EP1857682B1 - Machine à pistons rotatifs avec dispositif silencieux - Google Patents

Machine à pistons rotatifs avec dispositif silencieux Download PDF

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Publication number
EP1857682B1
EP1857682B1 EP06010289.4A EP06010289A EP1857682B1 EP 1857682 B1 EP1857682 B1 EP 1857682B1 EP 06010289 A EP06010289 A EP 06010289A EP 1857682 B1 EP1857682 B1 EP 1857682B1
Authority
EP
European Patent Office
Prior art keywords
chamber
rotary piston
sound absorber
piston machine
sound
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.)
Active
Application number
EP06010289.4A
Other languages
German (de)
English (en)
Other versions
EP1857682A1 (fr
Inventor
Christian-Philipp Hage
Hans-Ulrich Fleige
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.)
Aerzener Maschinenfabrik GmbH
Original Assignee
Aerzener Maschinenfabrik GmbH
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 Aerzener Maschinenfabrik GmbH filed Critical Aerzener Maschinenfabrik GmbH
Priority to ES06010289.4T priority Critical patent/ES2581731T3/es
Priority to EP06010289.4A priority patent/EP1857682B1/fr
Publication of EP1857682A1 publication Critical patent/EP1857682A1/fr
Application granted granted Critical
Publication of EP1857682B1 publication Critical patent/EP1857682B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/06—Silencing
    • F04C29/061—Silencers using overlapping frequencies, e.g. Helmholtz resonators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2220/00—Application
    • F04C2220/10—Vacuum
    • F04C2220/12—Dry running

