JP2007205327A - Variable frequency silencing system - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a simply formed variable frequency silencing system which improves silencing effects on both peak noise (noise of frequencies with primary components) and noise of the frequencies with components of its integral multiple, and noise of the other frequencies (noise of frequencies with 0.5th components and noise of frequencies with 1.5th components), and which, even if the frequencies of the noise are changed, provides silencing effects according to that change. <P>SOLUTION: A movable sleeve 4 having openings B1, B2 with different shapes is slidably inserted into an intake pipe 1. The movable sleeve 4 is slid according to the rotational speed of an engine to change the communication area between the internal space of the intake pipe 1 and each of the resonator chambers 21a, 31a of resonators 2, 3 at a predetermined rate. Thus, the frequencies of noise to be silenced by each variable resonator are simultaneously changed by one actuator. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention is represented by, for example, a silencer system that is provided in an intake system of an automobile engine and reduces intake noise, and relates to a variable frequency silencer system that can change the frequency of noise that can be reduced. In particular, the present invention relates to an improvement of a silencing system that can exert a silencing effect on noises of a plurality of types of frequencies.

  2. Description of the Related Art Conventionally, for example, a technique of providing a resonator that suppresses noise (intake sound) generated in an intake pipe is known as a noise countermeasure for an automobile engine. This type of resonator generally functions as a silencer that reduces noise at a specific frequency by using Helmholtz's resonance principle.

  Specifically, the resonator includes a resonator body having a resonator chamber having a relatively large capacity, and a communication pipe that communicates the resonator body with the intake pipe. In this configuration, if the length of the communication pipe is L, the passage area inside the communication pipe (passage area in the direction orthogonal to the extension direction of the communication pipe) is S, the volume of the resonator chamber is V, and the speed of sound is c, The noise of the frequency f represented by the following formula (1) can be reduced.

f = (c / 2π) × (S / (L × V)) ^1/2 (1)
In the intake pipe, intake sounds of various frequencies are generated, and the expression (1) is adapted to the peak frequency of the intake sound (the frequency having the highest noise level (hereinafter, this frequency is referred to as a primary component)). If the above L, S, and V are designed, it is possible to reduce the noise of the primary component and the integral multiples thereof (secondary component, tertiary component, etc.) For example, an intake air having a frequency of 200 Hz. If the above L, S, and V are designed so that the above equation (1) is adapted to this frequency in a situation where the sound noise level is the highest, not only this 200 Hz intake sound but also 400 Hz or 600 Hz intake air Sound can also be reduced.

  However, if only one fixed resonator having a constant L, S, and V is provided, only the intake sound of each frequency of the primary component and its integral multiple component generated at a specific engine speed can be reduced.

  Therefore, as a technique for taking measures against noise at frequencies other than these, for example, as disclosed in Patent Document 1 and Patent Document 2 below, a plurality of types of resonators in which at least one of L, S, and V is different are provided. It is known to do. According to this, not only the intake sound of the frequency of the primary component and its integral multiple component, but also other frequencies (for example, the 0.5th-order component which is half the frequency of the primary component and the primary component) A silencing effect can also be obtained with respect to the intake sound of the 1.5th-order component that is a frequency intermediate to the secondary component. For example, it is possible to reduce the intake sound having a frequency of 200 Hz, 400 Hz, and 600 Hz with one resonator, and to reduce the intake sound having a frequency of 100 Hz, 300 Hz, and 500 Hz with the other resonator.

  On the other hand, since the engine speed of a car engine changes according to the driving situation of the car, the intake air flow velocity etc. change accordingly, and the frequency of the intake sound also changes. That is, the frequency of the noise peak frequency (the first-order component) and the integral multiple components (second-order component, third-order component, etc.) in the intake pipe also change according to the engine speed.

As a technique for coping with the fluctuation of the frequency of the primary component and the frequency of the integral multiple component thereof, a variable resonator disclosed in the following Patent Document 3 has been proposed. This variable resonator can change any one of the above L, S, and V. That is, at least one of the above L, S, and V is made variable by a drive source such as an actuator, and the actuator is operated in accordance with a change in the engine speed to change the resonance frequency of the resonator. The noise of the frequency of the primary component and the integral multiple component thereof can be reduced.
Japanese Utility Model Publication No. 58-35666 Japanese Patent Laid-Open No. 60-30463 JP 2005-256663 A

  However, if a conventional variable resonator is used to exhibit a silencing effect for frequencies other than the first order component and its integral multiple components (0.5th order component and 1.5th order component described above), It is necessary to provide a plurality of variable resonators of a kind, each provided with an actuator, and further, an operating system for individually operating each actuator. This not only complicates the configuration of the silencer system, but also complicates the control operation for operating each actuator, leading to an increase in cost and a possibility of causing a malfunction.

  The resonator is attached not only to the intake pipe but also to the exhaust pipe and may be used to reduce exhaust noise. This exhaust pipe resonator also has the same problems as described above.

  The present invention has been made in view of such a point, and the object of the present invention is not only the peak noise (noise of the primary component frequency) and the noise of the integer multiple component frequency but also other frequencies. It can also be effective for noise (noise of 0.5th order component frequency, 1.5th order component frequency, etc.), and will follow even if the frequency of noise fluctuates. Another object of the present invention is to provide a variable frequency silencing system having a simple configuration capable of obtaining a silencing effect.

-Principle of solving the problem-
The solution principle of the present invention devised to achieve the above object is that at least one of L (length of the communication pipe), S (passage area inside the communication pipe), V (volume of the resonator chamber) is Multiple types of resonators with specific ratios are actuated by a single actuator. When the actuator is operated, the frequency of the noise targeted by each resonator can be changed simultaneously by changing at least one of the L, S, and V while maintaining the specific ratio. It is configured.

-Solution-
Specifically, the present invention is attached to a gas flow pipe connected to the internal combustion engine body, and is adapted to the Helmholtz's frequency response to a change in the frequency of gas noise in the gas flow pipe accompanying a change in the operating state of the internal combustion engine body. A variable frequency silencer system that uses the resonance principle to reduce gas noise at that frequency is assumed. The variable frequency silencing system is provided with a plurality of resonators each having a resonator body having a resonator chamber and a communication pipe for communicating the resonator body with the gas flow pipe. The ratio between the resonators in at least one of “the length of the communication pipe”, “the passage area inside the communication pipe”, and “the volume of the resonator chamber” is maintained constant, and a single actuator is used. An interlocking mechanism is provided so that at least one of “the length of the communication pipe”, “the passage area inside the communication pipe”, and “the volume of the resonator chamber” is changed in conjunction.

  As an application mode of the present invention, specifically, it is possible to reduce intake noise by providing it in an intake system of an internal combustion engine. Specific examples of the configuration when the intake system is provided include the following. A variable frequency silencer system that is attached to an intake pipe of an internal combustion engine and that reduces the intake noise of that frequency using Helmholtz resonance principle so as to respond to a change in frequency of the intake sound accompanying a change in the rotational speed of the internal combustion engine Assuming The variable frequency silencing system is provided with a plurality of resonators each having a resonator body having a resonator chamber and a communication pipe for communicating the resonator body with the intake pipe. The ratio between the resonators in at least one of “the length of the communication pipe”, “the passage area inside the communication pipe”, and “the volume of the resonator chamber” is maintained constant, and a single actuator is used. An interlocking mechanism is provided so that at least one of “the length of the communication pipe”, “the passage area inside the communication pipe”, and “the volume of the resonator chamber” is changed in conjunction.

  The “passage area inside the communication pipe” in each of the above solution means not only the passage area of the communication pipe itself in a direction substantially orthogonal to the extending direction thereof, but also the communication pipe opens to the gas flow pipe (intake pipe). It is a concept including an opening area or an opening area where the communication pipe opens to the resonator chamber. For example, the smallest portion of the opening area and the passage area of the communication pipe itself corresponds to the “passage area inside the communication pipe”.

  According to these specific matters, the primary component and its integral multiple components (secondary component, tertiary component, etc.) of gas noise (intake air temperature) in various frequency bands generated in the gas flow pipe (intake pipe) ) Can be reduced by one of a plurality of resonators, and gas noise in other frequency bands (for example, 0.5th-order component, 1.5th-order component, etc.) can be reduced by other resonators. In addition, when the noise generation state in the gas flow pipe changes (for example, when the frequency of the intake sound changes along with the change in the rotational speed of the internal combustion engine), each resonator is "," The passage area inside the communication pipe ", and" the volume of the resonator chamber "are changed in conjunction with each other. At this time, the ratio between the resonators in at least one of “the length of the communication pipe”, “the passage area inside the communication pipe”, and “the volume of the resonator chamber” is kept constant. Therefore, the primary component and the integral multiple components (secondary component, tertiary component, etc.) after the noise generation state is changed can be reduced by one of a plurality of resonators, and in other frequency bands. Noise (for example, a 0.5th-order component or a 1.5th-order component after the noise generation state has changed) can be reduced by other resonators. As described above, it is possible to effectively reduce noise in each frequency band while operating each resonator by a single actuator, and it is not necessary to provide an actuator for each resonator. Therefore, according to the present solution, while only one actuator is required and the configuration is simplified, not only the peak noise (noise of the primary component frequency) and the noise of the integral multiple of the component frequency, This is a case where the noise reduction effect can be exhibited even for noises of other frequencies (noises of 0.5th-order component frequency, 1.5th-order component frequency, etc.) and the noise frequency fluctuates. Can also follow it to obtain a silencing effect.

  As described above, elements that change the silencing characteristics (resonance frequencies) of individual resonators in conjunction with a single actuator include “length of communication pipe”, “passage area inside communication pipe”, “resonator chamber Although there is a “volume”, specific configurations for changing the “passage area inside the communication pipe” include the following.

