CN104213955A - Dual-mode silencer for internal combustion engine exhausting system - Google Patents

Dual-mode silencer for internal combustion engine exhausting system Download PDF

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Publication number
CN104213955A
CN104213955A CN201310217269.0A CN201310217269A CN104213955A CN 104213955 A CN104213955 A CN 104213955A CN 201310217269 A CN201310217269 A CN 201310217269A CN 104213955 A CN104213955 A CN 104213955A
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CN
China
Prior art keywords
room
silencing apparatus
dividing plate
operating mode
valve
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Pending
Application number
CN201310217269.0A
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Chinese (zh)
Inventor
洛朗·马洛潘尼塞
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Faurecia Emissions Control Technologies Development Shanghai Co Ltd
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Faurecia Emissions Control Technologies Development Shanghai Co Ltd
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Application filed by Faurecia Emissions Control Technologies Development Shanghai Co Ltd filed Critical Faurecia Emissions Control Technologies Development Shanghai Co Ltd
Priority to CN201310217269.0A priority Critical patent/CN104213955A/en
Priority to KR1020130155217A priority patent/KR20140141416A/en
Publication of CN104213955A publication Critical patent/CN104213955A/en
Pending legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N1/00—Silencing apparatus characterised by method of silencing
    • F01N1/02—Silencing apparatus characterised by method of silencing by using resonance
    • F01N1/023—Helmholtz resonators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N1/00—Silencing apparatus characterised by method of silencing
    • F01N1/08—Silencing apparatus characterised by method of silencing by reducing exhaust energy by throttling or whirling
    • F01N1/084—Silencing apparatus characterised by method of silencing by reducing exhaust energy by throttling or whirling the gases flowing through the silencer two or more times longitudinally in opposite directions, e.g. using parallel or concentric tubes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N13/00—Exhaust or silencing apparatus characterised by constructional features ; Exhaust or silencing apparatus, or parts thereof, having pertinent characteristics not provided for in, or of interest apart from, groups F01N1/00 - F01N5/00, F01N9/00, F01N11/00
    • F01N13/08—Other arrangements or adaptations of exhaust conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N2470/00—Structure or shape of gas passages, pipes or tubes
    • F01N2470/02—Tubes being perforated
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N2470/00—Structure or shape of gas passages, pipes or tubes
    • F01N2470/14—Plurality of outlet tubes, e.g. in parallel or with different length
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N2490/00—Structure, disposition or shape of gas-chambers
    • F01N2490/02—Two or more expansion chambers in series connected by means of tubes
    • F01N2490/06—Two or more expansion chambers in series connected by means of tubes the gases flowing longitudinally from inlet to outlet in opposite directions

Abstract

The invention provides a dual-mode silencer for an internal combustion engine exhausting system. The dual-mode silencer comprises a housing, a first end cover, a second end cover, an input pipe, multiple output pipes and a control device, wherein the first end cover and the second end cover are respectively located at two ends of the housing, the input pipe outward extends from the first end cover so as to collect exhausted gas from an internal combustion engine, the multiple output pipes outward extend from the second end cover, and the multiple output pipes, the input pipe and the housing of the silencer form multiple exhausting paths. The control device is arranged on one of the multiple output pipes and used for operably switching the silencer to be in a first operating mode or a second operating mode according to one or more conditions of the internal combustion engine. The corresponding exhausting path is defined in each operating mode, and at least most of the exhausted gas is transferred through the exhausting paths. The exhausting path corresponding to the first operating path is different from the exhausting path corresponding to the second operating path.

Description

The double mode silencing apparatus of internal combustion engine exhaust system
Technical field
The present invention relates to a kind of for the silencing apparatus in internal combustion engine exhaust system, internal-combustion engine can be turbosupercharged engine also can be naturally aspirated engine.
Background technique
For reducing the noise that internal-combustion engine produces, its vent systems adopts silencing apparatus.Silencing apparatus generally includes a housing, at least one supplying tube be used for from internal-combustion engine receive exhaust and at least one output tube by exhaust emissions to air.Sometimes, for obtaining balance better between acoustic efficiency/back pressure, need to provide two or more exhaust pathway.A subject matter of internal-combustion engine (especially turbosupercharged engine) is the pressure of the silencing apparatus inside be connected with motor, and---namely alleged exhaust back pressure---produces resistance to the exhaust of discharging motor.The resistance caused by back pressure adversely have impact on performance and the efficiency of internal-combustion engine, if particularly when motor is turbosupercharged engine.
Therefore, there will be the new challenge different from the conventional Research idea of natural intake engine when the vent systems of research and development high-performance high efficiency turbosupercharged engine.One of them is exactly that back pressure must remain on the level more much lower than the back pressure of natural intake engine, this is not only the situation (more than 6000 turns per minute) for high rotating speed (rmp) per minute, and also should keep low back pressure for low medium speed scope (per minute 1000 forward between 6000 turns), thus ensure that turbogenerator reaches desirable performance and efficiency.
