Intake noise reducing device for internal combustion engine

Information

  • Patent Grant
  • 6450141
  • Patent Number
    6,450,141
  • Date Filed
    Wednesday, July 1, 1998
    26 years ago
  • Date Issued
    Tuesday, September 17, 2002
    22 years ago
Abstract
A continuous partition wall is formed in the air introducing duct. The air introducing duct has a length L. The partition wall has a length equal to or greater than L/2. The partition wall divides the air introducing duct into first and second sections. A resonance silencer and a connecting duct are connected to the first section. A connecting position of the resonance silencer and the connecting duct is set such that the connecting position is fully included within a partition wall positioned range. A valve is arranged in the second section. Thus, intake noises is decreased in a wide range from a low frequency about 40 Hz to an intermediate frequency about several hundred Hz, which is normally hearable.
Description




The content of Application No. TOKUGANHEI 9-178495 filed Jul. 3, 1997, in Japan is hereby incorporated by reference.




BACKGROUND OF THE INVENTION




The present invention relates to a noise reducing device for an internal combustion engine of an automobile, etc., and particularly relates to an intake noise reducing device capable of improving comfortableness by reducing noises of an intake system.




In a related intake system, an air introducing duct is divided into two sections and a valve is attached to one duct of the sections. The valve is opened and closed in accordance with a change of engine speed, etc. (See Japanese Laid-Open Patent Nos. 3-290052 and 4-8861.)




SUMMARY OF THE INVENTION




In one of the above related intake systems, a resonance silencer is formed by closing the valve in low speed rotation so that silencing effects with respect to a specific frequency are obtained (see Japanese Laid-Open Patent No. 3-290052). In the other, duct resonance from 200 to 300 Hz is reduced by a side branch (Japanese Laid-Open Patent No. 4-8861). Therefore, it is difficult to sufficiently reduce noises in a wide frequency range from a lower frequency.




The present invention is achieved with such points in view. It therefore is an object of the present invention is to provide an intake noise reducing device for an internal combustion engine capable of silencing noises in a wide range from a low frequency to an intermediate frequency, which is normally hearable by a human being.




An intake noise reducing device for an internal combustion engine in the present invention has a duct, a partition wall, a silencer, a connecting duct and a valve. The duct introduces air into an internal combustion engine and has a length L. The partition wall is arranged within the duct to divide into first and second sections and has a length equal to or greater than L/2. The connecting duct connects the first section and the silencer. A connecting position of the connecting duct to the duct is in opposite to the partition wall. The valve opens and closes the second section.




In the above construction, for low engine loads, the valve of the second section is closed. As a result, the silencing effects are increased in a frequency area from low to high. Accordingly, silencing performance is greatly improved over a wide range of frequency and the intake noises are greatly reduced and quietness is improved in an ordinary low load driving condition in which operating frequency is high.




For high engine loads, the valve of the second section is opened. As a result, a required engine output is secured and excellent silencing performance is exhibited in comparison with a conventional structure having no partition wall.




Accordingly, silencing performance is greatly improved over a wide range of frequency and intake noises are greatly reduced.











BRIEF DESCRIPTION OF THE DRAWING





FIG. 1

is a plan view of an engine room showing a first embodiment of the present invention.





FIG. 2

is a cross-sectional view showing an intake noise reducing device in the first embodiment.





FIG. 3

is a perspective view showing an air introducing duct in the first embodiment.





FIG. 4

is a cross-sectional view of the air introducing duct in the first embodiment.





FIG. 5

is a graph showing silencing characteristic data in the first embodiment.





FIG. 6

is a cross-sectional view showing a structure in which a partition wall is offset to a base end of the air introducing duct for investigating a change in silencing characteristics as a length of the partition wall and a position of a connecting duct are changed.





FIG. 7

is a graph showing silencing characteristics of the air introducing duct of FIG.


6


.





