The present invention relates to method and apparatus for controlling engine exhaust sound that is emitted from an exhaust system of vehicles such as an automobile.
There have been conventionally proposed engine exhaust sound controlling apparatuses for vehicles which reduce exhaust sound in high engine speed region as well as in low engine speed region while reducing exhaust loss in high engine speed region.
Japanese Patent Application First Publication No. 8-109815 (corresponding to U.S. Pat. Nos. 5,614,699 and 5,739,483) indicates engine exhaust sound controlling apparatus for vehicles which includes a valve for conducting changeover of exhaust paths in response to exhaust pressure, a biasing member such as a spring which biases the valve in a closing direction of the valve against the exhaust pressure, and a spring constant changing member that reduces an increment of a reaction force of the biasing member when a rotational angle of the valve exceeds a predetermined value.
Recently, it has been required to reduce back pressure and vary a level of exhaust sound in an exhaust system in response to a vehicle running state. Specifically, when a vehicle engine is started, the exhaust sound would be increased to create a powerful sound to be heard by a passenger of the vehicle. When the engine is operated in an idling region and a low engine speed region, i.e., a slow acceleration state, the exhaust sound would be reduced to ensure a silence within the interior of the vehicle. Further, when the engine is operated in a high engine speed region, i.e., a rapid acceleration state, the exhaust sound would be increased again to create a good acceleration sound to be heard by the passenger.
However, in the apparatus of the conventional art as described above, when the engine is operated in the low engine speed region, the valve is kept in the closed state by the biasing member until a pressure in a muffler reaches a certain pressure value in order to ensure the silence within the interior of the vehicle. Further, in the conventional apparatus, the valve is kept closed even in the engine starting region. Thus, the conventional art shows the exhaust system that is constructed from a viewpoint of reducing the exhaust sound. Therefore, the apparatus of the conventional art fails to produce a powerful exhaust sound in the engine starting region.
It is an object of the present invention to provide a method and apparatus for controlling exhaust sound which is capable of producing a powerful exhaust sound in an engine starting region and ensuring silence in the interior of the vehicle in a low engine speed region.
In one aspect of the present invention, there is provided a method for controlling exhaust sound from an engine which is emitted through an exhaust path, the method comprising:
a first control step of reducing a flow rate of exhaust gas that passes through the exhaust path, to a first flow rate in accordance with increase in engine speed in a first engine speed region; and
a second control step of increasing the flow rate of exhaust gas to a second flow rate in accordance with increase in engine speed in a second engine speed region in which the engine speed is higher than that in the first engine speed region.
In a further aspect of the present invention, there is provided an apparatus for controlling exhaust sound from an engine which is emitted through an exhaust path, the apparatus comprising:
a baffle plate that is disposed within the exhaust path so as to block a flow of exhaust gas in the exhaust path, the baffle plate being formed with an aperture;
a communication passage that communicates an upstream side of the baffle plate and a downstream side of the baffle plate with each other;
a valve that is so disposed as to cover a part of the aperture of the baffle plate and operated to open and close the communication passage; and
wherein the valve is operated to open the communication passage in an engine starting region, the valve is operated to close the communication passage in an idling region and a low engine speed region, and the valve is operated to open the communication passage and increase an opening of the valve as the engine speed rises in a high engine speed region.