In order to reach the target making internal-combustion engine keep low back pressure, some design have employed passive type " self-driven " valve, but this can produce relatively high back pressure when the slow-speed of revolution or low quality flow rate (mass flow rate).And when high rotating speed, strengthen along with the pressure in silencing apparatus and make passive type " self-driven " valve open, thus back pressure is made to keep low-level.This design opens valve by the high pressure in silencing apparatus, solves the back pressure problems under middle high rotating speed.But when the slow-speed of revolution, valve closing, this produces high back pressure in silencing apparatus.
Although some silencing apparatus solution employs multi-mode in vent systems in current convention, those patterns are arranged in multiple vent systems or are arranged in multiple silencing apparatus, instead of in a silencing apparatus.This design in multiple vent systems or multiple silencing apparatus can increase obviously vent systems complexity and due to vehicle space limit and the problem installed brought.Therefore, market demand is a kind of simple, compact and have the silencing apparatus scheme of identical or better performance and efficiency.
The vent systems of an automobile is applied in the example of double mode silencing apparatus, the exhaust pathway having use two acoustical absorptivities different reduces the example of exhaust noise level.In another exemplary arrangement, provide a bypass, separate the portion discharge of discharging from silencing apparatus when large mass flowrate, to discharge the back pressure of silencing apparatus inside.Be used for controlling by the tolerance separated by a pressure-actuated passive type control valve.As described above, this design when motor is in slow-revving, because passive type valve closing makes its back pressure higher.
U. S. Patent 4913260 discloses the device of a kind of operator of being supplied in order to control to reduce the noise that in vent systems, air-flow produces.In this type of design, because control signal can not reflect in-engine rotating speed or exhaust back pressure level, so the scheme keeping low back pressure when low engine speeds can not be used as.
Therefore, the silencing apparatus scheme of a kind of acoustical absorptivity had at low speed and middle high rotating speed and the low back pressure that can keep internal-combustion engine is needed.
Summary of the invention
In order to overcome the problems referred to above, the invention provides a kind of double mode silencing apparatus for internal combustion engine exhaust system, it is characterized in that silencing apparatus comprises: housing; First end cap and the second end cap, it lays respectively at housing two ends, is formed between suppressor case together with housing; Supplying tube, stretches out to receive exhaust from internal-combustion engine from the first end cap; Multiple output tube, stretches out from the second end cap and form multiple exhaust pathway together with between supplying tube and suppressor case; And control gear, be provided on one of them output tube of multiple output tube, for operationally silencing apparatus being switched to the first operating mode or the second operating mode according to one or more conditions of internal-combustion engine.Each operating mode limits corresponding exhaust pathway, and at least major part of exhaust is through exhaust pathway discharge thus.Exhaust pathway corresponding to the first operating mode is different from the exhaust pathway corresponding to the second operating mode.
In a preferred embodiment, the feature of silencing apparatus is that the first operating mode is designed to abate the noise when internal-combustion engine low cruise back pressure is maintained below the first predetermined target value simultaneously; The second operating mode in two operating modes is designed to abate the noise when internal-combustion engine runs with high speed and back pressure is maintained below the second predetermined target value simultaneously; Wherein the first predetermined target value can be identical value with the second predetermined target value, also can be different value.First and second predetermined target value may be defined as the back pressure value preset for given mass flowrate or is defined as other that automobile industry is commonly used, irrelevant with exhaust parameter value: be equal to cross section (Equivalent Section) Se, loss coefficient (Loss Coefficient) K or Nissan side reaction coefficient (Nissan α Coefficient).For ease of understanding, the relation be equal between cross section and back pressure is illustrated by lower example:
dP = Q 2 2 * ρ * Se total 2
dP ≈ 96 2 2 * 0.55 * 5.2 2 = 310 mbars
Wherein:
DP represents the back pressure that unit is mbar, and the back pressure in this example is 310mbar;
Q represents the mass flowrate of motor, and unit is g/s;
ρ represents the gas density at given air pressure and temperature, is 0.55 in this example;
The equivalent cross section of Se representative, unit is cm 2.
Silencing apparatus in the present invention passes through to share a sound cavity volume (acousticvolume) under two operating modes, thus makes it under low, middle and high frequency rate, all have high acoustical absorptivity.By the present invention, the acoustical absorptivity of motor when raising speed and slow down all can be greatly improved, and required sound cavity volume can be made to reduce.
These features of the present invention and other features are understood further by following explanation and accompanying drawing.
Accompanying drawing explanation
With reference to the accompanying drawings and describe in detail preferred implementation the present invention is further described.
Figure 1 shows that the schematic perspective view of the silencing apparatus according to one embodiment of the present invention.
Fig. 2 is the schematic perspective view after the silencing apparatus shown in Fig. 1 removes suppressor case and optional fiber.
Fig. 3 is the internal structure schematic diagram of silencing apparatus shown in Fig. 1.
Fig. 4 is the exhaust pathway schematic diagram of silencing apparatus of the present invention when being operated in the first operating mode (" pure Helmholtz (Helmholtz) pattern ").
Acoustic efficiency when Fig. 5 illustrates that the silencing apparatus of Fig. 1 is operated in two mode of executions (" pure Helmholtz's pattern " and " band leak Helmholtz's pattern ") of the first operating mode compares.