FIG. 8

is a cross-sectional view showing a structure in which a partition wall is arranged in an intermediate position of the air introducing duct.





FIG. 9

is a graph showing silencing characteristics of the air introducing duct of FIG.


8


.





FIG. 10

is a cross-sectional view showing a structure in which the partition wall is offset to a front end of the air introducing duct.





FIG. 11

is a graph showing silencing characteristics of the air introducing duct of FIG.


10


.





FIG. 12

is a table for explaining improvements of silencing effects with respect to frequencies.





FIG. 13

is a view for comparing the silencing effects summarized in the position of the connecting duct.





FIG. 14

is a cross-sectional view of an air introducing duct in a second embodiment of the present invention.





FIG. 15

is a cross-sectional view showing an intake noise reducing device in a third embodiment of the present invention.





FIG. 16

is a cross-sectional view showing an intake noise reducing device in a fourth embodiment of the present invention.





FIG. 17

is a graph showing a proximity noise level when the intake noise reducing device in the fourth embodiment is mounted to an automobile.





FIG. 18

is a cross-sectional view showing an intake noise reducing device in a fifth embodiment of the present invention.





FIG. 19

is a cross-sectional view showing an intake noise reducing device in a sixth embodiment of the present invention.











DESCRIPTION OF THE PREFERRED EMBODIMENTS




The preferred embodiments of the invention is described next. In the following explanation, equivalent members are designated by the same reference characters, and only different members are designated by different reference characters. Further, upwardness and downwardness in the explanation correspond to directions in the drawings.





FIGS. 1

to


5


are views showing an intake noise reducing device in a first embodiment of the invention.




A whole structure of the intake noise reducing device is explained with reference to FIG.


1


.




An engine


8


, an intake-air collector


9


, an air cleaner


10


, a clean side duct


11


, an air introducing duct


12


, a resonance silencer


14


, and a vacuum actuator


19


, etc. are arranged within an engine room


30


of an automobile. The intake-air collector


9


and the air cleaner


10


are connected to each other via the clean side duct


11


. The air introducing duct


12


extends forward from the air cleaner


10


.




A structure of the air introducing duct


12


is explained with reference to

FIGS. 2

to


4


.




The air introducing duct


12


has a length L. A partition wall


16


is formed within the air introducing duct


12


. The partition wall


16


has the length L and extends from a front end


13


of the air introducing duct


12


to a base end


17


thereof. The partition wall


16


divides the air introducing duct


12


into a first section


31


on a lower side and a second section


32


on an upper side. A butterfly valve


18


is arranged to the second section


32


at the front end


13


. The vacuum actuator


19


operates the valve


18


to close the second section


32


when the load on the engine


8


is low and to open when the load is high.

FIG. 4

shows a sectional shape of a position including the partition wall


16


of the air introducing duct


12


. The air introducing duct


12


is constructed by two parts


12




a


,


12




b


on left and right sides in the FIG.


4


. The air introducing duct


12


is entirely formed in the shape of a number “8” in section such that each of the first and sections


31


,


32


has a substantially oval-shaped cross-section. The partition wall


16


is formed by central joining members


16




a


,


16




b


of the parts


12




a


,


12




b.






The resonance silencer


14


is connected to the first section


31


via a connecting duct


15


in a position about 2L/5 apart from the front end


13


. Accordingly, an connecting position of the connecting duct


15


to the air introducing duct


12


fully included within an arranging range of the partition wall


16


.




The above construction is used because it has become clear, as a result of a silencing characteristic measuring experiment in a structure changed with the length of the partition wall


16


as a parameter, that the length of the partition wall


16


must be equal to or greater than L/2 to obtain silencing effects greatly at a low frequency equal to or smaller than 100 Hz. Further, the above construction is used because it has become clear that the connecting position of the connecting duct


15


to the resonance silencer


14


must be in opposite to the partition wall


16


.




An operation of the intake noise reducing device in the first embodiment is explained next.