In a still further aspect of the present invention, there is provided an apparatus for controlling exhaust sound from an engine which is emitted through an exhaust path, the apparatus comprising:
a baffle plate that is disposed within the exhaust path so as to block a flow of exhaust gas in the exhaust path, the baffle plate being formed with an aperture;
a valve that is so disposed as to cover a part of the aperture of the baffle plate, the valve being rotationally moveable relative to the baffle plate so as to be apart from the baffle plate in a direction of the flow of exhaust gas,
a biasing means for biasing the valve toward the baffle plate; and
an enclosure member that extends from the baffle plate so as to be opposed to the outer periphery of the valve when the valve is moved relative to the baffle plate,
wherein the valve has a contact position in which the valve is contacted with the baffle plate and covers the part of the aperture of the baffle plate, a small distance position in which the valve is apart from the baffle plate in the direction of the flow of exhaust gas with a first distance therebetween, an intermediate distance position in which the valve is apart from the baffle plate in the direction of the flow of exhaust gas with a second distance therebetween which is larger than the first distance, and a large distance position in which the valve is apart from the baffle plate in the direction of the flow of exhaust gas with a third distance therebetween which is larger than the first distance and the second distance, and
wherein when the valve is placed in the contact position, the valve cooperates with the baffle plate to define an opening between the outer periphery of the valve and a periphery of the aperture of the baffle plate,
when the valve is placed in the small distance position, the valve cooperates with the enclosure member to define a first clearance between the outer periphery of the valve and an opposing surface of the enclosure member that is opposed to the outer periphery of the valve,
when the valve is placed in the intermediate distance position, at least a part of the outer periphery of the valve is substantially contacted with the opposing surface of the enclosure member, and
when the valve is placed in the large distance position, the valve cooperates with the enclosure member to define a second clearance between the outer periphery of the valve and the opposing surface of the enclosure member, and the second clearance is increased as the third distance between the valve and the baffle plate becomes larger.
Referring to
Baffle plate 1 includes a generally rectangular-shaped aperture la as shown in
Valve 2 is rotationally moveable relative to baffle plate 1 so as to be apart from baffle plate 1 in a direction of the flow of exhaust gas. Valve 2 is operated to open and close a communication passage which allows fluid communication between an upstream side expansion chamber and a downstream side expansion chamber which are disposed on an upstream side and a downstream side of baffle plate 1 with respect to the flow of exhaust gas in the exhaust path.
Specifically, valve 2 is a generally rectangular-shaped plate member. Valve 2 includes curved end portion 2a at one end thereof, a pair of support portions 2b disposed on opposite sides of curved end portion 2a and planar valve body 2c connected with curved end portion 2a. Valve 2 has end peripheral surface 2d and two side peripheral surfaces which are disposed on an outer periphery of valve body 2c. End peripheral surface 2d is located at an opposite end of valve 2, namely, at a lower end of valve 2 when viewed in
Curved end portion 2a is so curved as to have a predetermined radius that extends from a central axis of valve shaft 4. An outer circumferential surface of curved end portion 2a is opposed to baffle plate 1 and substantially in slide contact with baffle plate 1 during the rotational movement of valve 2 about valve shaft 4.
Torsion spring 5 is mounted to valve shaft 4 and biases valve body 2c of valve 2 toward baffle plate 1. When valve 2 is biased by torsion spring 5 so as to be placed in a position shown in
Aperture 1a is so configured as to be partially covered by valve body 2c of valve 2. Specifically, aperture 1a extends in the axial direction of valve shaft 4 so as to have an opening width equal to or slightly smaller than a width of valve 2 as shown in
Valve guides 6, 7 and 8 serve as an enclosure member that extends from baffle plate 1 so as to surround the outer periphery of valve 2. Valve guides 6, 7 and 8 cooperate with baffle plate 1 and valve 2 to define the communication passage that allows the fluid communication between the upstream side expansion chamber disposed on the upstream side of baffle plate 1 and the downstream side expansion chamber disposed on the downstream side of baffle plate 1.
Specifically, side valve guides 6 and 7 are disposed on both sides of valve 2 in an opposed and spaced relation thereto in the axial direction of valve shaft 4. Side valve guides 6 and 7 are formed into a plate shape and extend from the downstream side surface of baffle plate 1 in the direction of the flow of exhaust gas, namely, in a rotational direction of valve 2, so as to be opposed to the side peripheral surfaces of valve 2 during the rotational movement of valve 2 about valve shaft 4. End valve guide 8 is interposed between side valve guides 6 and 7 on the side of the other end of valve 2.
