferred embodiment, the processor first obtains the crank angles of the high pressure fuel inlet valve opening or the fuel outlet valve opening. The processor then calculates the inverse angular frequency and then the masking threshold necessary to superimpose either the fuel inlet valve opening or the fuel outlet valve opening with the fuel injection timing. The processor then generates an output signal to update the cam phase of the fuel pump multi-lobe cam to superimpose either the fuel inlet valve opening or fuel outlet valve opening with the fuel injector opening.
By superimposing either the fuel pump inlet valve or the fuel pump outlet valve timing with the activation or opening of the fuel injectors at low engine speeds, the number of noise peaks from the engine is effectively reduced.
A better understanding of the present invention will be had upon reference to the following detailed description when read in conjunction with the accompanying drawing, wherein like reference characters refer to like parts throughout the several views, and in which:
With reference first to
The fuel system 21 includes a fuel pump 24 having a housing 26 which defines an internal pump chamber 28. An inlet valve 30 is fluidly connected in series between the pump chamber 28 and a fuel source 32, such as a fuel tank. Similarly, a fuel rail 34 is fluidly connected in series to the pump chamber 28 through a fuel pump outlet valve 36.
In a conventional fashion, a fuel injector 38 (only one illustrated) is associated with each cylinder in the direct injection engine 22. An engine control unit (ECU) also controls the activation or opening of the fuel injectors 38 in the conventional fashion.
Still referring to
In the conventional fashion, the reciprocation of the pump plunger 40 in its bore 42 inducts fuel into the fuel chamber 28 whenever the plunger 40 moves away from the pump chamber 28. During this time, fuel is inducted from the fuel tank 32, through the inlet valve 30, and into the pump chamber 28. Conversely, reciprocation of the pump plunger 40 in the opposite direction, i.e. towards the pump chamber 28, pumps fuel through the outlet valve 36 to the fuel rail 34 and ultimately to the fuel injectors 38.
With reference now to
The processor is programmed so that, whenever the engine speed is less than a predetermined threshold Trpm, the processor 50 generates an output to a fuel pump control 56. The fuel pump control then varies the angle of the fuel pump cam 44 so that the opening of either the fuel inlet valve 30 or the fuel outlet valve 36 coincides with the activation or opening of the fuel injectors 38.
With reference now to
At step 64, the processor 50 compares the actual engine speed with the low speed threshold Trpm. If the engine rotational speed is greater than the threshold Trpm, step 64 proceeds to step 66 and terminates the routine.
Conversely, whenever the engine rotational speed is less than the threshold Trpm, step 64 instead proceeds to step 66 where the processor 50 inputs the crank angle ω in radians, and also the pump inlet valve 30 opening angle or timing ωi. Step 66 also determines the fuel injection angle or timing ωf. Step 66 then proceeds to step 68.
At step 68, the processor calculates the inverse angular frequency (seconds/radians), i.e. in accordance with the following formula:
1/ω=60/(2π rpm)
Step 68 then proceeds to step 70.
At step 70, the difference between the fuel injection timing ωf and the inlet valve opening ωi is multiplied by the inverse angular frequency and compared to a masking threshold Tmask as follows:
1/ω|ωi−ωf|<Tmask
If less than the masking threshold, i.e. the difference between ωi and ωf is small and the inlet valve opening substantially coincides with the fuel injection timing, step 70 proceeds to step 67 and exits from the routine. Otherwise, step 70 proceeds to step 72 where the phase angle of the fuel pump cam 44 is updated by the processor 50 to superimpose the fuel pump inlet valve opening with the fuel injection timing by sending the appropriate signal to the fuel pump control 56 (
With reference now to
Whenever the engine rpm is less than the threshold Trpm, step 64 branches to step 80 in which the crank angle of the outlet valve opening ωo, rather than the inlet opening as in
Step 82 is identical to prior step 68 and calculates the inverse angular frequency ω of the engine. Step 82 then proceeds to step 84. At step 84, the difference between the fuel pump outlet valve opening timing and the fuel injection timing is multiplied by the inverse angular frequency and compared to the masking threshold Tmask in accordance with the following formula:
1/ω|φo−φf|<Tmask
If less than the masking threshold Tmask, indicative that the fuel pump outlet valve opening and the fuel injection opening are substantially superimposed with each other, step 84 proceeds to step 66 and exits to step 66.