For low engine loads, intake air amount is small and an intake air resistance is small. Thus, the second section


32


does not need intake air, so the valve


18


is closed by the vacuum actuator


19


. Therefore, the air introducing duct


12


becomes equivalent to a duct having reduced cross-sectional area. Consequently, silencing characteristics at a low frequency obtained by the air cleaner


10


are improved and the silencing effects are increased in a frequency area from a low frequency about 40 Hz to a high frequency. Further, the connecting position of the connecting duct


15


to the air introducing duct


12


is fully included within the arranging range of the partition wall


16


so that the connecting duct


15


is connected to the first section


31


having reduced cross-sectional area. Therefore, the intake noise reducing device attains a state equivalent to a state in which air flows from a duct having a small diameter into the connecting duct. As a result, effects of the resonance silencer


14


are improved and silencing effects are simultaneously greatly increased in an frequency area equal to or higher than a resonance frequency, e.g., in a frequency equal to or higher than 80 Hz. By these two actions, intake noises from a low frequency to an intermediate frequency as a possibility of causes of confined sounds within a vehicle room are effectively reduced.





FIG. 5

shows results of silencing performance as an intake system obtained by applying this embodiment to the intake system of a front-wheel-drive 2000 cc class vehicle. In

FIG. 5

, high performance is expressed by high silencing amount revel.

FIG. 5

shows frequencies up to 200 Hz. However, it is actually confirmed that the silencing performance is greatly improved up to 250 Hz and is also greatly improved in a frequency range from 300 Hz to 500 Hz.




Accordingly, the silencing amount is increased equal to or greater than 10 dB in a frequency range from a lower level near 40 Hz.




In contrast to this, for high engine loads, intake air amount is large, so the second section


32


needs intake air. It is particularly necessary to reduce a intake resistance in a high speed rotating area of the engine


8


. Accordingly, the valve


18


is opened in a high load with the intake air amount, the engine speed, etc. as a judging standard. Thus, air also flows into the second section


32


so that the intake resistance is reduced and the engine


8


generates a sufficient output.




With respect to the intake noises, a phase difference between sounds propagated in the first and second section


31


,


32


is caused. Thus, slight noise reducing effects are provided on a lower frequency side than a design frequency of the resonance silencer


14


and effects of a frequency shift equivalent to an increase in volume of a resonance chamber are provided. As a result, a degree of freedom of a silencer arrangement is increased within an engine room


30


having a limited space and excellent silencing performance is exhibited in comparison with a conventional structure having no partition wall.




An experiment made to decide a preferable length of the partition wall and an connecting range of the connecting duct is explained by referring

FIGS. 6

to


13


. Similar members is explained by using the same reference characters even when lengths and positions of these characters are respectively different from each other.





FIG. 6

shows an air introducing duct


3


of a first example. In the first example, a partition wall starting point is set to a base end


1


on an air cleaner side. An entire length L of the air introducing duct


3


is set to 300 mm. The air introducing duct


3


is set to 76 mm in height H and 40 mm in width D. A connecting duct


7


is set to 50 mm in length La and a distance Lb from a front end


4


of the air introducing duct


3


to a center of the connecting duct


7


is set to 100 mm. The air introducing duct


3


is separated into a first section


31


and a second section


32


by the partition wall


2


. A resonance silencer


6


is arranged in the first section


31


through the connecting duct


7


. The second section


32


is closed by a closing member


5


arranged in the second section


32


and offset to the front end


4


.




The experiment is made with respect to three kinds of lengths X of the partition wall


2


, 75 mm (L/4), 150 mm (L/2) and 225 mm (3L/4). In

FIG. 7

, Nos. (2), (3) and (4) respectively show experimental results of X=75 mm, 150 mm and 225 mm. When the length X of the partition wall


2


is 75 mm and 150 mm, no partition wall


2


reaches the connecting duct


7


of the resonance silencer


6


. When the length X of the partition wall


2


is 225 mm, a connecting position of the connecting duct


7


is fully included in a partition wall positioned range.