End valve guide 8 is opposed to and spaced from end peripheral surface 2d of valve 2 in the direction perpendicular to the axial direction of valve shaft 4. End valve guide 8 uprightly extends from the downstream side surface of baffle plate 1 and has a predetermined height. End valve guide 8 extends along the bottom-linear part of the generally rectangular-shaped periphery of aperture 1a in the axial direction of valve shaft 4. End valve guide 8 has clearance forming surface 8a and contact surface 8b on a side of valve 2 and valve shaft 4, namely, on an upper side of end valve guide 8 in
Valve 2 serves as a control valve that controls the flow of exhaust gas passing through the exhaust path. An operation of valve 2 is explained hereinafter with reference to
Next, as shown in
When the external force that is applied to valve 2 in the opening direction is increased, valve 2 is further rotated about valve shaft 4 against the biasing force of torsion spring 5. Valve 2 is placed in position B and then moved from position B to position C. At this time, the rotation amount of valve 2 becomes intermediate and the distance between baffle plate 1 and valve body 2c in the direction of the flow of exhaust gas becomes intermediate. During the rotational movement of valve 2 from position B to position C, at least a part of the outer periphery of valve 2, namely, end peripheral surface 2d of valve 2, is in substantially contact, namely, slide contact, with contact surface 8b of end valve guide 8. Therefore, the upstream side expansion chamber on the upstream side of baffle plate 1 can be prevented from being communicated with the downstream side expansion chamber on the downstream side of baffle plate 1. Thus, during the rotational movement of valve 2 from position B to position C, valve 2 is restrained from the first open state and kept in a closing state in which there is the intermediate distance between valve body 2c and baffle plate 1 in the direction of the flow of exhaust gas and the fluid communication between the upstream side expansion chamber and the downstream side expansion chamber which are disposed on the upstream and downstream sides of baffle plate 1 can be substantially prevented.
When the external force is further increased, valve 2 is further rotated about valve shaft 4 against the biasing force of torsion spring 5 and moved from position C in the opening direction to thereby be apart from end valve guide 8. At this time, the rotation amount of valve 2 becomes large and the distance between baffle plate 1 and valve body 2c in the direction of the flow of exhaust gas becomes large. End peripheral surface 2d of valve 2 is apart from contact surface 8b of end valve guide 8, and there is generated a clearance between end peripheral surface 2d and contact surface 8b. Therefore, the upstream side expansion chamber on the upstream side of baffle plate 1 can be communicated again with the downstream side expansion chamber on the downstream side of baffle plate 1 through the clearance between end peripheral surface 2d and contact surface 8b. Thus, when valve 2 is further rotationally moved from position C in the opening direction, valve 2 is in a second open state in which the fluid communication between the upstream side expansion chamber and the downstream side expansion chamber which are disposed on the upstream and downstream sides of baffle plate 1 can be re-established through the clearance between end peripheral surface 2d and contact surface 8b. The clearance is increased as the distance between baffle plate 1 and valve body 2c in the direction of the flow of exhaust gas becomes larger. Further, in the second open state of valve 2, the opening of valve 2 and the angular position of valve 2 with respect to baffle plate 1, varies in accordance with the rotation amount of valve 2 and the distance between baffle plate 1 and valve body 2c in the direction of the flow of exhaust gas. That is, as the rotation amount of valve 2 and the distance between baffle plate 1 and valve body 2c in the direction of the flow of exhaust gas increases, the opening of valve 2 becomes larger.
Opening 10 and the clearance between baffle plate 1, valve body 2c and valve guides 6, 7 and 8 constitute the communication passage between the upstream side expansion chamber disposed on the upstream side of baffle plate 1 and the downstream side expansion chamber disposed on the downstream side of baffle plate 1. That is, the communication passage is formed by the aperture-forming rim of baffle plate 1, end peripheral surface 2d of valve body 2c, opposed surfaces of side valve guides 6 and 7 opposed in the axial direction of valve shaft 4, and clearance forming surface 8a and contact surface 8b of end valve guide 8.
