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WO2008015046A1 - Dispositif d'amortissement des sons dans un conduit tubulaire - Google Patents

Dispositif d'amortissement des sons dans un conduit tubulaire Download PDF

Info

Publication number
WO2008015046A1
WO2008015046A1 PCT/EP2007/055641 EP2007055641W WO2008015046A1 WO 2008015046 A1 WO2008015046 A1 WO 2008015046A1 EP 2007055641 W EP2007055641 W EP 2007055641W WO 2008015046 A1 WO2008015046 A1 WO 2008015046A1
Authority
WO
WIPO (PCT)
Prior art keywords
channel section
tube channel
sectional area
flow cross
medium
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/EP2007/055641
Other languages
German (de)
English (en)
Inventor
Peter Marschall
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
ContiTech Kuehner GmbH and Cie KG
Original Assignee
ContiTech Kuehner GmbH and Cie KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by ContiTech Kuehner GmbH and Cie KG filed Critical ContiTech Kuehner GmbH and Cie KG
Priority to EP07730000A priority Critical patent/EP2049776A1/fr
Publication of WO2008015046A1 publication Critical patent/WO2008015046A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • F01N1/08—Silencing apparatus characterised by method of silencing by reducing exhaust energy by throttling or whirling
    • F01N1/12—Silencing apparatus characterised by method of silencing by reducing exhaust energy by throttling or whirling using spirally or helically shaped channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L55/00—Devices or appurtenances for use in, or in connection with, pipes or pipe systems
    • F16L55/02—Energy absorbers; Noise absorbers
    • F16L55/027—Throttle passages
    • F16L55/02772—Throttle passages using spirally or helically shaped channels
    • 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
    • F01N2490/18—Dimensional characteristics of gas chambers
    • 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
    • F01N2490/20—Chambers being formed inside the exhaust pipe without enlargement of the cross section of the pipe, e.g. resonance chambers