  First, a plurality of intake pipe side openings are formed in the intake pipe so as to individually communicate with the resonator chambers of the respective resonators through the respective communication pipes. In addition, a cylindrical movable member having a plurality of movable member side openings individually facing each intake pipe side opening is assembled inside the intake pipe so as to be relatively movable. And, by moving the movable member relative to the intake pipe, the overlapping state of the intake pipe side openings and the movable member side openings facing each other is changed to change the communication area between the openings, Thus, the frequency of the intake sound that can be reduced is changed by changing the resonance frequency of each resonator.

  In this case, there are the following two types of configurations for moving the movable member relative to the intake pipe. First, the movable member slides in the direction along the axis of the intake pipe with respect to the intake pipe, thereby changing the overlapping state of each intake pipe side opening and the movable member side opening facing each other. The communication area between them is changed. Further, the movable member rotates about the axis of the intake pipe with respect to the intake pipe, thereby changing the overlapping state of each intake pipe side opening and the movable member side opening facing each other. The communication area is changed.

  In this way, when the resonance frequency of each resonator is changed by moving the cylindrical movable member inside the intake pipe, the above-mentioned effects (various types are achieved while reducing the number of parts arranged outside the intake pipe. Is it possible to reduce noise in the frequency band (0.5th-order component, first-order component, etc.), improve followability when the frequency of these noises fluctuates, and simplify the configuration by using only a single actuator? it can. For this reason, the space for incorporating the variable frequency silencing system according to the present invention is small, and the utility is high.

  Other configurations for changing the “passage area inside the communication pipe” of each resonator by a single actuator include the following. First, each resonator is arranged adjacent to each other, and a slider that makes the passage area inside the communication pipe variable by sliding the communication pipes of these resonators in a direction substantially perpendicular to the extending direction of the communication pipe. Prepare each. Further, the opposing side surfaces of these sliders are formed as inclined surfaces. On the other hand, by moving in the extension direction of the communication pipe between the sliders, a pressure is applied to the inclined surface of each slider to slide the slider in a direction substantially perpendicular to the extension direction of the communication pipe. A pressing member is provided. Then, the inclination angles of the inclined surfaces of the sliders are set to different inclination angles so that the sliding movement amount of the slider with respect to the movement amount of the pressing member is maintained at a constant ratio.

  According to this specific matter, as the pressing member moves, each slider slides by receiving the pressing force from the pressing member, and is pushed out into each communication pipe. As a result, each communication pipe is Both internal passage areas become smaller. The rate at which the passage area decreases is determined by the angle of the inclined surface of each slider. For example, when the angle of the inclined surface is 45 °, the slider slides by the same size as the amount of movement of the pressing member, and when the angle of the inclined surface is about 63 °, the amount of movement of the pressing member. Therefore, the slider slides by about half of the dimension. In other words, by appropriately setting the angle of this inclined surface, the ratio of the slide movement amount of each slider can be arbitrarily set, and the ratio of the passage area inside the communication pipe between the resonators can be kept constant. Can do.

  Moreover, the following is mentioned as a structure which changes the "length of a communication pipe" of each resonator with a single actuator. First, each resonator main body is configured to be movable integrally in the contact / separation direction with respect to the intake pipe as the actuator is driven. In addition, each communication pipe that connects the resonator main body and the intake pipe is configured such that the length dimension thereof can be changed according to the movement position of the resonator main body. On the other hand, the “passage area inside the communication pipe” in each resonator is set to a different area. As a result, the length of the communication pipe is maintained while the ratio of the “passage area inside the communication pipe” is kept constant by moving each resonator body in the contact / separation direction with respect to the intake pipe as the actuator is driven. The configuration is changed.

  Moreover, the following is mentioned as a structure which changes the "volume of a resonator chamber" of each resonator with a single actuator. First, each resonator main body is formed by including a first member fixed to the intake pipe and a second member that makes the volume of the resonator chamber variable by moving relative to the first member. On the other hand, the areas of the surfaces extending in the direction substantially orthogonal to the moving direction of the second member in each resonator are set to different areas. As a result, the second member of each resonator body moves relative to the first member as the actuator is driven, so that the ratio of the “volume of the resonator chamber” is maintained constant. The “volume” is changed.

  Furthermore, the following can be cited as a configuration in which the “length of the communication pipe” of each resonator is changed by a single actuator. First, each resonator body is configured to be movable independently of each other in the direction of contact with and away from the intake pipe as the actuator is driven. In addition, each communication pipe that connects the resonator main body and the intake pipe is configured such that the length dimension thereof can be changed according to the movement position of the resonator main body. On the other hand, the “length of the communication pipe” in each resonator is set to a different length. As the actuators are driven, the resonator bodies move in the direction of contact and separation independently of the intake pipe, so that the ratio of the “communication pipe length” is maintained constant. The length dimension of the “pipe length” is changed.

  In the present invention, when a plurality of variable resonators in which at least one of L (length of the communication pipe), S (passage area inside the communication pipe), and V (volume of the resonator chamber) is variable are provided, Each resonator in which at least one of V has a specific ratio is operated by a single actuator, and when the actuator is operated, at least one of L, S, and V is maintained while maintaining the specific ratio. I am trying to change it. For this reason, it becomes possible to simultaneously change the frequency of the noise to be silenced by each resonator by a single actuator, and while simplifying the configuration, the peak noise (the noise of the primary component frequency) and its noise Not only the noise of the frequency of the integral multiple component, but also the noise of other frequencies (the noise of the frequency of the 0.5th order component, the frequency of the 1.5th order component, etc.) can exert the silencing effect, In addition, it is possible to provide a variable frequency silencing system that can exhibit a silencing effect even if the noise frequency fluctuates.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the present embodiment, a case where the present invention is applied as a variable frequency silencing system provided in an intake system of an automobile engine will be described.

(First embodiment)
-Schematic configuration of variable frequency silencer system-
FIG. 1 is a side view showing a part of an intake pipe (gas flow pipe) 1 of an automobile engine according to this embodiment, and FIG. 2 is a cross-sectional view taken along line II-II in FIG. FIG. 5 is a diagram showing the internal structure of the intake pipe 1. FIG. 5 is a cross-sectional view at a position corresponding to line VV in FIG.

  As shown in these drawings, two resonators 2 and 3 are attached to the intake pipe 1 of the automobile engine according to the present embodiment. Specifically, these resonators 2 and 3 are provided on the upstream side of the air cleaner in the intake system of the engine. A cylindrical movable sleeve (movable member) 4 is inserted into the intake pipe 1 at the attachment position of the resonators 2 and 3. The movable sleeve 4 is assembled so as to be slidable in a direction along the axis of the intake pipe 1 by a drive motor 5 (see FIG. 5) as an actuator (for the configuration and operation for this sliding movement). Will be described later). Hereinafter, each member will be described.

-Configuration of resonators 2 and 3-
The resonators 2 and 3 attached to the intake pipe 1 have the same configuration. Specifically, the resonator main bodies 21 and 31 having the resonator chambers 21a and 31a having relatively large capacities, and the communication pipes 22 and 32 for communicating the resonator main bodies 21 and 31 and the intake pipe 1 are provided. ing. In the following description, the resonator located on the right side in FIG. 2 is referred to as a first resonator 2, and the resonator located on the left side is referred to as a second resonator 3.

  The resonators 2 and 3 are provided at positions facing each other across the intake pipe 1. That is, the communication pipes 22 and 32 are respectively connected to the left and right sides of the intake pipe 1 facing each other, and the resonator main bodies 21 and 31 are respectively attached to the outer ends of the communication pipes 22 and 32. ing. The resonator main bodies 21 and 31 are formed of substantially arc-shaped containers so as to be substantially along the outer peripheral surface of the intake pipe 1, that is, surrounding the outer periphery of the intake pipe 1, thereby installing the resonators 2 and 3. The space is made compact.

  Moreover, the cross-sectional shape (cross-sectional shape of the direction orthogonal to the extension direction of the communication pipes 22 and 32) of each communication pipe 22 and 32 is a substantially rectangular shape. For this reason, the openings (intake pipe side openings) A1 and A2 formed in the intake pipe 1 to connect the communication pipes 22 and 32 have the same substantially rectangular shape. 10A is a diagram in which the intake pipe 1 is cut in a direction along the axis at the connection position of the communication pipes 22 and 32 and developed (the inner peripheral surface of the intake pipe 1 is the front side). FIG. In this way, substantially rectangular openings A1 and A2 are formed at two locations on the intake pipe 1, and each communication pipe is connected to the edge of the openings A1 and A2 (the edge on the outer peripheral surface side of the intake pipe 1). 22 and 32 are connected to each other.

-Movable sleeve 4-
FIG. 3 is a perspective view showing the movable sleeve 4. The movable sleeve 4 is inserted into the intake pipe 1 such that the outer diameter dimension thereof substantially coincides with the inner diameter dimension of the intake pipe 1 and the outer peripheral surface is in contact with the inner peripheral surface of the intake pipe 1. A slit 11 extending in the direction along the axis is formed in a part of the outer periphery of the intake pipe 1 (lower end position in FIGS. 2 and 5). On the other hand, a pin 41 whose width dimension is substantially located in the width dimension of the slit 11 is projected from the outer peripheral surface (lower end position in FIG. 3) of the movable sleeve 4, and this pin 41 is inserted into the slit 11. In the state, the movable sleeve 4 is inserted into the intake pipe 1. For this reason, the movable sleeve 4 is assembled so that it can slide in the direction along the axis (left-right direction in FIG. 5) while preventing relative rotation (shift about the axis) with respect to the intake pipe 1. ing. The pin 41 of the movable sleeve 4 is connected to an operating rod 51 protruding from a drive motor (electric motor or hydraulic motor) 5, and is movable as the operating rod 51 moves forward and backward as the drive motor 5 is driven. The sleeve 4 is slidable in the direction along the axis within the intake pipe 1.