Referring to
Inlet tube 24 extends into second expansion chamber 23 through an upstream end wall of muffler 20, first expansion chamber 22 and baffle plate 21. Inlet tube 24 has one end that outwardly projects from the upstream end wall of muffler 20 and is connected to the engine through an exhaust pipe, not shown. Inlet tube 24 has the other end that is opened within second expansion chamber 23. Inlet tube 24 serves as a first communication tube that communicates second expansion chamber 23 with the engine. Inlet tube 24 introduces the exhaust gas from the engine into second expansion chamber 23. Pass-through tube 25 extends through baffle plate 21 and communicates first expansion chamber 22 and second expansion chamber 23 with each other. Pass-through tube 25 has one end that is opened within second expansion chamber 23 and the other end that is opened within first expansion chamber 22. Tail tube 26 extends from first expansion chamber 22 to an outside of muffler 20 through baffle plate 21, second expansion chamber 23 and a downstream end wall of muffler 20. Tail tube 26 has one end that is opened within first expansion chamber 22 and the other end that outwardly projects from the downstream end wall of muffler 20 and is exposed to atmospheric air. Tail tube 26 serves as a second communication tube that communicates first expansion chamber 22 with atmospheric air. First expansion chamber 22 and second expansion chamber 23 are larger in cross-sectional area than inlet tube 24, pass-through tube 25 and tail tube 26.
Baffle plate 21 has generally rectangular-shaped aperture 21a that is disposed parallel with pass-through tube 25. The valve structure described above with reference to
In thus constructed muffler 20, exhaust sound generated from the engine is controlled in accordance with an operating condition of the engine. The exhaust sound is emitted to atmospheric air via a first route, a second route or both of the first and second routes in accordance with the engine operating condition. The first route is indicated by arrow A in
Specifically, in an engine starting region in which a flow of exhaust gas from the engine starts at zero and increases, the exhaust sound from the engine is emitted from tail tube 26 to atmospheric air via the first route indicated by arrow A in
Further, when the engine speed is raised up to a predetermined engine speed which is in the idling region, valve 2 is rotationally moved to position B shown in
When the engine speed is raised up to the low engine speed region in which the engine speed is higher than in the idling region, namely, when the engine is operated in a slow acceleration state, and the engine is maintained in the low engine speed region, the valve-forward pressure is further increased with the engine speed raise. Due to the increase in the valve-forward pressure, valve 2 is rotationally moved from position B to position C shown in
When the engine speed is further raised up to a high engine speed region in which the engine speed is higher than in the low engine speed region, namely, when the engine is operated in a rapid acceleration state, the valve-forward pressure is further increased due to an increase in the flow of exhaust gas from the engine. Valve 2 is further rotationally moved away from position C and placed in the second open state. In the second open state, end peripheral surface 2d of valve 2 becomes out of contact with contact surface 8b of end valve guide 8 so that there is generated a clearance therebetween. Therefore, the exhaust sound from the engine is emitted from tail tube 26 to atmospheric air via both the first route and the second route. Thus, even when the flow of exhaust gas is increased, increase in pressure loss can be suppressed to thereby enhance the engine output in the high engine speed region.
Referring
That is, in the exhaust sound controlling apparatus of the present invention, valve 2 is constructed to be operated corresponding to the engine speed. The spring force (spring constant) of torsion spring 5, the opening of valve 2 and the opening area of aperture 1a, 21a may be suitably set to operate valve 2 corresponding to the engine speed as described above. Alternatively, the valve-forward pressure (the exhaust pressure in second expansion chamber 23) may be suitably set to operate valve 2 corresponding to the engine speed.
On the basis of the relationships as explained above, the construction of the exhaust sound controlling apparatus of the present invention is appropriately designed. For instance, the spring constant (the biasing force) of torsion spring 5 can be set such that valve 2 is rotationally moveable from position A to the position immediately before position B against the valve-forward pressure in the engine starting region, valve 2 is rotationally moveable from position B to position C against the valve-forward pressure in the idling region and the low engine speed region, and valve 2 is rotationally moveable beyond and away from position C in the high engine speed region, as shown in
Owing to suitably setting the spring constant of torsion spring 5 as described above, the rotational movement of valve 2 from position B and position C can be ensured even when the flow of exhaust gas pulses in the idling region and the low engine speed region and the rotational movement of valve 2 pulses along with the pulse of the flow of exhaust gas. Valve 2, therefore, can be prevented from coming into contact with baffle plate 1, 21. As a result, when the engine is operated in the idling region and the low engine speed region, it is possible to suppress occurrence of striking noise which would be caused due to the contact of valve 2 with baffle plate 1, 21, and maintain a silence within the interior of the vehicle.