FIG. 8

shows a second example. In the second example, the partition wall


2


is formed in an intermediate range including a connecting position of the connecting duct


7


. An experiment of the second example is made with respect to three kinds of lengths X of the partition wall


2


, 75 mm, 150 mm and 225 mm. In

FIG. 9

, Nos. (5), (6) and (7) respectively show experimental results of X=75 mm, 150 mm and 225 mm. In this case, each the connecting positions of the connecting ducts


7


is fully included in a partition wall positioned range.





FIG. 10

shows a third example. In the third example, a partition wall starting point is set to a front end


4


of an air introducing duct


3


. An experiment of the third example is made with respect to three kinds of lengths X of the partition wall


2


, 75 mm, 150 mm and 225 mm. In

FIG. 11

, Nos. (8), (9) and (10) respectively show experimental results of X=75 mm, 150 mm and 225 mm. When the length X of the partition wall


2


is 75 mm, no partition wall


2


reaches the connecting range of a connecting duct


7


. When the length X of the partition wall


2


is 150 mm and 225 mm, each the connecting positions of the connecting ducts


7


is fully included in a partition wall positioned range.




The experimental results are shown in the graphs of

FIGS. 7

,


9


and


11


. In these graphs, No. (1) is a silencing characteristic comparing example. In the comparing example, an air introducing duct has the same basic size as each of the above examples and has no partition wall (X=0 mm). From these graphs, it should be understood that silencing performance is greatly changed in a wide range including three frequency areas in which an internal sound of the vehicle tends to be caused. These performance differences are summarized in the table of

FIG. 12

with respect to three noted frequencies.




In

FIG. 12

, values express the amount of the silence effects, the circled values show the better performance. Range of the connecting duct


7


of the circled values are within a partition wall positioned range. So it is effective to layout the connecting duct


7


facing to the partition wall


2


.





FIG. 13

shows a graph in which the connecting position of the connecting duct


7


is shown on the abscissa and a silencing effect improvement amount is shown on the ordinate. From

FIG. 13

, high silencing effects are shown in a condition in which the length of the partition wall


2


is equal to or longer than L/2 and the connecting position of the connecting duct


7


is fully included within the partition wall positioned range. An average improving amount of the silencing effects in a way satisfying the condition is about 9.5 dB and is therefore very high. In contrast to this, the average improving amount of the silencing effects is about 4.4 dB and is therefore not so high in a way in which the length of the partition wall


2


is L/4 or the connecting position of the connecting duct


7


is partially or fully departed from the partition wall positioned range.




Accordingly, it is necessary to greatly improve the silencing effects that the length of the partition wall


2


is set to be equal to or greater than a length half the entire length L of the air introducing duct


3


and the connecting position of the connecting duct


7


is fully included in the partition wall positioned range.




As explained above, in accordance with the embodiment, by closing the valve


18


of the second section


32


in driving conditions resulting from a constant speed or a slow acceleration of a low load in which driving frequency is high and a continuous time is long, silencing effects of the air cleaner


10


and the resonance silencer


14


at low and intermediate frequencies are improved, intake noises are greatly reduced and comfortableness is improved. Further, by opening the valve


18


of the second section


32


in high load conditions resulting from a sudden acceleration, an ascent, etc, the intake resistance of an intake system is reduced and a required engine output is secured. Accordingly, quietness is improved and the engine output is secured in accordance with the driving conditions. Further, great silencing effects are obtained in a low frequency area equal to or lower than 100 Hz since the length of the partition wall


16


is set to be equal to or longer than L/2 with respect to the length L of the air introducing duct


12


.





FIG. 14

is a view showing a second embodiment of the invention. In the second embodiment, an air introducing duct


20


has a substantially oval-shaped cross-section and a partition wall


21


having a flat plate shape is arranged at a center of the air introducing duct


20


. The air introducing duct


20


is formed by two parts


20




a


,


20




b


divided on left and right sides in FIG.