Fig. 6 is the exhaust pathway schematic perspective view of silencing apparatus of the present invention when being operated in a mode of execution (" pure Helmholtz's pattern ") of the first operating mode.
Fig. 7 is the sound equivalence (acoustic equivalence) of silencing apparatus of the present invention when being operated in a mode of execution (" pure Helmholtz's pattern ") of the first operating mode or lumped model (lumped model) schematic diagram.
Fig. 8 is the exhaust pathway schematic diagram of silencing apparatus of the present invention when being operated in the second operating mode (" interference (adding absorption) pattern ").
Fig. 9 is the acoustic efficiency figure of silencing apparatus of the present invention when being operated in the second operating mode (" interference (adding absorption) pattern ").
Figure 10 is two the exhaust pathway schematic perspective view of silencing apparatus of the present invention when being operated in the second operating mode (" interference (adding absorption) pattern ").
Figure 11 is the sound equivalent schematic of silencing apparatus of the present invention when being operated in the second operating mode (" interference (adding absorption) pattern ").
Figure 12 illustrates the comprehensive acoustic efficiency that silencing apparatus of the present invention reaches.
Figure 13 is valve location in the present invention and the binary function relation schematic diagram between control signal (engine speed).
Figure 14 is valve location in the present invention and the linear functional relation schematic diagram between control signal (engine speed).
Embodiment
Figure 1 shows that a mode of execution of silencing apparatus of the present invention.As shown in Figure 1, silencing apparatus 100 has a supplying tube 101 and two output tubes 102 and 103.Supplying tube 101 provides the connection with the vehicle motor being provided with silencing apparatus 100, is used for receiving exhaust.Outlet pipe 102 is provided with a control gear 104.As shown in Figure 1, housing 105 is closed by two end caps 106 and 107 and to be formed between suppressor case 120.
Fig. 2 is the schematic perspective view after silencing apparatus shown in Fig. 1 removes the housing of silencing apparatus and optional fiber, to be clearly shown that the internal structure of silencing apparatus.As shown in Figure 2, silencing apparatus has three dividing plates 108,109 and 110.These dividing plates together with two end caps 106,107 by suppressor case between 120 be divided into four rooms: be the first Room 201 between end cap 106 and dividing plate 108, it is the second Room 202 between dividing plate 108 and dividing plate 109, being the 3rd Room 203 between dividing plate 109 and dividing plate 110, is fourth ventricle 204 between dividing plate 110 and end cap 107.As shown in Figure 2, only have dividing plate 108 to be to establish foraminate in three dividing plates 108,109 and 110, make to can be between room 201 with other room 202,203 and 204 sound insulation.Dividing plate 109 and 110 there is aperture, makes room 202, be not sound insulation between 203 and 204.Therefore, three rooms 202,203 and 204 form a large sound cavity volume.
This silencing apparatus also comprises a recurrent canal 111(and will discuss in detail below) and a control gear 104 being arranged at output tube 102.Control gear 104 runs under can controlling the pattern of silencing apparatus in two operating modes.In Fig. 1 to Figure 14, a mode of execution of this control gear 104 is depicted as a valve, and this valve can by opening or closing the operating mode switching silencing apparatus.But, it is apparent to those skilled in the art that the control gear also can applying other form in the present invention, as long as this control gear can control/by the switching between control realization silencing apparatus operating mode.
Fig. 3 show further the internal structure of silencing apparatus shown in Fig. 1, comprises a supplying tube, two output tubes, a recurrent canal and multiple dividing plates.As shown in Figure 3, supplying tube 101 stretches out to provide the connection with the motor being provided with this silencing apparatus to silencing apparatus by end cap 106.Supplying tube 101 ends at room 204(added partition 112 through dividing plate 108,109 and 110 and will discuss in another embodiment) in.Output tube 102 originates in room 202, through dividing plate 109 and 110, and finally extends to the outside of between suppressor case 120 from end cap 107.Control gear 104 is arranged at the end close to output tube 102.In this embodiment, control gear 104 is valve 104.Output tube 103 originates in room 201, through dividing plate 108,109 and 110, and finally extends to the outside of between suppressor case 120 from end cap 107.Recurrent canal 111 originates in room 202, through dividing plate 109 and 110, ends in room 204.
