1. Field of the Invention
The present invention relates to a resonator for suppressing the intake noise of an intake system for a vehicle.
2. Related Art
A side branch resonator or a Helmholtz resonator has been used in the related art in order to suppress intake noise of an intake system. Such a related art resonator has a disadvantage that a larger installation space for a resonator is required in case the sound pressure of a lower frequency component with lower frequency of intake noise is to be suppressed.
For a side branch resonator, the natural frequency of sound that can be silenced by resonance depends on the length of the side branch. Meanwhile, the wavelength becomes longer as the signal component becomes lower. In order to suppress a low frequency component by using a side branch resonator, the side branch length must be increased. This increases the installation space for the resonator.
For a Helmholtz resonator, the natural frequency of sound that can be silenced by resonance is represented by the following expression:
In the above expression, f represents a natural frequency (resonance frequency), c a sound velocity, l the length of a communication pipe, V the volume of a cavity chamber, and S the cross-sectional area of the communication pipe. To suppress a low frequency component, it is necessary to reduce the natural frequency f. To reduce the natural frequency f, it is necessary to increase l or V with respect to S. In this case also, the installation space for the resonator is increased.
A resonator having a small installation space is described in JP-UM-A-2-080710. The resonator comprises an elastic film and a cup member. The cup member is attached to a surge tank with the cup opening turned down. Between the cup opening and the surge tank is interposed an elastic film. The elastic film separates the cup interior from the surge tank interior.
The natural frequency of the elastic film is set to be equal to the resonance frequency of columnar resonance in the surge tank. The resonator described in JP-UM-A-2-080710 is capable of suppressing columnar pulsation in the surge tank by way of the film vibration effect of the elastic film.
A problem with the resonator described in JP-UM-A-2-080710 is that it is difficult to maintain a desired sound pressure suppression effect for a substantial period of time. In other words, the natural frequency of an elastic film must be constantly maintained to be equal to the frequency of the resonance frequency of columnar resonance. The natural frequency of the elastic film depends on the tension of the elastic film. The tension of an elastic film gradually decreases with time from when the elastic film is installed. Thus, it is difficult for the resonator described in JP-UM-A-2-080710 to maintain a desired sound pressure suppression effect for a substantial period of time.
A resonator according to the invention has been accomplished in view of the above problems. An object of the invention is to provide a resonator having a small installation space that readily maintains a desired sound pressure suppression effect.
(1) In order to solve the problems, the invention provides a resonator arranged in an intake system comprising a pipe section for partitioning an intake port from an intake passage that communicates the intake port with a combustion chamber of an engine, the resonator comprising: a branch pipe having one end branching to the pipe section and another end closed so that a silencing chamber is defined therein; and at least one partitioning member for partitioning the silencing chamber into at least one pneumatic spring chamber, the partitioning member having a natural frequency lower than the frequency of silencing target sound of intake noise propagated from the intake passage.
The resonator according to the invention utilizes the mass effect of a partitioning member. In other words, resonance of a partitioning member and the air in the pneumatic spring chamber adjacent to the rear of the partitioning member is used to suppress the sound pressure of the frequency of the silencing target sound. Unlike the resonator described in JP-UM-A-2-080710, the inventive resonator does not utilize the film vibration effect. The term “rear” of the partitioning member herein refers to the side opposite to the side where intake noise is input as seen from the partitioning member.
Thus, the natural frequency of the partitioning member of the resonator according to the invention is set lower than the frequency of the silencing target sound of the intake noise. Even when the tension of the partitioning member is decreased and the natural frequency of the partitioning member lowered, the mass effect of the partitioning member is not degraded. The resonator according to the invention thus readily maintains a desired sound pressure suppression effect.
For the resonator according to the invention, the internal attenuation of the partitioning member itself produces unsharpened echo resonance (a portion where the sound pressure appearing on high frequencies or low frequencies of the resonance frequency is high). This makes it possible to reduce the sound pressure of echo resonance.
(2) The silencing chamber may comprise a communication pipe which directly communicates with the intake passage and to which the silencing target sound is propagated from the intake passage and a cavity chamber communicating with the communication pipe, the cavity chamber having a larger cross sectional area in vertical direction with respect to the propagation direction of the silencing target sound than that of the communication pipe, and the partitioning member may be arranged in the cavity chamber.
This configuration embodies the resonator according to the invention as a Helmholtz resonator. According to the configuration, it is possible to shift the natural frequency of a resonator toward lower frequencies than a Helmholtz resonator of the same shape. It is further possible to more compact resonator than a Helmholtz resonator to which the frequency of the same silencing target sound is set.