Definitions

  • the invention relates to a device for sound attenuation of a flowing through a pipe channel, pulsating pressure density differences and at least partially having a rotating about the longitudinal axis of the pipe channel share medium, wherein the rotational speed of the medium from the center of rotation radially outward to the radial distance from the center of rotation is proportional.
  • Such devices are used for example in exhaust pipes of internal combustion engines or air conditioning lines of automotive air conditioning.
  • pulsating pressure generation arise in such systems oscillations in the medium, which cause pressure density differences and make themselves felt as unwanted noise emissions.
  • swirling elements such as vanes or coiled tubes while at least a portion of the medium is forced to cover a longer path in the pipe channel than the rest, not or rotating at a lower rotational speed part of the medium.
  • waves and valleys of the pressure density differences are shifted from each other during the interaction of the parts of the medium.
  • the resulting superposition vibration is smoothed compared to the original vibration, which reduces the noise emission.
  • Such devices are known, for example, from DE 103 281 44 A1 or DE 101 63 812 A1.
  • a disadvantage of these solutions, however, is that the effects of the devices are very difficult to predict and interpret in advance and therefore must be determined in practice for each system by experiments.
  • the invention has for its object to provide a device of the type described, which effectively attenuates the sound emissions at different vibration ratios even without complex individual adjustments.
  • the tube channel has at least two tube channel sections, wherein the first tube channel section is arranged upstream of the second tube channel section and the first tube channel section has a predetermined flow cross-sectional area which is larger than the flow cross-sectional area of the second tube channel section and the ratio of flow cross-sectional area of first tube channel portion and flow cross-sectional area of the second tube channel portion is selected so that the rotating medium in the transition from the first tube channel portion in the second tube channel portion in the direction of rotation can be accelerated proportional to the rotational speed and while the axial velocity of the rotating medium is reduced proportional to the rotational acceleration of the medium.
  • the rotating medium When the rotating medium exits the first tube channel section, it has a certain rotation momentum. Apart from low friction losses, which occur at the wall of the pipe channel, after the spin set of the mechanics, the angular momentum also remains at the transition of the medium into the smaller flow cross-sectional area. This has the consequence that the angular velocity of the rotating medium increases, the medium thus accelerated in the direction of rotation.
  • the medium is decelerated in the axial direction during this change in the rotational speed of the Coriolis acceleration, since the Coriolis acceleration acts perpendicular to the direction of movement of the medium.
  • the Coriolis acceleration generates a force which is also effective in the axial direction, the amount of energy required by this force along the path of the medium during the transition into the smaller flow cross-sectional area being removed from the axial kinetic energy of the medium, ie the medium in the axial direction is slowed down.
  • the Coriolis acceleration is also dependent on the rotational speed of the medium, so that the braking effect is greatest on the areas of the medium which are most strongly accelerated during the transition from the first flow cross-sectional area to the second flow cross-sectional area.
  • the axial velocity of the medium thus decreases continuously from the center of the tube channel to the most strongly rotating regions on the inner wall of the tube channel.
  • swirling bodies are arranged with an inflow end and an outflow end, by means of which the rotation of the medium can be influenced.
  • the rotation of the medium flowing through the first pipe channel section is insufficient during the transition into the second pipe channel section in order to achieve the desired effect, the rotation of the medium can be increased with said swirling bodies.
  • the outflow ends of the swirling body are spaced from the transition from the first pipe channel section to the second pipe channel section by a predetermined amount.
  • the rotational acceleration and associated axial delay of the medium can be influenced.
  • the acceleration smaller, larger at a small distance.
  • the swirl bodies are coiled vanes which are arranged twisted about the central axis of the pipe channel section and which are fixedly and permanently attached to a coaxial pipe to the vanes and form a swirl insert with the pipe inside the first pipe - Channel section is arranged coaxially with the pipe channel.
  • the swirling insert is a profile section produced in the extrusion process.
  • the swirling insert is a plastic injection-molded part.
  • the geometry of the swirling insert according to the invention allows a simple and secure installation in the pipe channel.
  • a swirling insert designed in this way can be produced cost-effectively in the aforementioned ways.
  • the swirl bodies are formed by radially inwardly directed axially coiled projections of the wall of the first pipe channel section, which have a predetermined length and pitch matched to the first pipe channel section and the transition region.
  • Such projections can be produced for example by plastic deformation of the pipe channel wall. As a result, no separate use is necessary.
  • the first flow cross-sectional area in the first tube channel section is greater than the flow cross-sectional area of a third, to the first tube channel section in the flow direction of the medium before the first
  • Pipe duct section arranged pipe duct section, wherein the transition from the Strö- mung cross-sectional area of the third tube channel portion in the flow cross-sectional area of the first tube channel portion of the said third tube channel portion associated end of the swirl body is spaced by a predetermined amount.
  • the Verwirbelungsharmos reduce the free flow cross-sectional area by the extent of their end faces, so that it can come to a dynamic pressure and thus to an undesirable reduction of the flow velocity when the medium impinges on the turbulence body.