In Fig. 3, the part of supplying tube 101 in room 201 is provided with one group of aperture 303.The part of recurrent canal 111 in room 203 is provided with aperture 304.By two ends and the aperture 304 thereof of recurrent canal 111, recurrent canal 111 constitutes the acoustic path between room 202,203 and 204, and sound between these rooms can be flowed.Similarly, as shown in Figure 3, output tube 102 and 103 appropriate section respective in room 203 can be provided with the aperture 305 and 306 of oneself.Aperture on output tube 102 and 103 is used to mounting sleeve resonator.The part being provided with aperture 305 and 306 on output tube 102 and 103 is used for mounting sleeve resonator to reduce high-frequency noise (can describe in detail this) below.But output tube 102 and 103 does not establish aperture and the mode of execution of mounting sleeve resonator does not deviate from principle of the present invention yet.In an Alternate embodiments, another dividing plate 112 can be set between dividing plate 110 and end cap 107, make output tube 102 and 103 through dividing plate 112.Like this, as shown in Figure 3, dividing plate 110 and the dividing plate 112 inserted form a room 205, and the dividing plate 112 inserted and end cap 107 form room 206.In another Alternate embodiments, at least one output tube is provided with high frequency sleeve pipe resonator.As shown in Figure 3, output tube 102 is provided with high frequency sleeve pipe resonator S1+M1, and on output tube 103, is provided with high frequency sleeve pipe resonator S2+M2.Wherein, the diameter of sleeve pipe M1 and M2 is slightly less than the respective diameters of high-frequency reonsator S1 and S2, closely cooperates respectively to make sleeve pipe M1 and M2 with resonator S1 and S2.Potential " sharp whistle noise "/" whistle " can by establishing the method for aperture to solve on resonator S1 and S2.In addition, by increasing the quantity of aperture on resonator S1 and S2, can realize further disturbing with the other parts of silencing apparatus.Preferably, above-mentioned high frequency sleeve pipe resonator is stainless steel high frequency sleeve pipe resonator.
Two kinds of operating modes according to silencing apparatus of the present invention are discussed below.By opening or closing valve 104, operationally select the one in two kinds of operating modes according to silencing apparatus of the present invention.
Fig. 4 is the exhaust pathway schematic diagram of silencing apparatus of the present invention when being operated in the first mode of execution (" the pure Helmholtz " design or " pure Helmholtz's pattern ") of the first operating mode, comprising Helmholtz chamber and Helmholtz's neck.Under this " pure Helmholtz's pattern ", the valve 104 of output tube 102 end is in closed condition.This Model Design is run when motor is at low-speed running.In such a mode, because in this embodiment dividing plate 108 does not establish aperture, so dividing plate 108 120 will be divided into two different intervals between suppressor case: room 201 is separately first interval, room 202,203 and 204 forms second interval.In the present embodiment, the first interval and the second interval sound insulation.Because the exhaust pathway of solid arrow instruction in Fig. 4 is the path of uniquely going out, is vented and from the aperture 303 supplying tube 101, flows to room 201 flow directly to output tube 103 again, so just by between suppressor case 120 the second interval become Helmholtz chamber.Helmholtz's neck is the part of supplying tube 101 at aperture 303 and supplying tube 101 between the end in Helmholtz chamber, and Helmholtz chamber is the volume in second interval of between suppressor case 120.In this " pure Helmholtz's pattern ", silencing apparatus has high soundproof effect at Helmholtz resonance frequency place under making back pressure keep below the prerequisite of the first predetermined target value.
Figure 5 shows that the acoustical absorptivity figure under silencing apparatus operates in " pure Helmholtz's pattern ".Its X-axis represents frequency, and Y-axis represents soundproof effect.The frequency of maximum soundproof effect when silencing apparatus operates in " pure Helmholtz's pattern " can be calculated by following formula:
f = c 2 π A VL
Wherein:
C: the velocity of sound
A: the sectional area of Helmholtz's neck, the i.e. sectional area of supplying tube 101
V: the volume in Helmholtz chamber, namely between suppressor case 120 the volume in the second interval
L: the length of Helmholtz's neck, the i.e. length of supplying tube 101 at aperture and supplying tube 101 between the end in Helmholtz chamber
From formula and Fig. 5 above, when low engine speed is run, " pure Helmholtz's pattern " has very high acoustic efficiency to low exhaust gas pulses frequency (pulsating frequency), back pressure can be remained on lower than the first predetermined target value simultaneously.Therefore, the first operating mode is designed to remain on lower than first object value when low discharge frequency (usually not higher than 100Hz) by back pressure, and the slow-speed of revolution of the corresponding motor of this low discharge frequency, is generally per minute 1000 and forwards 2500 turns to.As an example, above-mentioned first predetermined target value can be: be set to 50mbars when the rotating speed of motor is 2500 turns per minute or be set to 50mbars when the mass flowrate of motor is 250kg/h.Also can be limited by the equivalent section S e that system is given in addition:
Se = Q 2 * ρ * dP
Se ≈ 250 * 1000 3600 2 * 0.55 * 50 = 9.36 cm 2
The schematic perspective view of exhaust pathway when Fig. 6 is for illustrating that silencing apparatus of the present invention is operated in " pure Helmholtz's pattern ".In figure 6, be vented and got out by the aperture 303 on supplying tube 101, in room 201, enter one end of output tube 103, then discharged by the other end of output tube 103.When engine operation is when the slow-speed of revolution (being generally 1000 to 2500 turns per minute), its produces low-frequency noise (generally lower than 100Hz), this noise for routine silencing apparatus need very large tuned volume (tuning volume) or need very large back pressure.When being operated in this speed range, silencing apparatus according to the present invention makes it be in " pure Helmholtz's pattern " by throttle down 104, therefore, silencing apparatus is now acoustically equivalent to pure Helmholtz's design, and this pattern has very high acoustic efficiency when low exhaust gas pulses frequency and back pressure remained under predetermined target value simultaneously.