  The movable sleeve 4 is formed with triangular openings (movable member side openings) B1 and B2 at positions corresponding to the substantially rectangular openings A1 and A2 formed in the intake pipe 1. Hereinafter, the triangular openings B1 and B2 formed in the movable sleeve 4 will be described. The right side of FIG. 10A is a diagram in which the movable sleeve 4 is cut in a direction along the axis thereof and developed (the diagram showing the inner peripheral surface of the movable sleeve 4 as the front side). Thus, triangular openings B1 and B2 are formed at two positions of the movable sleeve 4 at positions corresponding to the substantially rectangular openings A1 and A2 formed in the intake pipe 1.

  As one of the features of this embodiment, the shapes of the triangular openings B1 and B2 are different from each other. Specifically, the triangles that are the shapes of the openings B1 and B2 have angles α and α formed by the sides a1 and a2 extending in the circumferential direction of the movable sleeve 4 and the sides b1 and b2 extending in the direction along the axis. It is a right triangle that is a right angle (see FIG. 10A). These right triangles have different heights (lengths of the sides a1 and a2 extending in the circumferential direction) when the sides b1 and b2 extending in the direction along the axis of the movable sleeve 4 are used as the base. Specifically, the length of the other side a1 is set to about four times the length of one side a2. The opening B1 having a long side a1 is opposed to the communication tube 22 of the first resonator 2 through the opening A1, and the opening B2 having a short side a2 is the opening. The movable sleeve 4 is assembled to the intake pipe 1 so as to face the communication pipe 32 of the second resonator 3 via A2. Thus, in a state where the openings B1 and B2 formed in the movable sleeve 4 overlap the openings A1 and A2 formed in the intake pipe 1, the internal space of the intake pipe 1 and the resonators of the resonators 2 and 3 Although the chambers 21a and 31a are in communication with each other, the communication areas of the first resonator 2 and the second resonator 3 are different. That is, the communication area between the resonator chamber 21a of the first resonator 2 and the internal space of the intake pipe 1 is larger than the communication area between the resonator chamber 31a of the second resonator 3 and the internal space of the intake pipe 1, and The ratio of the communication areas is always a constant ratio regardless of the slide movement position of the movable sleeve 4. Specifically, since the ratio of the lengths of the sides a1 and a2 is set as described above, the ratio of these communication areas is “4: 1” (the resonator chamber 21a of the first resonator 2 and the intake pipe 1). The communication area with the internal space of the second resonator 3 is four times as large as the communication area between the resonator chamber 31a of the second resonator 3 and the internal space of the intake pipe 1), and the resonators 2 and 3 obtained by the above equation (1) The resonance frequency is set so that the resonance frequency of the first resonator 2 is approximately twice the resonance frequency of the second resonator 3 regardless of the slide movement position of the movable sleeve 4.

-Drive motor 5-
The drive motor 5 includes the operating rod 51 as described above, and the movable sleeve 4 is slid within the intake pipe 1 by the forward and backward movement of the operating rod 51 to adjust the slide movement position of the movable sleeve 4. Is. That is, by adjusting the forward / backward movement position of the operating rod 51, the communication area between the internal space of the intake pipe 1 and the resonator chambers 21a and 31a of the resonators 2 and 3 (the area where the openings A1 and B1 overlap, the openings A2 and B2). Are set in each case.

  The drive motor 5 is driven in response to a drive signal from an engine controller 6 (hereinafter referred to as ECU) that controls the engine, and slides the movable sleeve 4 to a predetermined position inside the intake pipe 1. ing. On the other hand, the ECU 6 receives an engine speed signal from the engine speed sensor 61, calculates a peak frequency (primary component) of the intake sound based on this signal, and outputs a drive signal based on the peak frequency to the drive motor 5. It is like that. That is, the ECU 6 detects the current engine speed from the signal from the engine speed sensor 61, calculates the peak frequency of the intake sound from the engine speed, and adapts it (the resonance frequency of the first resonator 2). The sliding movement position of the movable sleeve 4 is determined (so that the frequency coincides with the peak frequency), and the drive signal is output to the drive motor 5. Thereby, the interlocking mechanism referred to in the present invention is configured.

  The engine rotational speed sensor 61 detects the rotational speed of the crankshaft of the engine, and the outer peripheral teeth (protrusions) of the NE rotor attached integrally with the crankshaft pass therethrough. And an electromagnetic pickup that generates a pulse wave.

-Mute operation-
Next, the silencing operation by the variable frequency silencing system according to the present embodiment configured as described above will be described.

  When the engine is driven, an engine speed signal from the engine speed sensor 61 is transmitted to the ECU 6. Based on the received engine speed signal, the ECU 6 calculates the frequency (primary component) of the intake sound that peaks (maximum) at the engine speed. For example, the relationship between the engine speed signal and the peak intake sound frequency is stored in the ECU 6 as a map, and the peak intake sound frequency is read from this map.

  Thereafter, the ECU 6 outputs a drive signal based on the calculated peak intake sound frequency to the drive motor 5. The drive motor 5 that has received this drive signal drives in accordance with this drive signal, and slides the movable sleeve 4 to a predetermined position inside the intake pipe 1.

  As a result, in the first resonator 2, the resonance frequency coincides with the peak intake sound frequency (primary component), and the noise of the primary component and its integral multiple components (secondary component and 3). The noise of the next component etc. can be reduced.

  On the other hand, in the second resonator 3, since the resonance frequency is ½ of the resonance frequency of the first resonator 2 as described above, the second-order resonator 3 has a 0.5th-order component that is half the frequency of the first-order component. Resonance frequencies coincide with each other, and a silencing effect is exhibited with respect to the noise of the 0.5th order component and the noise of the 1.5th order component that is an intermediate frequency between the first order component and the second order component. Become.

  FIG. 4 shows a cross-sectional view of the same portion as FIG. 2 when the engine speed is relatively low (for example, about 2000 rpm). FIG. 5 is a cross-sectional view at a position corresponding to the line V-V in FIG. 4 and shows an overlapping state of the opening A1 and the opening B1 on the first resonator 2 side. FIG. 6 is a cross-sectional view at a position corresponding to the line VI-VI in FIG. 4 and shows an overlapping state of the opening A2 and the opening B2 on the second resonator 3 side. FIG. 10B is a diagram in which the intake pipe 1 and the movable sleeve 4 are cut and expanded in the direction along the axial center, and the overlapping states of the openings (A1, B1, A2, B2) are shown. ing. As can be seen from these drawings, the communication area between the resonator chamber 21 a of the first resonator 2 and the inside of the intake pipe 1 is larger than the communication area between the resonator chamber 31 a of the second resonator 3 and the inside of the intake pipe 1. The first resonator 2 reduces the noise of the primary component and the integral multiples thereof (secondary component, third-order component, etc.), and the second resonator 3 reduces the 0.5th-order component and the 1.5th-order component. The component noise will be reduced.

  When the engine speed fluctuates and the frequency of the intake sound changes accordingly, the engine speed signal from the engine speed sensor 61 is transmitted to the ECU 6 as in the above case, and the ECU 6 A drive signal based on the calculated peak intake sound frequency is output to the drive motor 5. The drive motor 5 that has received this drive signal is driven in accordance with this drive signal, and slides the movable sleeve 4 to a predetermined position inside the intake pipe 1.

  As a result, in the first resonator 2, the resonance frequency matches the peak intake sound frequency (primary component) after the engine speed fluctuates, and the noise of the primary component and its integral multiples. Noise (secondary component, tertiary component, etc.) can be reduced.

  On the other hand, in the second resonator 3, the resonance frequency coincides with the 0.5th order component, which is half the frequency of the first order component after the engine speed fluctuates. A silencing effect can be obtained for component noise and 1.5th order component noise, which is an intermediate frequency between the first and second order components.

  FIG. 7 shows a cross-sectional view of the same portion as FIG. 2 after the engine speed fluctuates and when the engine speed is relatively high (for example, about 4000 rpm). FIG. 8 is a cross-sectional view at a position corresponding to the line VIII-VIII in FIG. 7 and shows an overlapping state of the opening A1 and the opening B1 on the first resonator 2 side. FIG. 9 is a cross-sectional view at a position corresponding to the line IX-IX in FIG. 7 and shows an overlapping state of the opening A2 and the opening B2 on the second resonator 3 side. FIG. 10C is a diagram in which the intake pipe 1 and the movable sleeve 4 are cut and expanded in the direction along the axial center, and the overlapping states of the openings (A1, B1, A2, B2) are shown. ing. As can be seen from these drawings, the communication area between the resonator chamber 21 a of the first resonator 2 and the inside of the intake pipe 1 is larger than the communication area between the resonator chamber 31 a of the second resonator 3 and the inside of the intake pipe 1. The first resonator 2 reduces the noise of the primary component after the engine speed fluctuates and the integral multiple of the noise, and the second resonator 3 reduces the engine speed after the engine speed fluctuates by 0. The noise of the fifth order component and the noise of the 1.5th order component are reduced. In addition, since the frequency of each component (primary component, 1.5th-order component, etc.) increases as the engine speed increases, the sliding movement direction of the movable sleeve 4 in this case includes the openings A1, The opening area is increased so that B1, A2, and B2 overlap each other, and the resonance frequency of each of the resonators 2 and 3 is controlled to be increased.

  As described above, every time the frequency of the intake sound changes with the fluctuation of the engine speed, the drive motor 5 is driven accordingly to adjust the slide movement position of the movable sleeve 4, and each component (0. 5th order component, 1st order component, 1.5th order component, 2nd order component, etc.) can be effectively reduced, and the quietness of the intake system can always be maintained regardless of the engine speed.