(3) The silencing chamber preferably comprises a communication pipe which directly communicates with the intake passage and to which the silencing target sound is propagated from the intake passage and a cavity chamber communicating with the communication pipe, the cavity chamber having a larger cross sectional area in vertical direction with respect to the propagation direction of the silencing target sound than that of the communication pipe, and the partitioning member is preferably arranged in the communication pipe.
The silencing effect of the resonator according to the invention depends on the volume of the cavity chamber, not on its shape. Thus, according to the invention, a resonator may be designed in any shape as long as its volume is kept constant. For example, the cavity chamber may be provided having a large width and small thickness. Thus adds to space saving. By tailoring the shape of the cavity chamber to the shape of the pipe section of the intake system, the freedom of arrangement of the resonator is dramatically enhanced.
(4) In this case, the communication pipe is preferably positioned inside the cavity chamber. By doing so, a projection is not formed outside the cavity chamber, which provides a lower-profile resonator design.
(5) Preferably, the natural frequency of the partitioning member is less than 10 percent of the resonance frequency of the resonance s less than 10 percent of the resonance frequency of the resonance sound calculated from the mass of the partitioning member and the spring constant of the pneumatic spring chamber with the latter being assumed as 100 percent. This is because the natural frequency of the resonator would otherwise be shifted toward higher frequencies by 10 percent or more with respect to the frequency of the silencing target sound.
(6) Preferably, the spring constant of the partitioning member is less than 1 percent assuming the spring constant of the pneumatic spring chamber adjacent to the rear of the partitioning member as 100 percent. This is because the spring effect would otherwise become non-negligible and the natural frequency of the resonator would be shifted toward higher frequencies by 10 percent or more with respect to the frequency of the silencing target sound.
(7) Preferably, the branch pipe is arranged at a site where the antinode of a standing wave of the silencing target sound of the intake noise is positioned in the pipe section. The antinode of a standing wave has a large sound pressure. With this configuration, it is possible to more efficiently lower the sound pressure of the silencing target sound.
According to the invention, it is possible to provide a resonator having a small installation space that readily maintains a desired sound pressure suppression effect.
Embodiments of the resonator according to the invention will be described below.
As shown in
As understood from the comparison between the related art resonator shown in
In this way, the partition walls of the resonator according to the embodiment are equivalent to the mass of the communication pipes of the related art Helmholtz resonator. Thus, the resonator according to the embodiment requires a smaller installation space.
First, the arrangement of the resonator according to the embodiment is described.
The mounting base part 20 is made of a resin and comprises a small diameter part 200 and a large diameter part 201. The small diameter part 200 has a cylindrical shape. At the opening end of the small diameter part 200 is formed a flange part 200a on the small diameter part. From the side wall of the intake duct 90 are protruded a flange part 901 on the duct. The flange part 200a on the small diameter part is fixed to the flange part 901 on the duct with a screw (not shown). Between the intake passage 95 and a pneumatic spring chamber 50 mentioned later is interposed a communication pipe 4. In other words, the intake passage 95 is in communication with the communication pipe 4. The large diameter part 201 has a shape of s cylinder having a larger diameter than the small diameter part. Inside the large diameter part 201 is partitioned a pneumatic spring chamber 50. At the opening end of the large diameter part 201 is formed a flange part 201a on the small diameter part.
The intermediate coupling part 21 is made of a resin and has a shape of a cylinder having the same diameter as the large diameter part 201. Inside the intermediate coupling part 21 is partitioned a pneumatic spring chamber 51. At both opening ends of the intermediate coupling part 21 are respectively formed flange parts 210, 211 on the intermediate coupling part. The flange part 210 on the intermediate coupling part is fixed to the flange part 201a on the large diameter part with a screw (not shown).
The diaphragm 30 is made of rubber and has a shape of a thin disc. The diaphragm 30 is sandwiched between and fixed to the flange part 210 on the intermediate coupling part and the flange part 201a on the small diameter part with the screw.
The intermediate coupling part 22 has a shape similar to that of the intermediate coupling part 21. Inside the intermediate coupling part 22 is partitioned a pneumatic spring chamber 52. At both opening ends of the intermediate coupling part 22 are respectively formed flange parts 220, 221 on the intermediate coupling part. The flange part 220 on the intermediate coupling part is fixed to the flange part 211 on the intermediate coupling part of the intermediate coupling part 21 with a screw (not shown).