The exhaust sound controlling apparatus of the embodiment can perform the following function and effect. In the engine starting region, valve 2 is placed in the first open state in which exhaust gas emitted from the engine is permitted to pass through the communication passage in the second route B and thereby flow in the exhaust path via both the first route A and the second route B as shown in
Further, with the provision of the simple valve structure as described above, the exhaust sound control can be suitably performed depending on the engine speed as explained above. Further, the exhaust sound can be controlled by setting the spring constant (the biasing force) of torsion spring 5 as explained above.
Furthermore, curved end portion 2a of valve 2 serves as a gas leakage inhibiting portion that prevents the exhaust gas and the exhaust sound from leaking from curved end portion 2a toward the downstream side of baffle plate 1 during the rotational movement of valve 2. Valve 2 is supported at curved end portion 2a relative to baffle plate 1, and the outer circumferential surface of curved end portion 2a is substantially in contact (slide contact) with baffle plate 1 during the rotational movement of valve 2. Therefore, while valve 2 is rotationally moved, the exhaust gas and the exhaust sound can be prevented from leaking from curved end portion 2a toward the downstream side of baffle plate 1.
Referring to
Gas leakage inhibiting member 11 is disposed on the downstream side surface of baffle plate 1 and located on a side of one end portion 2e of valve body 2c. Gas leakage inhibiting member 11 extends parallel to valve shaft 4 or one end portion 2e of valve body 2c, namely, an upper end periphery of valve 102 when viewed in
As shown in
During the rotational movement of valve 102, the exhaust gas and the exhaust sound can be prevented from leaking from one end portion 2e of valve 102 at which valve 102 is supported relative to baffle plate 1 through gas leakage inhibiting member 11, toward the downstream side of baffle plate 1. In view of this effect of gas leakage prevention, it is preferred that the other strip portion 11b of gas leakage inhibiting member 11 is curved in conformity with a locus of the tip end of one end portion 2e of valve 102 which is drawn during the rotational movement of valve 102.
Valve 102 has the same operating positions and operating states as those of valve 2 as shown in
Referring to
Inlet tube 46 extends into second expansion chamber 44 through an upstream end wall of muffler 40, first expansion chamber 43 and first baffle plate 41. Inlet tube 46 has one end that outwardly projects from the upstream end wall of muffler 40 and is connected to the engine through an exhaust pipe, not shown. Inlet tube 46 has the other end that is opened within second expansion chamber 44. Inlet tube 46 introduces the exhaust gas from the engine into second expansion chamber 44.
First pass-through tube 47 is disposed within muffler 40 coaxially with inlet tube 46. First pass-through tube 47 extends from second expansion chamber 44 into third expansion chamber 45 through second baffle plate 42 and communicates second expansion chamber 44 and third expansion chamber 45 with each other. First pass-through tube 47 has one end that is opened within second expansion chamber 44 and the other end that is opened within third expansion chamber 45 with each other. Second pass-through tube 48 extends through second baffle plate 42 in parallel with first pass-through tube 47. Second pass-through tube 48 has one end that is opened within third expansion chamber 45 and the other end that is connected with one side surface of first baffle plate 41 which is exposed to second expansion chamber 44.