14


. Accordingly, the same cross-sectional area as the first embodiment can be attained by smaller space than the first embodiment.





FIG. 15

is a view showing a third embodiment of the invention. In the third embodiment, a partition wall


16


has a length similar to that in the first embodiment. However, in contrast to the first embodiment, an valve


18


is arranged at a base end


17


of a air introducing duct


22


. In accordance with the third embodiment, no parts of the valve


18


are influenced by rainwater, etc. and durability is excellent as merits in comparison with a case in which the valve


18


is arranged at a front end


13


of the air introducing duct


22


. Further, a space within the air cleaner


10


is utilized in the attachment of the valve


18


so that the valve


18


is stored in the same space as a conventional intake structure having no partition wall. Therefore, it is possible to embody the third embodiment without causing a great change in layout within an engine room, etc.





FIGS. 16 and 17

are views showing a fourth embodiment of the invention. In the fourth embodiment, a partition wall


24


has about 3L/4 in length. A partition wall starting point is set to a front end


13


of an air introducing duct


23


. A valve


18


is offset to the front end


13


.




In accordance with the fourth embodiment, there is no partition wall


24


in a portion near a base end


17


of the air introducing duct


23


. Thus, an inserting structure of the base end


17


and a projecting member


25


on an air cleaner


10


is easily formed by increasing a diameter of the base end


17


.





FIG. 17

shows measured results of a proximity sound near the front end


13


of the air introducing duct


23


within the engine room on which an intake noise reducing device in the fourth embodiment is mounted. These data are resultantly obtained by controlling an operation of the intake noise reducing device such that the valve


18


is opened at an engine speed equal to or greater than 4000 rpm. From

FIG. 17

, it is understood in comparison with a conventional structure having no partition wall that the intake noises of secondary components of the engine rotation are greatly reduced in a wide range equal to or smaller than 4000 rpm.





FIG. 18

is a view showing a fifth embodiment of the invention. In the fifth embodiment, a partition wall


27


has about 3L/4 in length. A partition wall starting point is set to a base end


17


of an air introducing duct


26


. A valve


18


is arranged at the base end


17


. A connecting duct


15


of a resonance silencer


14


is offset to the base end


17


.




The fifth embodiment is suitable for a case in which a position of the resonance silencer


14


is relatively offset to an air cleaner in view of layout within the engine room. Silencing performance on a low frequency side is slightly excellent as peculiar effects obtained by offsetting the resonance silencer


14


to the air cleaner.





FIG. 19

is a view showing a sixth embodiment of the invention. In the sixth embodiment, a partition wall


29


having L/2 in length is formed from a position L/4 apart from a front end


13


of an air introducing duct


28


to a position L/4 apart from a base end


17


thereof. A connecting position of a connecting duct


15


to the air introducing duct


28


is opposite to an intermediate position of the partition wall


29


. In accordance with the sixth embodiment, reliable silencing performance is obtained at a minimum length (L/2). Further, the connecting position of the connecting duct


15




14


is easily included within a partition wall positioned range even when the length of the partition wall


29


is short.




In each of the above embodiments, each of cross-sectional area ratios of the first and second sections


31


,


32


is set to 50%, but there is a case in which these ratios are changed in accordance with the concept of an automobile. The cross-sectional area ratios of the first and sections


31


,


32


are changed in accordance with required performance about quietness or maximum horsepower, etc. Thus, in a low load condition, intale noise level is required very very low, the sectional ratio of the first section


31


is set to be small such as about 30%. In contrast, in the case of an automobile having characteristics for securing its output in the low load condition to a certain extent, the sectional ratio of the first section


31


is set to be large such as about 70%. Thus, quietness in intake noises is suitably improved and the engine output is suitably secured in accordance with the characteristics of the automobile.