Figure 7 shows that sound equivalence when silencing apparatus of the present invention is operated in " pure Helmholtz's pattern " or lumped model.In such a mode, the sound wave from supplying tube 101 is divided into two sound travels.As shown in Figure 7, the sound wave through path A passes arrival room 201 by the aperture 303 on supplying tube 101, then enters output tube 103.Sound wave through path B is arrived the volume be made up of room 202,203 and 204 by supplying tube 101, owing to there is aperture on dividing plate 109,110 and on recurrent canal 111, and therefore not sound insulation between these rooms.Thus, Helmholtz's neck is in such a mode supplying tube 101 in the later part of aperture 303, and Helmholtz's volume is made up of room 202,203 and 204.
Should be appreciated that " pure Helmholtz's pattern " is only a mode of execution of the first operating mode.Alternatively, first mode can be " Helmholtz's pattern that band leaks ", wherein on dividing plate 108, only provides very small amount of aperture.What these apertures were generally diameter about 3.5 millimeters (mm) is less than 20 holes (such as, 15 holes), thus allows noise and/or gas to be spilt by the aperture in room 201 and room 202, between 203 and 204.Under Helmholtz's pattern that this band leaks, the first Room 201 and other room are incomplete sound insulation but limitedly acoustic connection." pure Helmholtz " shown in the table of Fig. 5 design/" pure Helmholtz's pattern " design with " being with the Helmholtz of leaking "/" being with Helmholtz's pattern of leaking " between acoustical absorptivity compare.Be similar to " pure Helmholtz's pattern ", under " Helmholtz's pattern that band leaks ", all exhausts all arrive room 201 via the aperture 303 on supplying tube 101, are more directly discharged by output tube 103.Equally, the silencing apparatus under " Helmholtz's pattern that band leaks " has high acoustical absorptivity at Helmholtz resonance frequency place, keeps back pressure lower than the first predetermined target value simultaneously.
Be appreciated that according to different elimination efficiency requirements, aperture can be arranged at least one in recurrent canal 111, dividing plate 109 and dividing plate 110, all like this can not deviate from the present invention, makes room 202,203 and 204 acoustic connection each other.
Fig. 8 schematically shows exhaust pathway when silencing apparatus of the present invention is operated under the second operating mode " interference (adding absorption) pattern ", and in the second operating mode, valve 104 is opened.This pattern designs when high speed is run for motor.In such a mode, because the valve opened makes output tube 102 open, like this for exhaust provides Liang Tiao road warp.Article 1, path is discharged through output tube 103 in room 201 by the aperture 303 on supplying tube 101 as represented by dashed arrows in fig. 8.Article two, the Article 2 exhaust pathway in exhaust pathway, as shown in solid arrow in Fig. 8, then in room 202 enters output tube 102 to recurrent canal 111 by supplying tube 101 in room 204, and discharges finally by output tube 102.Because air-flow is much smaller along the overall resistance of advancing in Article 2 exhaust pathway than the overall resistance of advancing along Article 1 exhaust pathway, therefore most of exhaust stream can be discharged along Article 2 path.This pattern is referred to as " interference " design or " jamming pattern ".In such a mode, the exhaust airstream of major part (being about 80%) is discharged along the second exhaust pathway, and the remaining exhaust airstream of about 20% is spilt by the first exhaust pathway.As from the foregoing, under " jamming pattern ", the exhaust pathway of most of exhaust stream warp is what to separate with the exhaust pathway of exhaust stream warp under " pure Helmholtz's pattern " or " be with and leak Helmholtz's pattern ".
In the mode of execution that dividing plate 112 is positioned between dividing plate 110 and end cap 107, by the fiber 301 in room 203 and/or the fiber 302 in room 206, the operating mode of silencing apparatus can be changed into " interference adds absorption mode ".In this embodiment, the space of room 203 is partly or entirely filled with fiber 301.Equally, the space of room 206 can be partly or entirely filled with fiber 302.
Overall acoustical absorptivity under second operating mode roughly as shown in Figure 9.Its X-axis represents frequency, and Y-axis represents soundproof effect.Higher when the acoustic efficiency of chart display in Fig. 9 when motor operates in high speed under " interference (adding absorption) pattern " is at high frequency, back pressure can be kept below the second predetermined target value simultaneously.The example of above-mentioned second predetermined target value is: when the rotating speed of motor is 6000 turns or when the mass flowrate of motor is 600kg/h, desired value can be set to 150mbars per minute.Also can be limited by equivalent section S e in addition:
Se = Q 2 * ρ * dP
Se ≈ 600 * 1000 3600 2 * 0.55 * 150 = 12 , 97 cm 2
Those skilled in the art will appreciate that equivalent cross section increases due to the cause of valve open.This means that system more easily have passed.Thus, second operating mode is designed to realize high efficiency under middle and high discharge frequency (being generally more than 100Hz), back pressure is maintained below the second predetermined target value, the middle and high rotating speed (be generally per minute 2500 and go to 6000 turns per minute) of the corresponding motor of middle and high discharge frequency simultaneously.Note that first and second predetermined target value above can be identical, also can be different.