Definitions

  • the invention relates to a dry-running rotary piston machine with ChristsSWlldämpfer for gases or gas-vapor mixtures, which at least two mounted in a housing via shafts and bearing assemblies rotary pistons, which mesh with each other in opposite directions to define a delivery chamber, said waves operationally via toothed timing wheels coupled together.
  • dry running is to be understood that the rotary piston itself not through.
  • Lubricating lubricants such as lubricating oil or the like.
  • Dry-running rotary piston engines in particular rotary screw compressors and Rotary blowers of the type Roots, but also rotary piston expansion machines, work today with relatively high differential pressures (up to 7 bar) and speeds (up to about 20,000 1 / min).
  • a problem which generally exists in these rotary piston machines is that a part of the already compressed medium from the pressure-side pipe strikes back into the delivery chamber when the delivery chamber is opened, thus leading to strong pulsations or oscillations both in the compressor and in the downstream delivery-side delivery line. These pulsations are responsible for the high noise level of such machines, especially in the low frequency range.
  • Rotary engines of this type are for Example from the DE 32 38 015 known.
  • screw compressors having an internal compression due to the highly twisted piston in addition to the phenomenon described above, depending on the backpressure when opening the delivery chamber to the pressure side, a sudden outflow of the previously over-compressed fluid may occur.
  • silencers are used, two types being basically to be distinguished. These are on the one hand absorption silencers, which work with different absorption materials such as steel or mineral wool, and on the other hand the so-called resonance or reaction silencers, which work without such materials only by the special shape and dimensions of the silencer.
  • Absorption mufflers damp particularly high frequencies very well, but have several disadvantages. On the one hand, they dampen the lower frequency range only poorly or not at all, due to the very small thickness of the absorptive material compared to the sound wave length. Because of their close-meshed structure, absorption mufflers also become dirty, especially in the case of exhaust gases loaded by liquids or solids, which increasingly prevents the correct functioning of the muffler. In addition, fibers or other components can be discharged from the absorbent material, which can lead to serious problems in the downstream system and is therefore undesirable.
  • Reflection mufflers generally consist of an inner tube and an outer tube (the chamber), which are connected together to allow the passage of gas. They work on the principle that by the smaller Inner tube with the gas flow into the chamber entering sound is reflected due to the abrupt change in cross section.
  • the cut-off frequency and the strength of the insulation depends to a great extent on the geometry of the silencer.
  • the ratio of the diameter of the chamber to the diameter of the inner tube (D / d) must be as large as possible.
  • the limit frequency f gr above which the Schalldämm Koch drops sharply, inversely proportional to the diameter of the chamber (f gr ⁇ 1 / D)
  • the outer diameter of the chamber must not be too large to allow the insulation of high frequencies.
  • a way out is the parallel arrangement of several inner tubes and the simultaneous subdivision of the outer tube (the so-called Mehrflutmaschine).
  • An example is in the EP 1 117 965 shown.
  • the diameter of the chamber D is halved, so that the limit frequency of the insulation can be approximately doubled.
  • Helmholtz inner tubes in which holes are provided at a certain axial position in the inner tube shell. These can be evenly distributed over the entire shell, such as in the US 2,241,010 described, or may be present only at certain points by means of perforated plates, see, for example EP 0 798 694 ,
  • the outer tube is often divided into axially arranged chambers of different lengths (and thus different resonance frequencies), wherein each of the chambers are connected via the holes in the inner tube shell with the sound-conducting inner tube.
  • An example is in the document DE 296 12 322 shown.
  • the insulation be effective not only in terms of the amplitude of the sound at certain frequencies but over the entire frequency range.
  • the invention is concerned with the connection openings in the shell of a Helmholtz inner tube. It has been found that more holes (or better a larger area of the holes) better Insulation properties bring with it. This can be done by enlarging the individual holes themselves. Extrapolating to the limiting case, the holes become slits, which are formed predominantly transversely to the axial extent, that is to say in the circumferential direction on the jacket of the inner tube. Only a few webs remain for the mechanical connection of the inner tube available. Measurements have shown that by using the slots instead of holes, the insulation effect is surprisingly greatly improved.
  • the present invention provides a dry-running rotary muffler with reaction muffler comprising at least two rotatably mounted in a housing via shafts and bearing assemblies rotors which mesh with each other in opposite directions to define a delivery space, the waves are operatively coupled via control wheels, and wherein the Muffler has a silencing chamber, an inlet opening and an outlet opening,.
  • the rotary engine with reaction muffler is characterized in that the sound-damping chamber is divided by one or more parallel to the axial direction partitions (55,63a, 65) into two or more chamber parts (51b-e, 61b, d), which together define a multi-flow chamber wherein an inner tube (52b-e, 62b, d) is provided through each chamber member, which gas passes through the sound attenuation chamber, and on the inner tubes a plurality of slots are provided substantially in the circumferential direction, wherein the majority of the gas flows through the inner tube.