Claims
  • 1. An intake noise reducing device for an internal combustion engine, comprising:an air introducing duct into an internal combustion engine, the duct having a length L; a partition wall in the duct dividing into first and second sections, the partition wall having a length equal to or greater than L/2; a silencer; a connecting duct connecting the first section and the silencer, a connecting position of the connecting duct to the duct being in opposite to the partition wall; and a valve opening and closing the second section.
  • 2. The intake noise reducing device according to claim 1, whereinthe duct includes one end connected to the engine, the partition wall extends from the one end of the duct, and the valve is offset to the one end of the duct.
  • 3. The intake noise reducing device according to claim 1, whereinthe duct includes one end connected to the engine, and the one end of the duct is disposed out of the partition wall.
  • 4. The intake noise reducing device according to claim 3, whereinthe other end of the duct is disposed out of the partition wall.
  • 5. The intake noise reducing device according to claim 1, whereinthe duct includes one end connected to the engine, and the connecting position of the connecting duct to the duct is offset to the one end of the duct.
  • 6. The intake noise reducing device according to claim 1, whereinthe duct comprises first and second members, a contact portion between the first and second members extends along an axial direction of the duct, the first and second members have first and second joining members being in contact with each other, and the partition wall is included in the first and second joining members.
  • 7. The intake noise reducing device according to claim 1, whereinthe duct comprises first and second members, a contact portion between the first and second members extends along an axial direction of the duct, and the partition wall is projected from at least one of the first and second members.
  • 8. The intake noise reducing device according to claim 1, whereinthe duct has a substantially oval-shaped cross-section, the partition wall is arranged at a center of the duct.
  • 9. The intake noise reducing device according to claim 1, whereinthe engine includes an air cleaner connected to one end of the duct, the partition wall dividing a predetermined interval within the duct into the first and second sections, the first and second sections connect an upstream and a downstream of the predetermined interval in parallel, and the connecting position of the connecting duct to the duct is included in the predetermined interval.
  • 10. The intake noise reducing device according to claim 9, whereinthe partition wall extends from the one end of the duct, and the valve is offset to the one end of the duct.
  • 11. The intake noise reducing device according to claim 9, whereinthe one end of the duct is disposed out of the predetermined interval.
  • 12. The intake noise reducing device according to claim 11, whereinthe other end of the duct is disposed out of the predetermined interval.
  • 13. The intake noise reducing device according to claim 9, whereinthe connecting position of the connecting duct to the duct is offset to the one end of the duct.
  • 14. The intake noise reducing device according to claim 9, whereinthe predetermined interval has a length equal to or greater than L/2.
  • 15. The intake noise reducing device according to claim 1, whereinthe silencer is a resonance type.
  • 16. An intake noise reducing device for an internal combustion engine, comprising:air introducing means for introducing air into an internal combustion engine, the introducing means having a length L; partitioning means in the introducing means for dividing into first and second sections, the partition means having a length equal to or greater than L/2; a silencer; connecting means for connecting the first section and the silencer, a connecting position of the connecting means to air introducing means being in opposite to the partitioning means; and opening-closing means for opening and closing the second section.
  • 17. An automobile, comprising:an internal combustion engine; a air introducing duct into the engine, the duct having a length L; a partition wall in the duct dividing into first and second sections, the wall having a length equal to or greater than L/2; a silencer; a connecting duct connecting the first section and the silencer, a connecting position of the connecting duct to the duct being in opposite to the partition wall; and a valve opening and closing the second section.
Priority Claims (1)
Number Date Country Kind
9-178495 Jul 1997 JP
Foreign Referenced Citations (8)
Number Date Country
03290052 Dec 1991 JP
3-290052 Dec 1991 JP
4-8861 Jan 1992 JP
04008861 Jan 1992 JP
06123260 May 1994 JP
07042638 Feb 1995 JP
08158970 Jun 1996 JP
09004529 Jan 1997 JP