The diaphragm 31 has a shape similar to that of the diaphragm 30. The diaphragm 31 is sandwiched between and fixed to the flange part 220 on the intermediate coupling part and the flange part 211 on the intermediate coupling part of the intermediate coupling part 21.
The intermediate coupling part 23 has a shape similar to that of the intermediate coupling part 22. Inside the intermediate coupling part 23 is partitioned a pneumatic spring chamber 53. At both opening ends of the intermediate coupling part 23 are respectively formed flange parts 230, 231 on the intermediate coupling part. The flange part 230 on the intermediate coupling part is fixed to the flange part 221 on the intermediate coupling part of the intermediate coupling part 22 with a screw (not shown).
The diaphragm 32 has a shape similar to that of the diaphragm 31. The diaphragm 32 is sandwiched between and fixed to the flange part 230 on the intermediate coupling part and the flange part 221 on the intermediate coupling part of the intermediate coupling part 22.
The end part 24 is made of a resin and has a shape of a cylinder with a bottom. Inside the end part 24 is partitioned a pneumatic spring chamber 54. At the opening end of the end part 24 is formed a flange part 240 on the end part. The flange part 240 on the end part is fixed to the flange part 231 on the intermediate coupling part with a screw (not shown).
The diaphragm 33 has a shape similar to that of the diaphragm 32. The diaphragm 33 is sandwiched between and fixed to the flange part 240 on the end part and the flange part 231 on the intermediate coupling part of the intermediate coupling part 23.
In this way, inside the branch pipe 2 are formed one communication pipe 4 and a total five pneumatic spring chambers 50 through 54. The five pneumatic spring chambers 50 through 54 are respectively partitioned by the diaphragms 30 through 33. The five pneumatic spring chambers 50 through 54 constitute the cavity chamber of the embodiment. The cavity chamber and the communication pipe 4 constitute the silencing chamber of the embodiment.
The embodiment of the resonator according to the invention has been described. Note that the invention is not limited to the above embodiment. A variety of modifications and adaptations will readily occur to those killed in the art.
While the resonator 1 is formed based on a Helmholtz resonator, the resonator may be formed in accordance with a side branch resonator. While the external shape of the resonator 1 is a cylinder in the embodiment, it maybe a prismatic cylinder. The number of diaphragms 30 through 33 is not particularly limited. For example, the number may be one. In this case, a single diaphragm may be interposed between the intake passage and the opening edge of the branch pipe. That is, a diaphragm may be used to seal the branch pipe. This partition walls a single pneumatic spring chamber in the branch pipe.
While diaphragms 30 through 33 are arranged as partition walls in the embodiment, a partition wall other than a diaphragm may be used as long as the partition wall has a natural frequency and a pneumatic spring chamber can be formed at the rear of the partition wall. For example, a block-shaped partition wall may be displaceably held in the branch pipe 2. While the diaphragms 30 through 33 are fixed with a screw, they may be fixed through bonding or welding. Or, the diaphragms 30 through 33 and part or entirety of the branch pipe 2 may be integrally formed. The position where the resonator 1 is attached to the intake system 9 is not particularly limited. For example, it may be attached via the air cleaner 91, the cleaner hose 92, the throttle body 93, or the intake manifold 94. A plurality of resonators 1 may be attached to a single intake system 9. In this case, the frequency of the silencing target sound may be changed per resonator 1.
The spring constant, density, thickness, mass or shape of the diaphragms 30 through 33 is not particularly limited. By decreasing the spring constant of the diaphragms 30 through 33, it is possible to decrease the natural frequency of the resonator 1. By increasing the mass, density or thickness of the diaphragms 30 through 33, it is possible to decrease the natural frequency of the resonator 1. The spacing between the diaphragms 30 through 33 is not particularly limited. By arranging the diaphragms 30 through 33 in close proximity to the communication pipe 4 with reduced spacing between them, it is possible to decrease the natural frequency of the resonator 1.
Measurement tests such as an acoustic excitation test and a numerical value test (transfer-matrix method) executed on the resonator of the embodiment will be described below.
The acoustic excitation test executed on the resonator 1 shown in
[Test sample]
The specifications of the resonator 1 shown in
[Test Method]
Next, the acoustic excitation test will be described. The acoustic excitation test uses a straight tubular pipe having an entire length of 0.6 m whose ends are open, a loudspeaker, and a microphone. To the side wall at the middle section of the straight tubular pipe branches the resonator 1. At one end of the straight tubular pipe is arranged the loudspeaker. At the other end of the straight tubular pipe is arranged the microphone. When while noise is output from the loudspeaker in this state, the white noise is propagated from one end to the other in the straight tubular pipe. The propagated sound is collected by the microphone.