  • the expansion volume formed by the arrangement according to the invention in front of the turbulence bodies allows the medium to distribute the dynamic pressure to the end faces of the turbulence bodies. As a result, the flow resistance in the first tube channel section is reduced again.
  • the first tube channel section is formed by a widening process from the tube channel.
  • the expansion for example by hydroforming or thorns, has the advantage that no additional material for the increased diameter is required.
  • the diameter of the second tube channel section is reduced by pulling it in relation to the diameter of the first tube channel section.
  • Retraction has the advantage that no thermal joining methods have to be used.
  • the turbulence insert is fixed by a press fit in the first tube channel section.
  • the solution according to the invention provides a cost-effective, easy-to-install and effective device for sound damping in pipe ducts, with which the sound emission of any pulsed flow can be reduced. Previous trial phases or complex calculations can be reduced or completely eliminated.
  • Fig. 2 is a symbolic diagram of the velocity distribution of the medium flowing through the device according to the invention.
  • FIG. 1 shows a part of a pipe channel with a first pipe channel section 1, a second pipe channel section 2 and a third pipe channel section 3 in longitudinal section.
  • a medium flows through the three tube channel sections 1, 2, 3 first through the tube channel section 3, then through the tube channel section 1 and then through the tube channel section 2.
  • a turbulence insert 4 is arranged coaxially with the tube channel section 1.
  • the turbulence insert 4 has a tubular central element 5, on whose outer surfaces uniformly distributed on the circumference of the central element 5 three vanes 6 are arranged.
  • the vanes 6 are helically coiled and insoluble and firmly connected to the central element 5.
  • the turbulence insert has an axial end face 7.
  • the outer diameter of the swirling insert 4 is dimensioned so that it can be pressed into the inner diameter of the tubular channel section 1 with a press fit.
  • the interference fit ensures a tight fit of the swirling body 4 in the pipe channel 1 Part of the medium, not shown, flows through the swirling insert 4 through the tube 5 and the remaining part of the medium, not shown, flows around the outside of the tube 5 and is set in rotation by the guide vanes 6.
  • the pipe channel section 1 has a flow cross-sectional area 8, wherein in the figure, for better clarity, the corresponding diameters are shown as equivalent to the flow cross-sectional areas.
  • the pipe channel section 3 has a flow cross-sectional area 9, the flow cross-sectional area 9 being approximately as large as the flow cross-sectional area 7, reduced around the end face 7 of the swirling body 4.
  • the flow cross-sectional area effective for the medium is therefore approximately as large in the pipe channel section 1 as in the pipe channel section 3.
  • the pipe channel has a transitional region 10, in which the pipe channel section 1 merges with the flow cross-sectional surface 8 into the pipe channel section 2 with a flow cross-sectional surface 11.
  • the rotating part of the medium undergoes an increase in its rotational angular velocity in the transition region 10 due to the spin set of the mechanism, while at the same time reducing its axial velocity caused by the Coriolis effect.
  • the non-rotating part does not experience this acceleration.
  • the oscillation amplitudes 12 to 16 each represent a selected instantaneous axial position of the flowing medium, the oscillation amplitude 12 representing the state of the medium in the flow direction before entering the region of the turbulizer 4.
  • the oscillation amplitude 13 represents the state after the medium has entered the region of the tube channel section 1 with the diameter 7, the oscillation amplitude 14 after the medium impinges on the turbulence body 4, the oscillation amplitude 15 immediately after leaving the region of the turbulence. 4 and the vibration amplitude 16 after flowing through the transition region 10.
  • each oscillation amplitude 12 to 16 represents the axial velocity in the center of the flow, the upper one the axial velocity of the medium in the edge region of the tube channel section 1.
  • all regions of the medium flow with approximately the same axial velocity Speed.
  • all regions of the medium likewise flow at approximately the same axial velocity.
  • the oscillation amplitude 13 is slightly attenuated because of the larger diameter 7 at this point of the pipe channel section 1.
  • the oscillation amplitude 14 after the impact of the medium on the turbulence body 4, the medium begins to rotate increasingly from the inside to the outside.
  • the axial velocity continuously decreases from the center of the flow to the edge of the flow, which is made clear by the staggered position of the arrow 17 relative to one another.
  • the lowest arrow represents the velocity of the non-rotating medium in the center of the flow.
  • the axial velocity of the medium continues to decrease toward the outside, which becomes clear at the oscillation amplitude 15.
  • the Coriolis effect additionally comes into play, which further slows down the axial velocity of the medium after flowing through the transitional region 10 of the tubular duct section 1.
  • FIG. 3 shows the effects of the speed changes from FIG. 2 on the amplitudes of the oscillations on the basis of five amplitude envelopes 18 to 22, wherein the envelope 18 is assigned to the oscillation amplitude 12 from FIG. 2 and the envelopes 19 to 22 are continuously assigned to the oscillation amplitudes 13 to 17 are assigned from Fig. 2. Due to the decreasing axial velocity of the rotating medium over the flow path along the swirling body 4 and through the transitional region 10, a displacement of the respective amplitude maxima results, so that with the enveloping curve 22 at the end of said flow path a particularly well smoothed vibration is obtained. yielding curve. This leads to a significant lowering of the sound level in the pipe channel section. 1
  • transition area 11 flow cross-sectional area of the second tube channel section 2 12 - 16 oscillation amplitudes