  As described above, in the present embodiment, only one drive motor 5 as an actuator is required, and while simplifying the configuration, the peak noise (noise of the primary component frequency) and the frequency of the integer multiple components thereof are reduced. Not only noise but also other frequency noise (0.5th order component frequency, 1.5th order component frequency, etc.) can be silenced and the noise frequency fluctuates. Even in such a case, it is possible to obtain a silencing effect by following it.

(Modification 1)
Next, Modification 1 of the above-described first embodiment will be described. In the first embodiment, the openings B1 and B2 formed in the movable sleeve 4 are right triangles. In this example, an isosceles triangle is used instead. FIG. 11 is a diagram corresponding to FIG. 10 in this example.

  Also in this case, the resonator chamber 31a and the intake pipe 1 of the second resonator 3 with respect to the communication area between the resonator chamber 21a of the first resonator 2 and the internal space of the intake pipe 1 are the same as in the case of the first embodiment described above. The ratio of the communication area with the internal space is “4: 1” regardless of the slide movement position of the movable sleeve 4 (the communication area between the resonator chamber 21a of the first resonator 2 and the internal space of the intake pipe 1 is the second resonator). The shapes of the openings B1 and B2 are designed so as to be four times the communication area between the three resonator chambers 31a and the internal space of the intake pipe 1. Thereby, the resonance frequency of each of the resonators 2 and 3 obtained by the above formula (1) is approximately equal to the resonance frequency of the second resonator 3 regardless of the slide movement position of the movable sleeve 4. It is set to be twice. Thereby, the interlocking mechanism referred to in the present invention is configured.

  The shape of the openings B1 and B2 formed in the movable sleeve 4 is not limited to a triangle, and the second shape with respect to the communication area between the resonator chamber 21a of the first resonator 2 and the internal space of the intake pipe 1 is not limited. Any shape is acceptable as long as the ratio of the communication area between the resonator chamber 31a of the resonator 3 and the internal space of the intake pipe 1 is kept constant regardless of the slide movement position of the movable sleeve 4. For example, a trapezoidal shape or the like is also applicable. .

(Modification 2)
Next, Modification 2 of the above-described first embodiment will be described. The variable frequency silencer system according to the first embodiment includes two resonators 2 and 3, and the first resonator 2 generates primary component noise and integral multiple components (secondary component, tertiary component, etc.). The noise of the 0.5th order component and the 1.5th order component was reduced by the second resonator 3. In this example, three resonators are provided instead.

  FIG. 12 is a diagram corresponding to FIG. 2 in the variable frequency silencing system according to this example. As shown in this figure, in the variable frequency silencing system according to this example, a total of three resonators 2, 3, and 7 are attached to the intake pipe 1. Each of the resonators 2, 3, and 7 has the same configuration as that of the first embodiment described above.

  Thus, in this example, since the three resonators 2, 3, and 7 are provided, FIG. 13 (the drawing in which the intake pipe 1 and the movable sleeve 4 are cut and expanded in the direction along the axis, As shown in the openings (showing overlapping states of A1, B1, A2, B2, A3, B3), the openings A1, A2, A3 formed in the intake pipe 1 and the openings formed in the movable sleeve 4 Three each of B1, B2, and B3 are also formed. The shapes of the openings B1, B2, and B3 formed in these movable sleeves 4 are also different from each other as in the case of the first embodiment described above, and the area of the opening B1 facing the first resonator 2 is the largest, and the third The area of the opening B3 that opposes the resonator 7 is the smallest, and the area of the opening B2 that opposes the second resonator 3 is set to a substantially intermediate size between the openings B1 and B3. Other configurations are substantially the same as those of the first embodiment described above.

  According to the configuration of this example, it is possible to exert a silencing effect on noise in three types of frequency bands. For example, the first resonator 2 reduces the noise of the primary component and the integral multiples thereof (secondary component, tertiary component, etc.), and the second resonator 2 reduces the 0.5th order component and 1.5th order component. The third resonator 2 can reduce noise such as a 0.3th order component and a 1.3th order component. Similarly to the case of the first embodiment described above, when the frequency of the intake sound changes with the fluctuation of the engine speed, the drive motor 5 is driven accordingly and the slide movement position of the movable sleeve 4 is changed. And adjusting the resonance frequency of each of the resonators 2, 3, and 7 in conjunction with each other (the 0.3th order component, the 0.5th order component, the first order component, .. 3rd order component, 1.5th order component, 2nd order component ...) noise can be effectively reduced. For this reason, the quietness of the intake system can always be maintained regardless of the engine speed.

  It should be noted that the number of resonators 2, 3, and 7 may be four or more. When four first to fourth resonators are provided, the number of resonators 2, 3, and 7 is, for example, 1 by the first resonator. The noise of the second component and its integral multiple components are reduced, the noise of the 0.7th order component and the 1.7th order component is reduced by the second resonator, and the 0.5th order component and the 1.5th order component are reduced by the third resonator. The noise of the component can be reduced, and the fourth-order resonator 2 can reduce the noise of the 0.3th order component and the 1.3th order component.

(Second Embodiment)
Next, a second embodiment will be described. In the above-described first embodiment and its modification, the resonance frequency of each of the resonators 2, 3, 7 is made variable by sliding the movable sleeve 4 in the direction along the axis of the intake pipe 1. In the present embodiment, instead, the movable sleeve 4 rotates around the axis of the intake pipe 1 to make the resonance frequency variable. Since the other configuration is the same as that of the first embodiment described above, only the arrangement state of the movable sleeve 4 and the change in the silencing operation accompanying the rotation of the movable sleeve 4 will be described here.

  FIG. 14 is a perspective view showing the movable sleeve 4 in the present embodiment. The movable sleeve 4 in the present embodiment also has an outer diameter that substantially matches the inner diameter of the intake pipe 1 and is inserted into the intake pipe 1 in the same manner as in the first embodiment described above. A pin 41 protrudes from the pin 41.

  As a difference of the present embodiment from the first embodiment, as shown in FIG. 15 (the figure corresponding to FIG. 4), a part of the outer peripheral portion of the intake pipe 1 (the lower periphery in the drawing) is provided. A slit 12 extending in the circumferential direction is formed. The movable sleeve 4 is inserted into the intake pipe 1 with the pin 41 protruding from the outer peripheral surface of the movable sleeve 4 being inserted into the slit 12. For this reason, the movable sleeve 4 is assembled so as to be able to rotate around the axis while preventing a positional shift in the direction along the axis of the intake pipe 1 (left-right direction in FIG. 16). The pin 41 of the movable sleeve 4 is connected to an operating rod protruding from the drive motor similar to that of the first embodiment, and the movable sleeve is moved along with the forward / backward movement of the operating rod accompanying the drive of the drive motor. 4 rotates inside the intake pipe 1.

  Further, similar to the first embodiment, the movable sleeve 4 has triangular openings B1 and B2 at positions corresponding to the substantially rectangular openings A1 and A2 formed in the intake pipe 1. Is formed. The shapes of the triangular openings B1 and B2 in the present embodiment are also different from each other. Specifically, the triangles that are the shapes of the openings B1 and B2 have angles α and α formed by the sides a1 and a2 extending in the circumferential direction of the movable sleeve 4 and the sides b1 and b2 extending in the direction along the axis. It is a right triangle that is a right angle (see FIG. 14). These right triangles are different from each other in height (the lengths of the sides b1 and b2 extending in the direction along the axis) when the sides a1 and a2 extending in the circumferential direction of the movable sleeve 4 are used as the bases. Specifically, the length of the other side b1 is set to about four times the length of one side b2. The opening B1 having the long side b1 is opposed to the communication pipe 22 of the first resonator 2 through the opening A1, and the opening B2 having the short side b2 is the opening. The movable sleeve 4 is assembled to the intake pipe 1 so as to face the communication pipe 32 of the second resonator 3 via A2. Thus, in a state where the openings B1 and B2 formed in the movable sleeve 4 overlap the openings A1 and A2 formed in the intake pipe 1, the internal space of the intake pipe 1 and the resonators of the resonators 2 and 3 Although the chambers 21a and 31a are in communication with each other, the communication areas of the first resonator 2 and the second resonator 3 are different. That is, the communication area between the resonator chamber 21a of the first resonator 2 and the internal space of the intake pipe 1 is larger than the communication area between the resonator chamber 31a of the second resonator 3 and the internal space of the intake pipe 1, and The ratio of the communication areas is always a constant ratio regardless of the slide movement position of the movable sleeve 4. Specifically, since the ratio of the lengths of the sides b1 and b2 is set as described above, the ratio of these communication areas is “4: 1” (the resonator chamber 21a of the first resonator 2 and the intake pipe 1). The communication area with the internal space of the second resonator 3 is four times as large as the communication area between the resonator chamber 31a of the second resonator 3 and the internal space of the intake pipe 1), and the resonators 2 and 3 obtained by the above equation (1) The resonance frequency is set so that the resonance frequency of the first resonator 2 is approximately twice the resonance frequency of the second resonator 3 regardless of the slide movement position of the movable sleeve 4. Thereby, the interlocking mechanism referred to in the present invention is configured. Other configurations are the same as those of the first embodiment described above.

  Next, the silencing operation by the variable frequency silencing system according to the present embodiment configured as described above will be described.

  FIG. 15 shows a cross-sectional view of the same portion as FIG. 4 when the engine speed is relatively low (for example, about 2000 rpm). FIG. 16 is a cross-sectional view at a position corresponding to the line XVI-XVI in FIG. 15, and shows an overlapping state of the opening A1 and the opening B1 on the first resonator 2 side. FIG. 17 is a cross-sectional view at a position corresponding to the line XVII-XVII in FIG. 15, and shows an overlapping state of the opening A2 and the opening B2 on the second resonator 3 side. As can be seen from these drawings, the communication area between the resonator chamber 21 a of the first resonator 2 and the inside of the intake pipe 1 is larger than the communication area between the resonator chamber 31 a of the second resonator 3 and the inside of the intake pipe 1. The first resonator 2 reduces the noise of the primary component and the integral multiples thereof (secondary component, third-order component, etc.), and the second resonator 3 reduces the 0.5th-order component and the 1.5th-order component. The component noise will be reduced.