Otherwise, step 84 proceeds to step 86 in which the processor 50 generates an output signal to the fuel pump control 56 (
With reference now to
More specifically, graph 90 illustrates the noise from the fuel injector timing. Graph 92 illustrates the noise from the pump outlet valve 36 while graph 94 illustrates the noise from the fuel pump inlet valve 30.
Unlike the prior art devices, however, the fuel pump plunger angle, shown at graph 96, is shifted from the position shown in phantom line and to the position shown in solid line. This shift, furthermore, corresponds to the phase shift of the multi-lobe cam phase shift illustrated in graph 98. This phase shift is also shifted, relative to the crank angle shown in graph 100, from the position shown in phantom line and to the position shown in solid line.
The net effect of the phase shift of the pump cam which results in a phase shift of the plunger angle superimposes the noise created by the inlet valve with the noise created by the fuel injectors as shown in graphs 94 and 90, respectively. This, in turn, effectively reduces the number of peaks on the overall noise, illustrated by graph 102, by three noise peaks per engine revolution for a six cylinder engine. In doing so, it reduces the overall noise sensation for occupants of a vehicle at low engine speeds.
The effect of flowchart 5 is essentially identical to that shown in
From the foregoing, it can be seen that the present invention provides an effective noise reduction method and apparatus for a direct injection engine, especially at low engine speeds. Having described our invention, however, many modifications thereto will become apparent to those skilled in the art to which it pertains without deviation from the spirit of the invention as defined by the scope of the appended claims.
Number | Name | Date | Kind |
---|---|---|---|
3709639 | Suda | Jan 1973 | A |
4476837 | Salzgeber | Oct 1984 | A |
4554634 | Shinoda | Nov 1985 | A |
4777921 | Miyaki et al. | Oct 1988 | A |
5201297 | Eblen et al. | Apr 1993 | A |
5592968 | Nakashima | Jan 1997 | A |
5697343 | Isozumi | Dec 1997 | A |
5771864 | Morishita et al. | Jun 1998 | A |
6142125 | Shimayama | Nov 2000 | A |
6314945 | Sugiyama et al. | Nov 2001 | B1 |
6378499 | Shimayama | Apr 2002 | B1 |
6694952 | Yamazaki | Feb 2004 | B1 |
6725837 | Hiraku | Apr 2004 | B2 |
6848477 | Treusch | Feb 2005 | B2 |
6901913 | Tsuchiya | Jun 2005 | B1 |
7063073 | Ausiello | Jun 2006 | B2 |
7198033 | Inaguma | Apr 2007 | B2 |
7198034 | Ausiello | Apr 2007 | B2 |
7373924 | Krengel | May 2008 | B1 |
7392793 | Hayakawa | Jul 2008 | B2 |
7406946 | Watanabe et al. | Aug 2008 | B1 |
7552720 | Borg | Jun 2009 | B2 |
7559313 | Tokuo | Jul 2009 | B2 |
7581519 | Hayase | Sep 2009 | B2 |
7789070 | Mouch | Sep 2010 | B2 |
7846597 | Yamagishi | Dec 2010 | B2 |
8015964 | Eddy | Sep 2011 | B2 |
8082904 | Ordanic | Dec 2011 | B2 |
8091530 | Surnilla | Jan 2012 | B2 |
8245693 | Surnilla | Aug 2012 | B2 |
8596051 | Malaney | Dec 2013 | B2 |
20020130287 | Smith | Sep 2002 | A1 |
20040168677 | Mashiki | Sep 2004 | A1 |
20050211224 | Inaguma et al. | Sep 2005 | A1 |
20060118089 | Tokuo | Jun 2006 | A1 |
20080098991 | Eddy | May 2008 | A1 |
20090025686 | Kato | Jan 2009 | A1 |
20090029226 | Yamagishi | Jan 2009 | A1 |
20090082939 | Iihoshi | Mar 2009 | A1 |
20090114191 | Pursifull | May 2009 | A1 |
20090139493 | Shafer | Jun 2009 | A1 |
20090241908 | Tokuo | Oct 2009 | A1 |
20100132798 | Malaney | Jun 2010 | A1 |
20100279193 | Yamagishi | Nov 2010 | A1 |
Number | Date | Country |
---|---|---|
06088557 | Mar 1994 | JP |
2002048023 | Feb 2002 | JP |
2006070880 | Mar 2006 | JP |
2008019755 | Jan 2008 | JP |
Number | Date | Country | |
---|---|---|---|
20120245826 A1 | Sep 2012 | US |