  • the slots are separated in the circumferential direction by webs. In this way, almost the entire circumference can be used for the slot surface, wherein the webs simultaneously ensure the stability of the tube.
  • the ratio of web area to slot area is preferably less than 30%, particularly preferably less than 25%, and in particular less than 20%. These values are significantly better than the corresponding values for perforated plates and provide improved leakage of sound pressure through the slots without jeopardizing tube stability.
  • the slots are provided in the flow direction on the front third and / or the middle third and / or the rear third of the inner tube. Measurements have shown that thereby the conditions of use (frequency spectrum and amplitude of the sound from the rotary piston engine, pipe diameter, type of gas application) adapted optimum insulation effect can be achieved.
  • the muffler is preferably divided by at least one partition wall such that they define / define a plurality of sound damping chambers in the flow direction, wherein an inner pipe leads through at least one sound damping chamber.
  • These Schalldämpfschn can be used for insulation around different resonance frequencies around or serve as distribution or collection chambers.
  • the partition wall or walls divide the muffler in the flow direction into chambers, so that arise at a deflected flow so-called folded arrangements, wherein the flow direction in a chamber in opposite directions or perpendicular to the flow direction in an adjacent, through the Partition wall is divided chamber.
  • one or more sound-damping chambers is or are divided by one or more partitions parallel to the axial direction into two or more chamber parts, which together form a multi-flow chamber or chambers define, wherein an inner tube is provided by each chamber part.
  • the respective inner tubes are usually parallel to each other.
  • the axes of the inlet opening and the outlet opening of the muffler form an angle of substantially 90 ° to one another.
  • This arrangement is particularly favorable for such rotary engines, which are made due to their relatively small size on the silencer and use this as a basis.
  • a first embodiment is shown.
  • the outlet of a rotary engine 10 is connected via flanges 11 and a pipe 12 to the inlet of a reflection muffler 20.
  • the muffler 20 into which the sounding gas ejected from the rotary piston engine flows consists of a muffler chamber 21 and an inner tube 22 through which the same cross section as the pipe 12 and the outlet of the rotary machine 10 pass, as small as possible To generate pressure drop.
  • slots 24 are provided in the flow direction (indicated by arrows) in the front and middle third, the size of which may be different.
  • the slots 24 are separated in the circumferential direction by webs 25, so that in Fig.
  • FIG. 4 illustrates an embodiment in which a muffler 30, as previously described in FIG Fig. 1 is connected to a rotary piston machine 10, divided by two partition walls 33 in a distribution chamber 31 a, a sound-damping chamber 31 b and a collecting chamber 31 c is.
  • a sound-damping chamber 31b performs an inner tube 32, which has slots 34 on its jacket in the flow direction in the front, middle and rear third, through which the sound pressure in the muffler chamber 31b can escape.
  • the manifold chamber 31a and 31c cause deceleration and subsequent acceleration of the gas entering the muffler 30 respectively before and after being damped in the muffler chamber 31b.
  • the chamber 31a and 31c thus also work as muffler chambers, but according to the conventional reflection principle.
  • FIG Fig. 3 An arrangement in which the rotary piston engine 10 uses the muffler 40 as a base is shown in FIG Fig. 3 illustrated.
  • the axes of inlet 48 and outlet 49 form an angle of 90 °.
  • the muffler 40 is divided by two partition walls 43 into an inlet chamber 41 a, a deflection chamber 41 b and an end chamber 41 c.
  • the gas ejected from the machine 10 is first guided into the inlet chamber 41a, from where it passes through a passage tube 45 into the deflection chamber 41b. From there it flows through a closed tube 42a again through the inlet chambers 41a and into the end chamber 41c, in which there is provided with circumferential slots 44 (without webs) in the front and middle third inner tube 42b.
  • the "deflection" of the gas flow is also called a "folded" silencer arrangement.
  • FIG. 4a An embodiment of the invention in which the Mehrflutmaschine is used is in FIG. 4a shown.
  • a muffler 50 serves as a base for the rotary engine 10, so that the axes of inlet and outlet of the muffler 50 form a 90 ° angle.
  • Two partition walls 53 divide the muffler 50 into an inlet chamber (manifold chamber) 51a, an outlet chamber (plenum) 51f, and a muffler chamber therebetween.
  • inlet chamber manifold chamber
  • plenum plenum
  • a muffler 60 is disposed above the rotary piston machine 10.
  • a plurality of partition walls 63a, b, c, d divide the muffler 60 in the flow direction into chambers 61a, b, c, d, e, with the partition wall 63a arranged horizontally and the remaining partition walls vertically.
  • the chamber 61b is divided by a vertical partition 65 into two chambers 61b 'and 61b''double-flow.
  • the chamber 61d is traversed by an inner tube 62d of square cross section, while the chambers 61b 'and 61b "are traversed by square inner tubes 62b' and 62b" respectively, the sum of their cross sections being equal to the cross section of the inner tube 62d.
  • All the inner tubes 62b ', 62b "and 62d have circumferential slots 64 in the direction of flow in the front and middle third portions the axes of the muffler inlet 68 and outlet 69 arranged parallel and offset from one another.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Exhaust Silencers (AREA)