  FIG. 18 shows a cross-sectional view of the same portion as FIG. 15 after the engine speed fluctuates and when the engine speed is relatively high (for example, about 4000 rpm). FIG. 19 is a cross-sectional view at a position corresponding to the line XIX-XIX in FIG. 18 and shows an overlapping state of the opening A1 and the opening B1 on the first resonator 2 side. FIG. 20 is a cross-sectional view at a position corresponding to the line XX-XX in FIG. 18 and shows an overlapping state of the opening A2 and the opening B2 on the second resonator 3 side. As can be seen from these drawings, the communication area between the resonator chamber 21 a of the first resonator 2 and the inside of the intake pipe 1 is larger than the communication area between the resonator chamber 31 a of the second resonator 3 and the inside of the intake pipe 1. The first resonator 2 reduces the noise of the primary component after the engine speed fluctuates and the integral multiple of the noise, and the second resonator 3 reduces the engine speed after the engine speed fluctuates by 0. The noise of the fifth order component and the noise of the 1.5th order component are reduced. Similarly to the case of the first embodiment, the frequency of each component (primary component, 1.5th component, etc.) increases as the engine speed increases. The rotation direction is a direction in which the opening area is increased so that the openings A1, B1, A2, and B2 overlap each other, and is controlled to increase the resonance frequency of the resonators 2 and 3.

  As described above, every time the frequency of the intake sound changes in accordance with the fluctuation of the engine speed, the drive motor is driven accordingly to adjust the rotational position of the movable sleeve 4, and each component (0.5 The noise of the next component, the first component, the 1.5th component, the second component, etc.) can be effectively reduced, and the quietness of the intake system can always be maintained regardless of the engine speed.

  As described above, according to the present embodiment, only one drive motor as an actuator is required, and the simplification of the configuration, while the peak noise (the noise of the primary component frequency) and the frequency of the integral multiple component thereof are reduced. Not only noise but also other frequency noise (0.5th order component frequency, 1.5th order component frequency, etc.) can be silenced and the noise frequency fluctuates. Even in such a case, it is possible to obtain a silencing effect by following it.

  Note that, as in this embodiment, even in the case where the resonance frequency of each of the resonators 2 and 3 is made variable by rotating the movable sleeve 4 around the axis of the intake pipe 1, The openings B1 and B2 formed in the movable sleeve 4 may be isosceles triangles or may be configured to include three or more resonators.

(Third embodiment)
Next, a third embodiment will be described. FIG. 21 is a cross-sectional view of the intake pipe 1 and the resonators 2 and 3 in the arrangement portion of the variable frequency silencing system according to the present embodiment.

  As shown in FIG. 21, the variable frequency silencing system according to the present embodiment includes a first resonator 2 and a second resonator 3 that are disposed adjacent to each other in the extending direction of the intake pipe 1.

  The capacities of the resonator chambers 21a and 31a in these resonators 2 and 3 are substantially the same. In addition, the lengths of the communication pipes 22 and 32 that connect the resonator main bodies 21 and 31 and the intake pipe 1 are substantially the same.

  The feature of this embodiment is that the passage areas of the communication pipes 22 and 32 are variable while maintaining a constant ratio. This will be specifically described below.

  As shown in FIG. 21, one side of the communication pipes 22 and 32 in each of the resonators 2 and 3 and the side facing the opposite resonators 3 and 2 is open to the side. In addition, sliders 23 and 33 for making the cross-sectional area (passage area) inside the communication pipes 22 and 32 variable are provided in the respective open portions. As the shape of the slider 23 provided in the communication pipe 22 of the first resonator 2 located on the left side in FIG. 21, the surface facing the internal space of the communication pipe 22 is a vertical surface 23a extending in the vertical direction. An inner wall of the communication pipe 22 is formed between the side face 22a facing the inside of the communication pipe 22. In addition, the surface of the slider 23 opposite to the surface 23a facing the internal space of the communication pipe 22 is formed as a first inclined surface 23b inclined with a predetermined inclination angle.

  On the other hand, as the shape of the slider 33 provided in the communication pipe 32 of the second resonator 3 located on the right side in FIG. 21, the surface facing the internal space of the communication pipe 32 is a vertical surface 33a extending in the vertical direction. In addition, an inner wall of the communication pipe 32 is formed between the communication pipe 32 and a side surface 32a facing each other. In addition, the surface of the slider 33 opposite to the surface 33a facing the internal space of the communication pipe 32 is formed as a second inclined surface 33b inclined with a predetermined inclination angle.

  The inclination angle of the second inclined surface 33b is set larger than the inclination angle of the first inclined surface 23b. For example, the inclination angle of the second inclined surface is set to 75 °, and the inclination angle of the first inclined surface is set to 45 °.

  A movable block (pressing member) 8 for moving the sliders 23 and 33 in the horizontal direction is disposed between the sliders 23 and 33. The inclination angles of the side surfaces 81 and 82 of the movable block 8 substantially coincide with the inclination angles of the opposing inclined surfaces 23b and 33b. In other words, the left side surface 81 in the drawing facing the first inclined surface 23b is set to be relatively small in angle with the second inclined surface 33b, while being substantially coincident with the inclination angle of the first inclined surface 23b. The side surface 82 on the right side in the figure facing is substantially equal to the inclination angle of the second inclined surface 33b, and the inclination angle is set to be relatively large.

  The lower end of the movable block 8 is connected to a pulling member 83 such as a wire that passes between the resonators 2 and 3 and extends downward, and the other end of the pulling member 83 is connected to an actuator. ing. Therefore, when the pulling member 83 is pulled down as the actuator is driven, the movable block 8 moves downward as shown in FIG. 22, and the sliders 23 and 33 are moved by the pressing force from the movable block 8. The areas of the communication pipes 22 and 32 of the resonators 2 and 3 are reduced by moving in directions away from each other (outside in the horizontal direction in the figure). At this time, since the inclination angles of the inclined surfaces 23b and 33b of the sliders 23 and 33 are different from each other as described above, the movement amounts of the sliders 23 and 33 relative to the movement amount of the movable block 8, that is, the communication pipes 22 and 33, respectively. The dimensions for reducing the passage area of 32 are different from each other, and the passage area can be varied while maintaining the ratio of the passage areas of the communication pipes 22 and 32 constant. Specifically, the dimensions and inclination angles of the respective parts are set so that the passage area of the communication pipe 22 of the first resonator 2 is always about four times the passage area of the communication pipe 32 of the second resonator 3. . For this reason, as the resonance frequency of each of the resonators 2 and 3 obtained by the above formula (1), the resonance frequency of the first resonator 2 is about 2 of the resonance frequency of the second resonator 3 regardless of the moving position of the movable block 8. It is set to be doubled. Thereby, the interlocking mechanism referred to in the present invention is configured.

  When the pulling force of the pulling member 83 by the actuator is released, an urging force such as a coil spring is applied so that the movable block 8 moves upward, and each slider 23 is moved along with the upward movement of the movable block 8. , 33 move in a direction approaching each other (inward in the left-right direction in the figure) to increase the passage area of the communication pipes 22, 32 of the resonators 2, 3. Various actuators such as an electric motor in which a roller for winding the traction member 83 is attached to the drive shaft, and a solenoid valve that can retract the traction member 83 along its extending direction are applied as the actuator. Is possible.

  According to the configuration of the present embodiment, it is possible to change the passage areas of the communication pipes 22 and 32 by sliding the sliders 23 and 33 together by only moving the movable block 8 by one actuator. The ratio of the passage areas of the communication pipes 22 and 32 is kept constant. Therefore, while simplifying the configuration, not only the peak noise (noise of the first-order component frequency) and the noise of the integer multiple component frequency, but also noise of other frequencies (0.5-order component frequency and The noise reduction effect can be exhibited even for noise (such as the frequency of the 1.5th-order component frequency), and even if the frequency of the noise fluctuates, the noise reduction effect can be obtained following it.

(Fourth embodiment)
Next, a fourth embodiment will be described. In each of the above-described embodiments and modifications, the opening area is variable between the resonators 2 and 3 while maintaining the opening area of the communication pipes 22 and 32 with respect to the internal space of the intake pipe 1 at a predetermined ratio. It was something to do. In the present embodiment, instead, between the resonators 2 and 3, the open areas of the communication pipes 22 and 32 with respect to the internal space of the intake pipe 1 are maintained at a predetermined ratio while the communication pipes 22 and 32 are connected. By changing the length dimension, the resonance frequency of each of the resonators 2 and 3 is changed, so that a silencing effect can be exhibited against noise in a plurality of frequency bands.

  FIG. 23 is a cross-sectional view of the intake pipe 1 and the resonators 2 and 3 in the arrangement portion of the variable frequency silencing system according to the present embodiment.

  As shown in FIG. 23, the variable frequency silencing system according to the present embodiment is configured such that the first resonator 2 and the second resonator 3 are disposed adjacent to the extension direction of the intake pipe 1.

  As a feature of the present embodiment, pipe-shaped inner pipes 13 and 14 extending toward the resonators 2 and 3 are integrally formed at connection portions of the resonators 2 and 3 in the intake pipe 1. 23, the passage area of the first inner tube 13 extending toward the first resonator 2 located on the right side in FIG. 23 is larger than the passage area of the second inner tube 14 extending toward the second resonator 3 located on the left side in FIG. It is set large. Specifically, the passage area of the first inner pipe 13 is set to be about four times the passage area of the second inner pipe 14. For example, the inner tubes 13 and 14 have a square cross-sectional shape, and one side of the first inner tube 13 is set to be approximately twice as long as one side of the second inner tube 14.