[Test Result]
Next, the test result will be described.
As understood from
For a Helmholtz resonator having the same volume V of the cavity chamber, inner diameter D of the cavity chamber, axial length l of the communication pipe 4, and inner diameter d of the communication pipe 4 as Example 1, the resonance frequency f may be represented in the following expression, where (8/3p)×0.042 is an opening end correction.
From the above expression, the resonance frequency f is approximately 360 Hz. This calculation result reveals that arrangement of a diaphragm shifts the resonance frequency to lower frequencies.
Calculation result of the transfer-matrix method executed on the test samples shown below will be described.
[Test Sample]
Specifications of test samples will be described.
Example 2-1 shown in
Example 2-2 shown in
[Calculation Method]
Next, the calculation method will be described. Calculation is performed using the transfer-matrix method. That is, the intake system 9 is schematically represented as a series of conduit elements and the intake noise is treated as a one-dimensional factor. The transfer-matrix method is well known so that details of the method are omitted.
[Calculation Result]
Calculation result of the primary resonance frequency by the transfer-matrix method is shown in Table 1.
From the calculation result, it is understood that Example 2-1 shows a lower primary resonance frequency than Comparison Example 2-1 and Example 2-2 shows a lower primary resonance frequency than Comparison Example 2-2. This calculation result reveals that arrangement of a diaphragm shifts the resonance frequency to lower frequencies.
The acoustic excitation test executed on the following test samples will be described. The text method is as mentioned earlier so that its details are omitted.
[Test Sample]
Specifications of test samples will be described.
The volume V of the cavity chamber shown in Example 3-1 is 1.0 1 (liter). The inner diameter D of the cavity chamber is 94 mm. The axial length L of the cavity chamber is 144 mm. The axial lengths L1 through L3 of the pneumatic spring chambers 50a through 50c each is 24 mm. The axial length L4 of the pneumatic spring chamber 50d is 72 mm. The axial length l of the communication pipe 4 is 85 mm. The inner diameter d of the communication pipe 4 is 42 mm. The spring constant k of the diaphragms 30a through 30c is 13.8 N/m. The mass m of the diaphragms 30a through 30c is 3.26 g. The thickness t of the diaphragms 30a through 30c is 0.5 mm.
The volume V of the cavity chamber shown in Example 3-2 is 1.0 1 (liter). The inner diameter D of the cavity chamber is 94 mm. The axial length L of the cavity chamber is 144 mm. The axial lengths L1 through L6 of the pneumatic spring chambers 50a through 50f are respectively 24 mm. The axial length l of the communication pipe 4 is 85 mm. The inner diameter d of the communication pipe 4 is 42 mm. The spring constant k of the diaphragms 30a through 30e is 13.8 N/m. The mass m of the diaphragms 30a through 30e is 3.26 g. The thickness t of the diaphragms 30a through 30e is 0.5 mm.
Comparison Example 3-1 shows a case where a resonator is not arranged in the straight tubular pipe used for the acoustic excitation test. The volume V of the cavity chamber shown in Comparison Example 3-2 is 1.0 1 (liter). The inner diameter D of the cavity chamber is 94 mm. The axial length L of the cavity chamber is 144 mm. The axial length l of the communication pipe 4 is 185 mm. The inner diameter d of the communication pipe 4 is 42 mm.
[Test Result]
Next, the test result will be described.
From
It is understood that secondary resonance occurs near 440 Hz in Example 3-1. Similarly, it is understood that secondary resonance occurs near 380 Hz in Example 3-2. Such secondary resonance occurs because a diaphragm has been arranged, or in other words, the freedom of the resonator has increased. For the secondary resonance also, it is possible to suppress the sound pressure of the intake noise. As understood from the comparison between Example 3-1 and Example 3-2, increasing the number of diaphragms shifts the secondary resonance frequency toward lower frequencies (indicated by an arrow in the drawing).
Text result of the transfer-matrix method executed on the following test samples will be described. The calculation method is as mentioned earlier so that its details are omitted.
[Test Sample]
Specifications of test samples will be described. The test samples used in Example 4 are same as those used in Example 3. The specifications of Example 4-1 is the same as Example 3-1, the specifications of Example 4-2 is the same as Example 3-2, the specifications of Comparison Example 4-1 is the same as Comparison Example 3-1, and the specifications of Comparison Example 4-2 is the same as Comparison Example 3-2.
[Calculation Result]
Next, the calculation result will be described.