First baffle plate 41 has generally rectangular-shaped aperture 41a. Second pass-through tube 48 is disposed coaxially with aperture 41a so as to communicate third expansion chamber 45 with aperture 41a. Third expansion chamber 45 and first expansion chamber 43 are communicated with each other through aperture 41a and second pass-through tube 48. The valve structure shown in
First tail tube 49 extends from first expansion chamber 43 to an outside of muffler 40 through first baffle plate 41, second baffle plate 42, second expansion chamber 44, third expansion chamber 45 and a downstream end wall of muffler 40. First tail tube 49 has one end that is opened within first expansion chamber 43 and the other end that outwardly projects from the downstream end wall of muffler 40 and is exposed to atmospheric air. Second tail tube 50 extends from second expansion chamber 44 to the outside of muffler 40 through second baffle plate 42, third expansion chamber 45 and the downstream end wall of muffler 40. Second tail tube 50 has one end that is opened within second expansion chamber 44 and the other end that outwardly projects from the downstream end wall of muffler 40 and is exposed to atmospheric air. Each of expansion chambers 43, 44, 45 is larger in cross-sectional area than inlet tube 46, pass-through tubes 47, 48 and tail tubes 49, 50. In the construction of muffler 40, the exhaust path extends through first inlet tube 46, second expansion chamber 44, second tail tube 50, first pass-through tube 47, third expansion chamber 45, second pass-through tube 48, first expansion chamber 43, first tail tube 49 and the communication passage between first expansion chamber 43 and third expansion chamber 45.
In thus constructed muffler 40, exhaust sound generated from the engine is controlled depending on an operating condition of the engine. The exhaust sound is emitted to atmospheric air via a first route indicated by arrow A in
Specifically, in the engine starting region, the exhaust sound from the engine is emitted from second tail tube 50 to atmospheric air via the first route indicated by arrow A in
Further, when the engine speed is raised up to the idling region, valve 2 or 102 is rotationally moved to position B shown in
When the engine speed is further raised up to the low engine speed region and maintained in the low engine speed region, the valve-forward pressure is further increased with raising of the engine speed. Due to the increase in the valve-forward pressure, valve 2 or 102 is rotationally moved from position B to position C shown in
Further, when the engine speed is raised up to the high engine speed region, the valve-forward pressure is further increased due to an increase in the flow of exhaust gas from the engine. Valve 2 or 102 is further rotationally moved away from position C shown in
Next, a method for controlling exhaust sound from the engine which is emitted through the exhaust path, of the embodiment is explained. The method includes a first control step of reducing a flow rate of exhaust gas that passes through the exhaust path, to a first flow rate in accordance with increase in engine speed in a first engine speed region, and a second control step of increasing the flow rate of exhaust gas to a second flow rate in accordance with increase in engine speed in a second engine speed region in which the engine speed is higher than the engine speed in the first engine speed region. The method further includes a third control step of reducing the flow rate of exhaust gas to a third flow rate that is lower than the first flow rate and the second flow rate in a third engine speed region between the first engine speed region and the second engine speed region. The engine speed in the first engine speed region includes an engine speed in an engine starting region. The engine speed in the second engine speed region includes an engine speed in a high engine speed region. The engine speed in the third engine speed region includes an engine speed in an idling region and an engine speed in a low engine speed region.
The method for controlling exhaust sound can perform the following effects. In the engine starting region, exhaust gas emitted from the engine is permitted to pass through the exhaust path so that powerful exhaust sound can be created. In the idling region and the low engine speed region, the flow of exhaust gas is reduced so that a silence within the interior of the vehicle can be ensured. In the high engine speed region, the flow of exhaust gas is permitted to pass through the exhaust path and the flow rate of exhaust gas is increased as the engine speed becomes higher. As a result, increase in pressure loss can be suppressed.
This application is based on prior Japanese Patent Application No. 2007-098526 filed on Apr. 4, 2007. The entire contents of the Japanese Patent Application No. 2007-098526 are hereby incorporated by reference.
Although the invention has been described above by reference to a certain embodiment of the invention and modifications of the embodiment, the invention is not limited to the embodiment and the modifications described above. Variations of the embodiment and the modifications described above will occur to those skilled in the art in light of the above teachings. The scope of the invention is defined with reference to the following claims.
Number | Date | Country | Kind |
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2007-098526 | Apr 2007 | JP | national |