  On the other hand, the communication pipes 22 and 32 extending from the resonator main bodies 21 and 31 of the resonators 2 and 3 extend toward the inner pipes 13 and 14, respectively, and the inner pipes 13 and 14 are inserted into the communication pipes 22 and 32, respectively. It has been configured. That is, the upper end portions of the communication pipes 22 and 32 and the lower end portions of the inner pipes 13 and 14 are overlapped, and these both communicate with the communication passages C1 and C2 that communicate the internal space of the intake pipe 1 and the resonator chambers 21a and 31a. It is the structure to form. Further, when the resonator bodies 21 and 31 of the resonators 2 and 3 are moved up and down together with the communication pipes 22 and 32, the communication pipes 22 and 32 move along the extending direction with respect to the inner pipes 13 and 14. The length of the communication passages C1 and C2 is substantially changed. As a configuration for changing the length of the communication passages C1 and C2, the resonator bodies 21 and 31 of the resonators 2 and 3 are integrally connected to each other, and are connected to the side surfaces of the resonator body 31 of the second resonator 3. Is provided with a pin 34 extending in the horizontal direction. And this pin 34 is connected with the operating rod 51 which protrudes from the drive motor 5 which is an actuator, The resonator main bodies 21 and 31 move with the advancing / retreating movement of the operating rod 51 accompanying the drive of the drive motor 5, Accordingly, the length of the communication paths C1 and C2 is changed. Thereby, the interlocking mechanism referred to in the present invention is configured.

  FIG. 24 shows a cross-sectional view of the intake pipe 1 and the resonators 2 and 3 when the engine speed is relatively low (for example, about 2000 rpm). On the other hand, FIG. 23 shows a cross-sectional view of the intake pipe 1 and the resonators 2 and 3 when the engine speed is relatively high (for example, about 4000 rpm). As described above, as the engine speed increases, the frequency of each component (primary component, 1.5th order component, etc.) also increases. Therefore, in this embodiment, as the engine speed increases, the communication path C1, The actuator 5 is driven to increase the resonance frequency of each of the resonators 2 and 3 so that the length dimension of C2 is shortened. As described above, in the present embodiment, it is possible to cope with a change in the frequency of the intake noise accompanying the fluctuation of the engine speed only by moving the resonator main bodies 21 and 31. Thereby, the interlocking mechanism referred to in the present invention is configured.

  As described above, according to the present embodiment, the length of the communication passages C1 and C2 (L in the above equation (1)) is changed only by moving the resonator main bodies 21 and 31 by one drive motor 5. The ratio of the passage areas of the communication passages C1 and C2 is maintained constant. Therefore, while simplifying the configuration, not only the peak noise (noise of the first-order component frequency) and the noise of the integer multiple component frequency, but also noise of other frequencies (0.5-order component frequency and The noise reduction effect can be exhibited even for noise (such as the frequency of the 1.5th-order component frequency), and even if the frequency of the noise fluctuates, the noise reduction effect can be obtained following it.

  In the present embodiment, the number of the resonators 2 and 3 is not limited to two, and three or more resonators may be provided.

(Fifth embodiment)
Next, a fifth embodiment will be described. In the present embodiment, the volumes of the resonator chambers 21a and 31a are made variable between the resonators 2 and 3 while maintaining the volumes of the resonator chambers 21a and 31a at a predetermined ratio.

  FIG. 25 is a cross-sectional view of the intake pipe 1 and the resonators 2 and 3 in the arrangement portion of the variable frequency silencing system according to the present embodiment.

  As shown in FIG. 25, in the variable frequency silencing system according to the present embodiment, a first resonator 2 and a second resonator 3 are disposed adjacent to the extension direction of the intake pipe 1.

  As a feature of the present embodiment, the resonator bodies 21 and 31 of the resonators 2 and 3 each have a divided structure. Specifically, upper members (first members) 21b and 31b integrally connected to the intake pipe 1 and lower sides constituting the resonator chambers 21a and 31a by being assembled to the upper members 21b and 31b. Members (second members) 21c and 31c, and the lower members 21c and 31c are assembled to the upper members 21b and 31b so as to be vertically movable. That is, the capacity of the resonator chambers 21a and 31a can be changed by the vertical movement of the lower members 21c and 31c.

  In addition, the bottom area of the second resonator 3 located on the left side in FIG. 25 is set larger than the bottom area of the first resonator 2 located on the right side in FIG. Specifically, the bottom area of the second resonator 3 is set to be about four times the bottom area of the first resonator 2.

  The lower members 21c and 31c of the resonator bodies 21 and 31 in the resonators 2 and 3 are integrally connected to each other, and a horizontally extending pin 34 projects from the side surface of the lower member 31c of the second resonator 3. The pin 34 is connected to an operating rod 51 that protrudes from a drive motor 5 that is an actuator. Therefore, the lower members 21c and 31c move as the operating rod 51 advances and retreats as the drive motor 5 is driven, and the volumes of the resonator chambers 21a and 31a in the resonators 2 and 3 are changed accordingly. It is the composition which becomes. Thereby, the interlocking mechanism referred to in the present invention is configured.

  FIG. 26 shows a cross-sectional view of the intake pipe 1 and the resonators 2 and 3 when the engine speed is relatively low (for example, about 2000 rpm). On the other hand, FIG. 25 shows a cross-sectional view of the intake pipe 1 and the resonators 2 and 3 when the engine speed is relatively high (for example, about 4000 rpm). As described above, as the engine speed increases, the frequency of each component (primary component, 1.5th order component, etc.) also increases. Therefore, in this embodiment, the resonator chamber 21a, The actuator 5 is driven to increase the resonance frequency of each of the resonators 2 and 3 so that the volume of 31a is reduced. As described above, in this embodiment, it is possible to cope with a change in the frequency of the intake noise accompanying the fluctuation of the engine speed only by moving the lower members 21c and 31c of the resonator main bodies 21 and 31.

  According to this embodiment, the volume of the resonator chambers 21a and 31a of the resonators 2 and 3 can be changed only by moving the lower members 21c and 31c of the resonator bodies 21 and 31 by the single drive motor 5. The volume ratio of the resonator chambers 21a and 31a is kept constant. Therefore, while simplifying the configuration, not only the peak noise (noise of the first-order component frequency) and the noise of the integer multiple component frequency, but also noise of other frequencies (0.5-order component frequency and The noise reduction effect can be exhibited even for noise (such as the frequency of the 1.5th-order component frequency), and even if the frequency of the noise fluctuates, the noise reduction effect can be obtained following it.

(Sixth embodiment)
Next, a sixth embodiment will be described. In the present embodiment, the lengths of the communication pipes 22 and 32 are made variable while maintaining the lengths of the communication pipes 22 and 32 at a predetermined ratio between the resonators 2 and 3. .

  FIG. 27 is a cross-sectional view in which a portion of the intake pipe 1 and the resonators 2 and 3 in the arrangement portion of the variable frequency silencing system according to the present embodiment is broken.

  As shown in FIG. 27, in the variable frequency silencing system according to the present embodiment, a first resonator 2 and a second resonator 3 are disposed adjacent to each other in the extending direction of the intake pipe 1. As in the case of the fourth embodiment described above, pipe-shaped inner pipes 13 and 14 extending toward the resonators 2 and 3 are integrally formed at the connection portions of the resonators 2 and 3 in the intake pipe 1. Is formed. The passage areas of the inner pipes 13 and 14 are set to be substantially the same.

  On the other hand, the communication pipes 22 and 32 extending from the resonator main bodies 21 and 31 of the resonators 2 and 3 extend toward the inner pipes 13 and 14, respectively, and the inner pipes 13 and 14 are inserted into the communication pipes 22 and 32, respectively. It has been configured. That is, when the resonator bodies 21 and 31 of the resonators 2 and 3 move up and down together with the communication pipes 22 and 32, the communication pipes 22 and 32 move along the extending direction with respect to the inner pipes 13 and 14, respectively. The length of the communication passages C1 and C2 is substantially changed.

  As one of the features of this embodiment, the length dimension of the communication path C2 of the second resonator 3 located on the right side in FIG. 27 is the same as that of the first resonator 2 located on the left side in FIG. It is set longer than the length dimension of the passage C1.

  In the present embodiment, the length dimension of the communication paths C1 and C2 is made variable while maintaining the ratio of the lengths of the communication paths C1 and C2 constant. As a configuration for changing the length of the communication passages C1 and C2, the resonator bodies 21 and 31 of the resonators 2 and 3 are independent from each other and can be moved up and down. In addition, connecting pins 25 and 35 project from the side surfaces (front side in FIG. 27) of the resonator main bodies 21 and 31, and a link mechanism using the connecting pins 25 and 35 is configured. That is, a long operating shaft 52 is connected across the connecting pins 25 and 35, and one end of the operating shaft 52 is connected to the drive shaft of the drive motor 5. The operating shaft 52 is formed with a long hole through which the connecting pins 25 and 35 are inserted.

  Therefore, when the drive motor 5 is driven and the drive shaft rotates, the operating shaft 52 swings accordingly, and the resonator main bodies 21 and 31 move up and down in conjunction with the swing. (See arrow in FIG. 27). The connecting positions of the connecting pins 25 and 35 with respect to the operating shaft 52 are the distance from the driving shaft of the driving motor 5 to the connecting pin 25 of the first resonator 2 and the second resonator from the driving shaft of the driving motor 5. Each connection position is set so that the distance to the three connection pins 35 is about four times. For this reason, the movement amount of the second resonator 3 is always four times the movement amount of the first resonator 2, and the resonance frequency of each of the resonators 2 and 3 obtained by the above equation (1) is that of the first resonator 2. The resonance frequency is set to be about twice the resonance frequency of the second resonator 3. Thereby, the interlocking mechanism referred to in the present invention is configured.