Figure 10 is the exhaust pathway schematic perspective view of silencing apparatus of the present invention when being operated in the second operating mode (interference (adding absorption) pattern).In Fig. 10, the major part of exhaust flows to recurrent canal 111 by supplying tube 101, then discharges (solid-line paths) from output tube 102; Only there is sub-fraction to be vented to spill from the aperture 303 of supplying tube 101, flow to output tube 103(dashed path).When a motor runs at the paramount rotating speed of medium speed (be generally per minute 2500 and go to 6000 turns per minute), it produces the noise of intermediate frequency tremendously high frequency (usually above 100Hz), this noise needs less tuned volume, and easilier to be processed by " interference (adding absorption) pattern ", under this pattern of present embodiment, valve 104 is opened.
Figure 11 shows that sound equivalence when silencing apparatus of the present invention is operated in the second operating mode (" interference (adding absorption) pattern ") or lumped model schematic diagram.In such a mode, sound wave is divided at least four tunnels after entering silencing apparatus by supplying tube 101.As shown in figure 11, the path C under " interference adds absorption mode " is the same with the path A under " pure Helmholtz's pattern ", be all by aperture 303 to room 201 again to output tube 103.Path D, as the main path under " interference adds absorption mode ", arrives output tube 102 again via supplying tube 101, room 204, recurrent canal 111, room 202.Path E arrives room 202 via supplying tube 101, room 204, dividing plate 110, room 203, optional fiber 301, dividing plate 109.Path F is via supplying tube 101, room 204, recurrent canal 111, arrive room 203 and optional fiber 301 by the aperture 304 on recurrent canal 111.To meet with the sound wave of path F and together with meeting at through path D, path E, thus produce the disturbance for sound wave.
Figure 12 shows that the composite sound efficiency that silencing apparatus of the present invention reaches when low engine speeds operates in the first operating mode and middle and high rotating speed operates in the second operating mode.In figure, X-axis represents frequency, and Y-axis represents soundproof effect.As shown in figure 12, the silencing apparatus under the present invention keep low back pressure prerequisite under, in basic, normal, high frequency, all there is high acoustical absorptivity.Therefore, required sound cavity volume can be made to reduce by the present invention, and efficiency during motor acceleration or deceleration significantly improve.
Consult prior figures 3, in another embodiment, if respectively at the part mounting bush resonator S2+M2 that output tube 102 is in the part mounting bush resonator S1+M1 in room 203 and/or is at output tube 103 in room 203, then the main gas circuit under the second pattern flows through supplying tube 101 and recurrent canal 111 and by sleeve pipe resonator S1+M1 before discharging from output tube 102.Similarly, in the first and second modes, for the acoustic path entering room 201 via the aperture 303 on supplying tube 101, exhaust same before discharging from output tube 103 by sleeve pipe resonator S2+M2.
In addition, the valve 104 in above-mentioned mode of execution of the present invention may also be passive " auto-excitation type (self-activated) " valve, and this valve can be opened or closed by the pressure in silencing apparatus.The pressure threshold opening or closing valve can according to the concrete acoustic condition setting of silencing apparatus service condition.
Preferably, valve 104 can be one by the electrically driven (operated) active valve of control signal from silencing apparatus inside or outside.This control signal can be the signal of a state/multiple state of the motor that a reflection silencing apparatus connects, such as reflect the signal of at least one following state, these states comprise: the back pressure of the acoustic pulsations frequency of exhaust, the rotating speed of internal-combustion engine, the mass flowrate of motor and vent systems.Reflect that the signal of above-mentioned state (can be arranged on silencing apparatus inner or outside by the sensor on vehicle, not shown in the diagram) sense, then valve is transferred to select operating mode by control wiring (silencing apparatus can be arranged on inner or outside, not shown in the diagram).Limited for purposes of illustration instead of to the present invention, when motor forwards 6000 turns (acceleration) to from per minute 1000, the threshold value of control signal can be set to 2000 turns per minute; When motor forwards 1000 turns (deceleration) to from per minute 6000, the threshold value of control signal can be set to 3000 turns per minute.According to the difference of application valve 104 type, valve 104 can be arranged at the different parts of output tube 102, such as in the middle part of the either end of output tube 102 or its.Valve 104 is arranged on any position that can control output tube 102 and open and close on output tube 102, is all regarded as falling into scope of the present invention.As selection, valve 104 also can be pneumatic valve or the valve that surges.Similarly, control this pneumatic valve or the valve that surges by same control signal, to enable silencing apparatus run according to the path under first mode when the slow-speed of revolution, run according to the path under the second pattern when middle and high rotating speed.