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Pipe Accessories (AREA)

Abstract

L'invention concerne un dispositif pour l'amortissement des sons d'un fluide s'écoulant à travers un conduit tubulaire, présentant des différences de pression pulsées et présentant au moins en partie une proportion tournant autour de l'axe longitudinal du conduit tubulaire. La vitesse de rotation du fluide depuis le centre de rotation radialement vers l'extérieur est proportionnelle à la distance radiale depuis le centre de rotation. L'invention est caractérisée en ce que le conduit tubulaire présente au moins deux parties de conduit tubulaire (1, 2), la première partie de conduit tubulaire (1) étant disposée, dans la direction de l'écoulement, avant la deuxième partie de conduit tubulaire (2), et la première partie de conduit tubulaire (1) présente une surface de section d'écoulement prédéfinie (8), qui est supérieure à la surface de section d'écoulement (11) de la deuxième partie de conduit tubulaire (2). De plus, le rapport de la surface de section d'écoulement (8) de la première partie de conduit tubulaire (1) et de la surface de section d'écoulement (11) de la deuxième partie de conduit tubulaire (2) est choisi de telle sorte que le fluide en rotation, lors du passage de la première partie de conduit tubulaire (1) dans la deuxième partie de conduit tubulaire (2) puisse être accéléré dans le sens de la rotation de manière proportionnelle à la vitesse de rotation et que la vitesse axiale du fluide en rotation puisse donc être réduite de manière proportionnelle à l'accélération en rotation du fluide.
PCT/EP2007/055641 2006-08-01 2007-06-08 Dispositif d'amortissement des sons dans un conduit tubulaire Ceased WO2008015046A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP07730000A EP2049776A1 (fr) 2006-08-01 2007-06-08 Dispositif d'amortissement des sons dans un conduit tubulaire

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006035755.8 2006-08-01
DE102006035755A DE102006035755A1 (de) 2006-08-01 2006-08-01 Vorrichtung zur Schalldämpfung in einem Rohrkanal

Publications (1)

Publication Number Publication Date
WO2008015046A1 true WO2008015046A1 (fr) 2008-02-07

Family

ID=38473925

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2007/055641 Ceased WO2008015046A1 (fr) 2006-08-01 2007-06-08 Dispositif d'amortissement des sons dans un conduit tubulaire

Country Status (3)

Country Link
EP (1) EP2049776A1 (fr)
DE (1) DE102006035755A1 (fr)
WO (1) WO2008015046A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202008013253U1 (de) * 2008-10-04 2010-01-07 Fürst, Gabi Einsatzvorrichtung für Auspuffrohrstutzen von Kraftfahrzeugen
US9243543B2 (en) 2012-12-07 2016-01-26 Hanon Systems Universal attenuation device for air-conditioning circuit
CN107002544A (zh) * 2015-02-26 2017-08-01 金基训 引擎配管流速增大装置及其加工方法
US12235024B2 (en) 2021-05-21 2025-02-25 Carrier Corporation Deflector for condenser, condenser having it and chiller system

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2949595B1 (fr) * 2009-08-31 2011-09-02 Ae2S Dispositif d'attenuation acoustique
CN101922169A (zh) * 2010-08-19 2010-12-22 沈仁泰 节水小水龙头用水装置

Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1543042A (en) * 1923-03-05 1925-06-23 Gen Motors Corp Muffler for internal-combustion engines
CH137556A (de) * 1929-05-21 1930-01-15 Knecht Frei Johann Schalldämpfer für Explosionsmotoren.
FR1087417A (fr) * 1953-07-29 1955-02-23 Silencieux pour amortir les bruits de pulsation des gaz d'un moteur et procédé de fabrication
FR1173807A (fr) * 1957-04-29 1959-03-03 Silencieux d'échappement à éléments tubulaires faciles à nettoyer
US3393767A (en) * 1967-06-28 1968-07-23 Travis B. Monk Combustion engine muffler
DE2620616A1 (de) * 1975-09-13 1977-03-17 Teruo Kashihara Auspuffvorrichtung fuer verbrennungskraftmaschinen
FR2382581A1 (fr) * 1977-03-04 1978-09-29 Chauvin Gilbert Dispositif combine de silencieux, accouples en serie ou non, pour echappement bruyant, a l'air libre, de tout fluide gazeux
FR2620169A1 (fr) * 1987-09-09 1989-03-10 Glaenzer Spicer Sa Partie de ligne d'echappement, notamment pour moteur a combustion interne
US6364055B1 (en) * 2000-09-26 2002-04-02 Alan H. Purdy Acoustically non-resonant pipe
DE10163812A1 (de) 2001-12-22 2003-07-03 Mann & Hummel Filter Vorrichtung zur Schalldämpfung in einem Rohrkanal
DE10328144A1 (de) 2001-12-22 2005-01-05 Mann + Hummel Gmbh Vorrichtung zur Schalldämpfung in einem Rohrkanal
US20050011700A1 (en) * 2003-07-14 2005-01-20 Dadd Paul M. Devices for regulating pressure and flow pulses

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1543042A (en) * 1923-03-05 1925-06-23 Gen Motors Corp Muffler for internal-combustion engines
CH137556A (de) * 1929-05-21 1930-01-15 Knecht Frei Johann Schalldämpfer für Explosionsmotoren.
FR1087417A (fr) * 1953-07-29 1955-02-23 Silencieux pour amortir les bruits de pulsation des gaz d'un moteur et procédé de fabrication
FR1173807A (fr) * 1957-04-29 1959-03-03 Silencieux d'échappement à éléments tubulaires faciles à nettoyer
US3393767A (en) * 1967-06-28 1968-07-23 Travis B. Monk Combustion engine muffler
DE2620616A1 (de) * 1975-09-13 1977-03-17 Teruo Kashihara Auspuffvorrichtung fuer verbrennungskraftmaschinen
FR2382581A1 (fr) * 1977-03-04 1978-09-29 Chauvin Gilbert Dispositif combine de silencieux, accouples en serie ou non, pour echappement bruyant, a l'air libre, de tout fluide gazeux
FR2620169A1 (fr) * 1987-09-09 1989-03-10 Glaenzer Spicer Sa Partie de ligne d'echappement, notamment pour moteur a combustion interne
US6364055B1 (en) * 2000-09-26 2002-04-02 Alan H. Purdy Acoustically non-resonant pipe
DE10163812A1 (de) 2001-12-22 2003-07-03 Mann & Hummel Filter Vorrichtung zur Schalldämpfung in einem Rohrkanal
DE10328144A1 (de) 2001-12-22 2005-01-05 Mann + Hummel Gmbh Vorrichtung zur Schalldämpfung in einem Rohrkanal
US20050011700A1 (en) * 2003-07-14 2005-01-20 Dadd Paul M. Devices for regulating pressure and flow pulses

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202008013253U1 (de) * 2008-10-04 2010-01-07 Fürst, Gabi Einsatzvorrichtung für Auspuffrohrstutzen von Kraftfahrzeugen
US9243543B2 (en) 2012-12-07 2016-01-26 Hanon Systems Universal attenuation device for air-conditioning circuit
CN107002544A (zh) * 2015-02-26 2017-08-01 金基训 引擎配管流速增大装置及其加工方法
CN107002544B (zh) * 2015-02-26 2019-08-02 金基训 引擎配管流速增大装置及其加工方法
US12235024B2 (en) 2021-05-21 2025-02-25 Carrier Corporation Deflector for condenser, condenser having it and chiller system

Also Published As

Publication number Publication date
DE102006035755A1 (de) 2008-02-07
EP2049776A1 (fr) 2009-04-22

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