  As described above, as the engine speed increases, the frequency of each component (primary component, 1.5th order component, etc.) also increases. Therefore, in this embodiment, as the engine speed increases, the communication path C1, The actuator 5 is driven to increase the resonance frequency of each of the resonators 2 and 3 so that the length dimension of C2 is shortened.

  As described above, according to the present embodiment, the lengths of the communication paths C1 and C2 can be changed only by moving the resonator main bodies 21 and 31 by the single drive motor 5, and these communication paths C1. , C2 length ratio is kept constant. Therefore, while simplifying the configuration, not only the peak noise (noise of the first-order component frequency) and the noise of the integer multiple component frequency, but also noise of other frequencies (0.5-order component frequency and The noise reduction effect can be exhibited even for noise (such as the frequency of the 1.5th-order component frequency), and even if the frequency of the noise fluctuates, the noise reduction effect can be obtained following it.

(Modification)
As a modification of the above-described sixth embodiment, the following configuration can be given. This example is a modification of the above link mechanism, and other configurations are the same as those of the sixth embodiment described above, so only the configuration of the link mechanism will be described here.

  As shown in FIG. 28, the connecting pins 25 and 35 projecting from the side surfaces of the resonator bodies 21 and 31 of the resonators 2 and 3 are formed with long holes through which the connecting pins 25 and 35 are inserted. Individual operating shafts 52a and 52b are connected to each other. Pinion gears 53a and 53b are attached to the other ends of these operating shafts 52a and 52b (ends opposite to the connecting portions with the connecting pins 25 and 35). The pinion gears 53a and 53b are rotatably attached to, for example, an engine cylinder head or the like. The pinion gears 53a and 53b are integrally attached to the operation shafts 52a and 52b. When the pinion gears 53a and 53b are rotated, the operation shafts 52a and 52b are pivoted about the pinion gears 53a and 53b. It swings (see arrow in FIG. 28). Each pinion gear 53a, 53b meshes with a common rack gear 54. The rack gear 54 is connected to the operating rod 51 of the drive motor 5, and the rack gear 54 moves (up and down) in the extending direction as the operating rod 51 moves forward and backward as the drive motor 5 is driven, and the pinion gear is moved. 53a and 53b are rotated. The swinging force of the operating shafts 52a and 52b due to the rotation of the pinion gears 53a and 53b is transmitted to the resonator main bodies 21 and 31 via the connecting pins 25 and 35, so that the resonator main bodies 21 and 31 individually move up and down. It is the composition to do. The length of each of the operating shafts 52a and 52b is about 4 for the length of the second operating shaft 52b connected to the second resonator 3 relative to the length of the second operating shaft 52a connected to the first resonator 2. It is set to double. For this reason, when the rack gear 54 is moved, the amount of movement of the resonator body 31 of the second resonator 3 is always about four times the amount of movement of the resonator body 21 of the first resonator 2, and each of the equations (1) is obtained. The resonance frequencies of the resonators 2 and 3 are set so that the resonance frequency of the first resonator 2 is approximately twice the resonance frequency of the second resonator 3.

-Other embodiments-
Each embodiment and the modification described above apply the present invention as a variable frequency silencing system provided in an intake system of an automobile engine. The present invention is not limited to this, and can also be applied as a variable frequency silencing system provided in an exhaust system of an automobile engine.

  Further, the present invention relates to each of the resonators 2, 3, and 7, among "the length of the communication pipes 22 and 32", "the passage area inside the communication pipes 22 and 32", and "the volume of the resonator chambers 21a and 31a". At least one of “the length of the communication pipes 22 and 32”, “the passage area inside the communication pipes 22 and 32”, and “the volume of the resonator chambers 21a and 31a” is maintained while the ratio between at least one of them is maintained constant. Any combination may be adopted as long as one is changed in conjunction with each other. In the first to third embodiments described above, the “passage area inside the communication pipes 22 and 32” is changed while maintaining the ratio of the “passage area inside the communication pipes 22 and 32” constant. . Further, in the fourth embodiment, the “length of the communication pipes 22 and 32” is changed while the ratio of “the passage area inside the communication pipes 22 and 32” is kept constant. In the fifth embodiment, the “volume of the resonator chambers 21a and 31a” is changed while the ratio of the “volume of the resonator chambers 21a and 31a” is kept constant. Further, in the sixth embodiment, the “length of the communication pipes 22 and 32” is changed while maintaining the ratio of the “lengths of the communication pipes 22 and 32” constant. In addition, the following combinations may be considered.

  -The "volume of the resonator chambers 21a, 31a" is changed while maintaining the ratio of the "passage area inside the communication pipes 22, 32" constant (V is variable with the constant ratio of S).

  -The "passage area inside the communication pipes 22 and 32" is changed while the ratio of the "lengths of the communication pipes 22 and 32" is kept constant (S is variable with a constant ratio of L).

  -The "volume of the resonator chambers 21a, 31a" is changed while maintaining the ratio of the "length of the communication pipes 22, 32" constant (V is variable with the constant ratio of L).

  -The "passage area inside the communication pipes 22 and 32" is changed while maintaining the ratio of the "volumes of the resonator chambers 21a and 31a" constant (S is variable with a constant ratio of V).

  -The "length of the communication pipes 22 and 32" is changed while maintaining the ratio of the "volumes of the resonator chambers 21a and 31a" constant (L is variable with a constant V ratio).

  Furthermore, the following combinations can be cited as a combination of a plurality of the above parameters.

  ・ In the case where the ratio of “the passage area inside the communication pipes 22 and 32” is kept constant, both “the passage area inside the communication pipes 22 and 32” and “the length of the communication pipes 22 and 32” are changed ( (S and L are variable with a constant S ratio), "Cross area of communication pipes 22 and 32" and "Volume of resonator chambers 21a and 31a" are both changed (S and V are variable with a constant S ratio) , “The length of the communication pipes 22 and 32” and “the volume of the resonator chambers 21a and 31a” are both changed (the ratio of S is constant and L and V are variable), “the passage area inside the communication pipes 22 and 32” And “the length of the communication pipes 22 and 32” and “the volume of the resonator chambers 21a and 31a” are both changed (the ratio of S is constant and S, L, and V are variable).

  In the case where the ratio of the “length of the communication pipes 22 and 32” is kept constant, the “passage area inside the communication pipes 22 and 32” and the “length of the communication pipes 22 and 32” are both changed (L S and L can be varied at a constant ratio), and "the passage area inside the communication pipes 22 and 32" and "the volume of the resonator chambers 21a and 31a" can both be changed (S and V can be varied at a constant L ratio), “The length of the communication pipes 22 and 32” and “the volume of the resonator chambers 21a and 31a” are both changed (the ratio of L is constant and L and V are variable), “the passage area inside the communication pipes 22 and 32” “The length of the communication pipes 22 and 32” and “the volume of the resonator chambers 21a and 31a” are both changed (the ratio of L is constant and S, L, and V are variable).

  ・ In the case where the ratio of the volume of the resonator chambers 21a and 31a is kept constant, both the “passage area inside the communication pipes 22 and 32” and the “length of the communication pipes 22 and 32” are changed (V (S and L are variable at a constant ratio), “the passage area inside the communication pipes 22 and 32” and “the volume of the resonator chambers 21a and 31a” are both changed (S and V are variable at a constant V ratio), “ The length of the communication pipes 22 and 32 and the volume of the resonator chambers 21a and 31a are both changed (the ratio of V is constant and L and V are variable), the passage area inside the communication pipes 22 and 32, and The length of the communication pipes 22 and 32 and the volume of the resonator chambers 21a and 31a are both changed (V, S, L, and V are variable with a constant V ratio).

  In the case where the ratio of the value (S / L) obtained by dividing the “passage area inside the communication pipes 22 and 32” by the “length of the communication pipes 22 and 32” is kept constant, "Variation of passage area" (S variable with constant S / L ratio), "Variation of communication pipes 22 and 32" (variable L with constant S / L ratio), "Resonator chamber" "Variation of 21a, 31a" (V is variable with constant S / L ratio), "Cross area of communication pipes 22, 32" and "Length of communication pipes 22, 32" (S / L ratio is constant and S and L are variable), "Variation area inside communication pipes 22 and 32" and "Volume of resonator chambers 21a and 31a" are both changed (S / L ratio is constant and S , V are variable), “the length of the communication pipes 22 and 32” and “the volume of the resonator chambers 21a and 31a”. (The ratio of S / L is constant and L and V are variable), “the passage area inside the communication pipes 22 and 32”, “the length of the communication pipes 22 and 32” and “the volume of the resonator chambers 21a and 31a” ”(Variable S, L, V with constant S / L ratio).

  In the case where the ratio of the value (S / V) obtained by dividing "the passage area inside the communication pipes 22 and 32" by "the volume of the resonator chambers 21a and 31a" is maintained constant, the "passage inside the communication pipes 22 and 32" “Area” is changed (S is variable with a constant S / V ratio), “Length of communication pipes 22 and 32” is changed (L is variable with a constant S / V ratio), “Resonator chamber 21a , 31a ”(V is variable with a constant S / V ratio),“ Cross area of communication pipes 22 and 32 ”and“ Length of communication pipes 22 and 32 ”are both changed ( S / V ratio is constant and S and L are variable), “passage area inside communication pipes 22 and 32” and “volume of resonator chambers 21a and 31a” are both changed (S / V ratio is constant and S, V V is variable), “the length of the communication pipes 22 and 32” and “resonator chambers 21a and 31a” “Volume” is changed together (L / V is variable at constant S / V ratio), “passage area inside communication pipes 22 and 32”, “length of communication pipes 22 and 32” and “resonator chamber 21a, "Volume 31a" is changed together (S / V ratio is constant and S, L, V are variable).