Be an embodiment of the invention about the description being changed operating mode by the opening and closing of valve 104 above, in this fashion, valve open and relation between closed condition and control signal follows binary function relation.As shown in figure 13, under this mode of execution, control signal follows 0-1 binary function, valve 104 is from closed condition to opening (such as completely, when the rotating speed of motor is raised to 1750 turns about per minute) or substantially there is no intermediateness from being opened to closed condition (such as, when the rotating speed of motor drops to 3250 turns about per minute) completely.In the embodiment of the present invention that another is more optimized, valve 104 opens or closes according to engine speed linear function, and it follows linear functional relation.In this linear mode of execution, when motor accelerates, when motor is lower than 2000 turns per minute, valve 104 is in closes completely.As shown in figure 14, valve 104 engine speed be in per minute 2000 forward between 3000 turns time follow linear function and linearly open.Such as: when 2250 turns per minute, open 25%, when 2500 turns per minute, open 50%, when 2750 turns per minute, open 75%, then all open when 3000 turns per minute.When motor is in more than 3000 turns per minute, then valve keeps opening completely.Similarly, when engine retard, valve 104 is in such as 3000 turns and 2000 turns of linearly closedowns per minute.Note that the above-mentioned per minute 2000 linear opening/closing speed range forwarding 3000 rotary valve doors per minute to are only exemplary purpose.Should be realized that, valve can operate in different speed range internal linear.
Two patterns selected by valve 104 described herein " pure Helmholtz's pattern " and " interference (adding absorption) pattern " are only the object of explanation, therefore should not be considered to be limitation of the present invention.Anyly with design of the present invention, the scheme of two model applications in a silencing apparatus all should to be considered to be application of the present invention.
Those skilled in the art can recognize easily, although disclose output tube and the exhaust pathway of some in mode of execution above, in the present invention, the outlet pipe of silencing apparatus and exhaust pathway number should not be only limitted to the concrete number disclosed in mode of execution above.Those skilled in the art can be that silencing apparatus selects the output tube of arbitrary number and exhaust pathway as required, for example 3 or more, and this should not be regarded as exceeding the scope of the invention.
Although disclose the preferred embodiment of the present invention at this, those skilled in the art can should be appreciated that and should to fall within the scope of protection of the present invention for changes more of the present invention.

Claims (18)

1. a double mode silencing apparatus for internal combustion engine exhaust system, is characterized in that described silencing apparatus comprises:
Housing (105);
First end cap (106) and the second end cap (107), it lays respectively at described housing (105) two ends to form (120) between suppressor case together with described housing (105);
Supplying tube (101), it stretches out to receive exhaust from described internal-combustion engine from described first end cap (106);
Multiple output tube (103,102), it stretches out from described second end cap (107) and form multiple exhaust pathway together with (120) between described supplying tube (101) and described suppressor case; And
Control gear (104), it is provided on one of them output tube of described multiple output tube, for operationally described silencing apparatus being switched to the first operating mode or the second operating mode according to one or more conditions of described internal-combustion engine, each operating mode limits corresponding exhaust pathway, it is at least most of through exhaust pathway transmission thus that it is vented, and the exhaust pathway corresponding to described first operating mode is different from the exhaust pathway corresponding to described second operating mode.
2. double mode silencing apparatus according to claim 1, it is characterized in that described first operating mode is designed to reduce noise when described internal-combustion engine low cruise and back pressure maintained below the first predetermined target value simultaneously, described second operating mode is designed to reduce noise when described internal-combustion engine middling speed or high speed operation and back pressure is maintained below the second predetermined target value simultaneously, wherein said first predetermined target value and described second predetermined target value may be the same or different, preferably, first and second predetermined target value described be defined as given mass flowrate default back pressure or be defined as the parameter irrelevant with exhaust stream.
3. double mode silencing apparatus according to claim 2, is characterized in that the described exhaust pathway corresponding to the first operating mode is separating in (120) between described suppressor case substantially with the described exhaust pathway corresponding to the second operating mode.
4. according to the double mode silencing apparatus of any one of claim 1,2,3, it is characterized in that described control gear comprises the valve that can open or close, for the operating mode switching described silencing apparatus.
5. double mode silencing apparatus according to claim 4, is characterized in that described valve is passive valve, opening or closing by the Stress control of described silencing apparatus inside of described passive valve.
6. double mode silencing apparatus according to claim 4, is characterized in that described valve is the active valve controlled by control signal, and preferably, described active valve is selected from the group be made up of electric valve, pneumatic valve and the valve that surges.
7. double mode silencing apparatus according to claim 6, is characterized in that at least one that described control signal reflects in following condition: the ripple frequency of the sound wave of exhaust, the rotating speed of internal-combustion engine, the mass flowrate of internal-combustion engine and the back pressure of vent systems.
8., according to the double mode silencing apparatus of claim 6 or 7, the relation between the Push And Release state that it is characterized in that described valve and described control signal follow a given function, are preferably binary function or linear function.
9. double mode silencing apparatus according to claim 4, is characterized in that described first operating mode is that " pure Helmholtz " design or " Helmholtz that band leaks " design and/or described second operating mode is " interference " design or " interference adds absorption " design.