From
It is understood that secondary resonance occurs near 440 Hz in Example 4-1. Similarly, it is understood that secondary resonance occurs near 380 Hz in Example 4-2. Such secondary resonance occurs because a diaphragm has been arranged, or in other words, the freedom of the resonator has increased. For the secondary resonance also, it is possible to suppress the sound pressure of the intake noise. As understood from the comparison between Example 4-1 and Example 4-2, increasing the number of diaphragms shifts the secondary resonance frequency toward lower frequencies (indicated by an arrow in the drawing).
Text result of the transfer-matrix method executed on the following test samples will be described. The calculation method is as mentioned earlier so that its details are omitted.
[Test Sample]
Specifications of test samples will be described. In Example 5, the spacing between the diaphragms 30a through 30e shown in Example 3-2 (refer to
[Calculation result]
Next, the calculation result will be described.
From the calculation result, it is understood that the primary resonance frequency shown in Example 5-1 is 100 Hz. As mentioned earlier, the primary resonance frequency shown in Example 4-2 (calculation result of Example 3-2) is approximately 130 Hz (refer to
From the calculation result, it is understood that the primary resonance frequency shown in Example 5-2 is 80 Hz. That is, it is understood that increasing the thickness of the diaphragms 30a through 30e shifts the natural frequency of the resonator 1 toward lower frequencies.
Result of the test executed on the test samples shown below will be described.
[Test Sample]
Specifications of test samples will be described.
The communication pipe 4 has a shape of a cylinder 80 mm in inner diameter and 20 mm in length. One end of the communication pipe 4 is in communication with the air cleaner 91 and extends inside the cavity chamber 40. The other end of the communication pipe 4 is open in the cavity chamber 40. The cavity chamber 40 is formed in a box whose inner dimensions are 260 mm by 120 mm by 32 mm. The volume V of the cavity chamber excluding the volume of the communication pipe 4 (0.1 liters) is 0.88 liters.
The diaphragms 30 through 32 each is made of a rubber film 0.5 mm in thickness, that constitutes a partitioning member of the invention, and held in the communication pipe 4 with spacing of 10 mm. The diaphragms 30 through 32 each has a mass of 2.36 g, Young's modulus of 1.64 MPa (300 Hz), and Poisson'S ratio of 0.5.
[Test Method]
The resonator 4 is attached to the air cleaner 91 of a 4-cylinder engine. A microphone is arranged at the intake port. The sound pressure of the secondary rotation component obtained at each engine revolutions is measured.
Next, the test result will be described below.
As shown in
The resonator according to this embodiment has a cavity chamber whose thickness as thin as approximately 30 mm. Mounting the resonator on an air cleaner does not provide a bulky configuration, which is advantageous in terms of space saving. As shown in
For the resonator according to Embodiment 6, the air inside the cavity chamber 40 is inflated/contracted due to a change in the temperature of outside air, which exerts an excessive pressure on the diaphragms 30 through 32. In this case, as shown in
An intake system to an engine is shown in Example 7, in which a resonator 71 according to one embodiment of the invention is disposed.
Basic structure of this intake system will be described with
As shown in
In the resonator 71, as shown in
Incidentally, as shown in
[Test Sample]
The intake system in which the resonator 71 is mounted as shown in
Specifications of the resonator 71 will be described. The volume of the resonator 71 is 2.2 l(liters). The inner diameter D of the communication portion 77 is 80 mm. Each of the films 77a, 77b has a thickness of 0.5 mm and disposed at a distance of 20 mm to each other. The films 77a, 77b each has a mass of 2.36 g, Young's modulus of 1.64 MPa (300 Hz), and Poisson'S ratio of 0.5. The resonance frequency of the resonator 71 is 85 Hz.
For comparison, data obtained without using a silencer is served as Comparison Example 7-1. Data obtained using, as an intake pipe, a Helmholtz resonator comprising a communication pipe 27 mm in diameter and 76 mm in length is shown as Comparison Example 7-2. In Comparison Example 7-2, the communication pipe is provided for communication between the resonator 71 and the air cleaner 72 in place of the communication portion 77 such that both ends of the communication pipe project into the air cleaner case and the resonator, respectively.
[Test Method]
Actual measurement tests similar to Example 6 are conducted to Example 7-1, Comparative Examples 7-1 and 7-2. The sound pressure of the primary explosion component obtained at each engine revolutions is measured.
[Test Result]
Next, the test result will be described below.
As shown in
Number | Date | Country | Kind |
---|---|---|---|
2004-284651 | Sep 2004 | JP | national |
2005-136037 | May 2005 | JP | national |
P2004-192619 | Sep 2004 | JP | national |