  In the case where the ratio of the value (L × V) obtained by multiplying the “length of the communication pipes 22 and 32” and the “volume of the resonator chambers 21a and 31a” is maintained constant, the “passage inside the communication pipes 22 and 32” “Area” is changed (S is variable with a constant ratio of L × V), “A length of communication pipes 22 and 32” is changed (L is a constant ratio of L × V, and L is variable), “Resonator chamber 21a , 31a ”(variable L with constant L × V ratio),“ path area inside the communication pipes 22 and 32 ”and“ length of the communication pipes 22 and 32 ”. (S and L are variable with a constant ratio of L × V), and “the passage area inside the communication pipes 22 and 32” and “the volume of the resonator chambers 21a and 31a” are both changed (S, V is variable), “the length of the communication pipes 22 and 32” and “the volume of the resonator chambers 21a and 31a” What is changed together (L × V is constant and L and V are variable), “the passage area inside the communication pipes 22 and 32”, “the length of the communication pipes 22 and 32”, and “the volume of the resonator chambers 21a and 31a” ”(S, L, V can be varied with a constant L × V ratio).

It is a side view showing a part of the intake pipe of the automobile engine according to the first embodiment. It is sectional drawing along the II-II line in FIG. It is a perspective view which shows the movable sleeve which concerns on 1st Embodiment. It is a figure which shows the cross section of the same location as FIG. 2 in case an engine speed is comparatively low. It is sectional drawing in the position corresponding to the VV line | wire in FIG. It is sectional drawing in the position corresponding to the VI-VI line in FIG. It is a figure which shows the cross section of the same location as FIG. 2 when an engine speed is comparatively high. It is sectional drawing in the position corresponding to the VIII-VIII line in FIG. It is sectional drawing in the position corresponding to the IX-IX line in FIG. It is the figure which cut | disconnected and developed the intake pipe and movable sleeve which concern on 1st Embodiment in the direction in alignment with the axial center. It is the figure which cut | disconnected and developed the intake pipe and movable sleeve which concern on the modification 1 of 1st Embodiment in the direction in alignment with the axial center. It is a figure which shows the cross section of the same location as FIG. 2 in the modification 2 of 1st Embodiment. It is the figure which cut | disconnected and developed the intake pipe and movable sleeve which concern on the modification 2 of 1st Embodiment in the direction in alignment with the axial center. It is a perspective view which shows the movable sleeve which concerns on 2nd Embodiment. It is a figure which shows the cross section of the same location as FIG. 2 when an engine speed is comparatively low in 2nd Embodiment. It is sectional drawing in the position corresponding to the XVI-XVI line | wire in FIG. It is sectional drawing in the position corresponding to the XVII-XVII line in FIG. It is a figure which shows the cross section of the same location as FIG. 2 in the case of an engine speed being comparatively high in 2nd Embodiment. It is sectional drawing in the position corresponding to the XIX-XIX line | wire in FIG. It is sectional drawing in the position corresponding to the XX-XX line in FIG. It is sectional drawing of an intake pipe and a resonator in case the engine speed is comparatively high in 3rd Embodiment. It is sectional drawing of an intake pipe and a resonator in case the engine speed is comparatively low in 3rd Embodiment. It is sectional drawing of an intake pipe and a resonator in case the engine speed is comparatively high in 4th Embodiment. It is sectional drawing of an intake pipe and a resonator in case the engine speed is comparatively low in 4th Embodiment. It is sectional drawing of an intake pipe and a resonator in case the engine speed is comparatively high in 5th Embodiment. It is sectional drawing of an intake pipe and a resonator in case the engine speed is comparatively low in 5th Embodiment. It is sectional drawing of the intake pipe and resonator in 6th Embodiment. It is a figure equivalent to FIG. 27 in the modification of 6th Embodiment.

Explanation of symbols

1 Intake pipe (gas distribution pipe)
2 First resonator 3 Second resonator 21, 31 Resonator body 21a, 31a Resonator chamber 21b, 31b Upper member (first member)
21c, 31c Lower member (second member)
22, 32 Communication pipes 23, 33 Sliders 23b, 33b Inclined surface 4 Movable sleeve (movable member)
5 Drive motor (actuator)
8 Movable block (pressing member)
A1, A2, A3 Intake pipe opening (intake pipe side opening)
B1, B2, B3 Movable sleeve opening (movable member side opening)
S passage area inside the communication pipe L length of the communication pipe V volume of the resonator chamber

Claims (9)

It is attached to the gas flow pipe connected to the internal combustion engine body, and uses the Helmholtz resonance principle to cope with the frequency change of the gas noise in the gas flow pipe accompanying the change in the operating state of the internal combustion engine body. In the variable frequency silencer system that reduces the gas noise of
A plurality of resonators each including a resonator body having a resonator chamber, and a communication pipe for communicating the resonator body and the gas flow pipe,
While the ratio between the resonators in at least one of the length of the communication pipe, the passage area inside the communication pipe, and the volume of the resonator chamber is maintained constant, It is characterized in that an interlocking mechanism is provided so that at least one of the length of the pipe, the passage area inside the communication pipe, and the volume of the resonator chamber is changed in conjunction with each other. Variable frequency silencer system. A variable frequency silencer system that is attached to an intake pipe of an internal combustion engine and that reduces the intake noise of that frequency using Helmholtz resonance principle so as to respond to a change in frequency of the intake sound accompanying a change in the rotational speed of the internal combustion engine In
A plurality of resonators each including a resonator body having a resonator chamber, and a communication pipe for communicating the resonator body and the intake pipe;
While the ratio between the resonators in at least one of the length of the communication pipe, the passage area inside the communication pipe, and the volume of the resonator chamber is maintained constant, It is characterized in that an interlocking mechanism is provided so that at least one of the length of the pipe, the passage area inside the communication pipe, and the volume of the resonator chamber is changed in conjunction with each other. Variable frequency silencer system. In the variable frequency silencer system according to claim 2,
The interlocking mechanism changes the “passage area inside the communication pipe” in each resonator by a single actuator,
The intake pipe is formed with a plurality of intake pipe side openings that individually communicate with the resonator chambers of the respective resonators via the communication pipes,
Inside the intake pipe, a cylindrical movable member having a plurality of movable member side openings individually facing the intake pipe side openings is assembled so as to be relatively movable, and the movable member is attached to the intake pipe. Relative movement changes the overlapping state of each intake pipe side opening and the movable member side opening facing each other, thereby changing the communication area between the openings, thereby changing the resonance frequency of each resonator. The variable frequency silencing system is configured to change the frequency of intake sound that can be reduced by the above. In the variable frequency silencer system according to claim 3,
The movable member slides in a direction along the axis of the intake pipe with respect to the intake pipe, thereby changing the overlapping state of each intake pipe side opening and each of the movable member side openings facing each other. A variable frequency silencer system configured to change a communication area. In the variable frequency silencer system according to claim 3,
The movable member rotates about the axis of the intake pipe with respect to the intake pipe, thereby changing the overlapping state of each intake pipe side opening and the movable member side opening facing each other, so that the communication area between these openings A variable frequency silencing system, characterized in that it is configured to vary. In the variable frequency silencer system according to claim 2,
The interlocking mechanism changes the “passage area inside the communication pipe” in each resonator by a single actuator,
The resonators are arranged adjacent to each other, and the communicating pipes of these resonators are slidably moved in a direction substantially perpendicular to the extending direction of the communicating pipes to change the passage area inside the communicating pipes. Are provided, and the opposite side surfaces of these sliders are formed as inclined surfaces,
The slider is disposed between the sliders and moves in the extending direction of the communication pipe, thereby applying a pressing force to the inclined surface of the slider so that the slider is substantially perpendicular to the extending direction of the communication pipe. A pressing member for sliding movement is provided,
The variable frequency silencing system is characterized in that the inclination angle of the inclined surface of each slider is set to a different inclination angle so that the sliding movement amount of the slider with respect to the movement amount of the pressing member is maintained at a constant ratio. . In the variable frequency silencer system according to claim 2,
The interlocking mechanism changes the “length of the communication pipe” in each resonator by a single actuator,
Each resonator body is configured to move integrally in the direction of contact with and away from the intake pipe as the actuator is driven, and each communicating pipe that connects the resonator body and the intake pipe moves the resonator body. While the length dimension can be changed according to the position,
The "passage area inside the communication pipe" in each resonator is set to a different area,
As the actuator is driven, each resonator body moves in the contact / separation direction with respect to the intake pipe, so that the length of the communication pipe is changed while the ratio of the “passage area inside the communication pipe” is maintained constant. A variable frequency silencing system characterized by having a configuration. In the variable frequency silencer system according to claim 2,
The interlocking mechanism changes the “volume of the resonator chamber” in each resonator by a single actuator,
Each resonator main body comprises a first member fixed to the intake pipe and a second member that makes the volume of the resonator chamber variable by moving relative to the first member,
The areas of the surfaces extending in the direction substantially orthogonal to the moving direction of the second member in each resonator are set to different areas.
As the actuator is driven, the second member of each resonator body moves relative to the first member, so that the ratio of the “resonator chamber volume” is maintained constant. A variable frequency silencing system characterized in that it is configured to be changed. In the variable frequency silencer system according to claim 2,
The interlocking mechanism changes the “length of the communication pipe” in each resonator by a single actuator,
Each resonator body is configured to be able to move independently from each other in the direction of contact with and away from the intake pipe as the actuator is driven, and the communication pipe connecting the resonator body and the intake pipe is the moving position of the resonator body. While the length dimension can be changed according to the
The length of the communication pipe in each resonator is set to a different length.
As the actuators are driven, the resonator bodies move in the direction of contact and separation independently from each other with respect to the intake pipe, so that the ratio of the “communication pipe length” is maintained constant. A variable frequency silencing system characterized in that the length dimension of "length" is changed.

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