10. double mode silencing apparatus according to claim 9, characterized by further comprising:
First dividing plate (108), second partition (109) and the 3rd dividing plate (110), it places successively in described housing (105), wherein,
Described first dividing plate (108), (120) between described suppressor case are divided into four rooms by second partition (109) and the 3rd dividing plate (110): be positioned at the first Room (201) between described first end cap (106) and described first dividing plate (108), be positioned at the second Room (202) between described first dividing plate (108) and described second partition (109), be positioned at the 3rd Room (203) between described second partition (109) and described 3rd dividing plate (110), and the fourth ventricle (204) be positioned between described 3rd dividing plate (110) and described second end cap (107),
Wherein,
Described second Room (202), the 3rd Room (203) and fourth ventricle (204) are acoustically communicating with each other.
11. double mode silencing apparatuss according to claim 10, it is characterized in that described supplying tube (101) is through described first dividing plate (108), second partition (109) and the 3rd dividing plate (110), and end in fourth ventricle (204), wherein, the part of described supplying tube (101) in described first Room (201) is provided with one group of aperture (303);
The first output tube (103) in described multiple output tube originates in described first Room (201), through described first, second and the 3rd dividing plate (108,, and extend to the outside of (120) between described suppressor case through described second end cap (107) 109,110);
The second output tube (102) in described multiple output tube originates in described second Room (202), through described second partition (109) and the 3rd dividing plate (110), and extend to the outside of (120) between described suppressor case through described second end cap (107); Further,
Described double mode silencing apparatus also comprises recurrent canal (111), and described recurrent canal (111) originates in described second Room (202), through described second and the 3rd dividing plate (109,110), and ends in fourth ventricle (204).
12. double mode silencing apparatuss according to claim 11, it is characterized in that at least on one of following assembly, being provided with multiple aperture: described second partition (109), described 3rd dividing plate (110) and described recurrent canal (111), preferably, the part of described recurrent canal in described 3rd Room (203) is provided with aperture (304).
13. according to the double mode silencing apparatus of any one of claim 10-12, it is characterized in that described first dividing plate (108) does not have aperture, with other each room sound insulation under described first operating mode making described first Room (201) design described " pure Helmholtz " thus.
14. according to the double mode silencing apparatus of any one of claim 10-12, it is characterized in that described first dividing plate (108) is provided with very small amount of aperture, make described first Room (201) and other each room limitedly acoustic connection under described first operating mode designed at described " band leak Helmholtz " thus.
15. according to the double mode silencing apparatus of any one of claim 10-12, characterized by further comprising the 4th dividing plate (112) be positioned between described 3rd dividing plate (110) and described second end cap (107), thus allow described first and second output tubes (103,102) through described 4th dividing plate (112); Be formed at the 5th Room (205) between described 3rd dividing plate (110) and described 4th dividing plate (112); And the 6th Room (206) be formed between described 4th dividing plate (112) and described second end cap (107), preferably, described double mode silencing apparatus also comprises the fiber (301,302) be located in described 3rd Room (203) and/or described 6th Room (206).
16. according to the double mode silencing apparatus of any one of claim 10-12, it is characterized in that the part of described first output tube (103) in described 3rd Room (203) is provided with aperture (306), and the part of described second output tube (102) in described 3rd Room (203) is provided with aperture (305).
17. double mode silencing apparatuss according to claim 16, characterized by further comprising and be arranged on described first output tube (103) and/or described second output tube (102) and be positioned at one or more sleeve pipe resonators (S1+M1, S2+M2) in the part of described 3rd Room (203).
18. double mode silencing apparatuss according to claim 17, is characterized in that described sleeve pipe resonator is high frequency sleeve pipe resonator, preferably, are high frequency stainless steel sleeve pipe resonator.
CN201310217269.0A 2013-05-31 2013-05-31 Dual-mode silencer for internal combustion engine exhausting system Pending CN104213955A (en)

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KR1020130155217A KR20140141416A (en) 2013-05-31 2013-12-13 Dual-scheme muffler for exhaust system of internal combustion engine

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CN104847449A (en) * 2015-04-13 2015-08-19 成都陵川特种工业有限责任公司 Noise weakening processing method for exhaust gas emission pipe
CN108331667A (en) * 2018-02-12 2018-07-27 江门市大长江集团有限公司 The noise control method of engine
JP2020067038A (en) * 2018-10-24 2020-04-30 マレリ株式会社 Muffler
CN113107641A (en) * 2021-05-25 2021-07-13 成都爱信智能燃气设备有限责任公司 Tail gas collection silencer
CN113323742A (en) * 2021-07-05 2021-08-31 北京汽车集团越野车有限公司 Silencer and vehicle
CN114439620A (en) * 2022-01-25 2022-05-06 东风汽车集团股份有限公司 Tuning valve and automobile silencer
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CN104847449A (en) * 2015-04-13 2015-08-19 成都陵川特种工业有限责任公司 Noise weakening processing method for exhaust gas emission pipe
CN108331667A (en) * 2018-02-12 2018-07-27 江门市大长江集团有限公司 The noise control method of engine
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CN116220861A (en) * 2023-03-31 2023-06-06 浙江春风动力股份有限公司 Motorcycle

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Application publication date: 20141217