Claims (8)

  1. Machine à pistons rotatifs (10) fonctionnant à sec et à silencieux (50, 60), comprenant :
    au moins deux pistons rotatifs qui sont montés dans un boîtier par l'intermédiaire d'arbres et d'ensembles de paliers et qui s'engrènent l'un dans l'autre en sens inverse afin de définir une chambre de refoulement,
    où les arbres sont accouplés l'un à l'autre en service par l'intermédiaire de roues de commande,
    où le silencieux comprend une chambre d'insonorisation (51, 61), une ouverture d'entrée (58, 68) et une ouverture de sortie (59, 69),
    caractérisée en ce que la chambre d'insonorisation est divisée par une ou plusieurs cloisons (55, 63a, 65) parallèles à la direction axiale en deux parties de chambre (51b-e, 61b-d) ou plus, qui définissent conjointement une chambre à passages multiples, où un tube intérieur (52b-e, 62b, d), qui guide du gaz à travers la chambre d'insonorisation, est aménagé à travers chaque partie de chambre, et
    plusieurs fentes (54, 64) sont ménagées sur les tubes intérieurs en étant orientées sensiblement dans la direction périphérique, où la majeure partie du gaz circule à travers le tube intérieur.
  2. Machine à pistons rotatifs (10) à silencieux selon la revendication 1, caractérisée en ce que les fentes sont séparées dans la direction périphérique par des éléments d'écartement (25).
  3. Machine à pistons rotatifs (10) à silencieux selon la revendication 2, caractérisée en ce que le rapport entre la surface des éléments d'écartement et la surface des fentes est inférieur à 30 %.
  4. Machine à pistons rotatifs (10) à silencieux selon la revendication 2, caractérisée en ce que le rapport entre la surface des éléments d'écartement et la surface des fentes est inférieur à 25 %.
  5. Machine à pistons rotatifs (10) à silencieux selon la revendication 2, caractérisée en ce que le rapport entre la surface des éléments d'écartement et la surface des fentes est inférieur à 20 %.
  6. Machine à pistons rotatifs (10) à silencieux selon l'une quelconque des revendications précédentes, caractérisée en ce que les fentes (24, 34, 44, 54, 64) sont ménagées dans la direction d'écoulement sur le tiers avant et/ou le tiers central et/ou le tiers arrière du tube intérieur (22, 32, 42, 52, 62).
  7. Machine à pistons rotatifs (10) à silencieux selon l'une quelconque des revendications précédentes, caractérisée en ce que le silencieux (30, 40, 50, 60) est divisé par au moins une cloison (33, 43, 53, 63), de telle manière que cette dernière/ces dernières définit/définissent plusieurs chambres d'insonorisation (31a-c ; 41a-c ; 51a-c ; 61a-c) dans la direction d'écoulement, où un tube intérieur (32 ; 42a, b ; 52bd ; d) traverse au moins une chambre d'insonorisation.
  8. Machine à pistons rotatifs (10) à silencieux selon l'une quelconque des revendications précédentes, caractérisée en ce que les axes de l'ouverture d'entrée (48, 58) et de l'ouverture de sortie (49, 59) du silencieux (40, 50) forment un angle mutuel de sensiblement 90°.
EP06010289.4A 2006-05-18 2006-05-18 Machine à pistons rotatifs avec dispositif silencieux Active EP1857682B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
ES06010289.4T ES2581731T3 (es) 2006-05-18 2006-05-18 Máquina de émbolos rotativos de funcionamiento en seco con silenciador reactivo
EP06010289.4A EP1857682B1 (fr) 2006-05-18 2006-05-18 Machine à pistons rotatifs avec dispositif silencieux

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP06010289.4A EP1857682B1 (fr) 2006-05-18 2006-05-18 Machine à pistons rotatifs avec dispositif silencieux

Publications (2)

Publication Number Publication Date
EP1857682A1 EP1857682A1 (fr) 2007-11-21
EP1857682B1 true EP1857682B1 (fr) 2016-05-04

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ID=37075668

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06010289.4A Active EP1857682B1 (fr) 2006-05-18 2006-05-18 Machine à pistons rotatifs avec dispositif silencieux

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EP (1) EP1857682B1 (fr)
ES (1) ES2581731T3 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20120020824A1 (en) * 2010-07-20 2012-01-26 Paul Xiubao Huang Roots supercharger with a shunt pulsation trap
CN103603795B (zh) * 2012-09-05 2016-01-27 厦门嘉达环保建造工程有限公司 液压消声器
CN107170436A (zh) * 2017-07-26 2017-09-15 安徽理工大学 一种折叠式共振消音方法与复合装置

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR945632A (fr) * 1946-04-24 1949-05-10 Vokes Ltd Procédé et silencieux à filtres pour assourdir le bruit de gaz d'admission ou d'échappement
DE1166970B (de) * 1955-11-21 1964-04-02 Aerzener Maschinenfabrik G M B Resonanzschalldaempfer fuer zweiwellige Drehkolbenmaschinen
US5214937A (en) * 1991-10-28 1993-06-01 Carrier Corporation Integral oil separator and muffler
DE9113962U1 (de) * 1991-11-09 1992-02-27 Wilms, Peter, 4355 Waltrop Schalldämpfer für einen Schraubenverdichter
NL1006892C2 (nl) * 1997-08-29 1999-03-02 Q E International Bv Pulsatiedemper.
FI113892B (fi) * 1998-09-30 2004-06-30 Metso Paper Inc Reaktiivinen äänenvaimennin teollisuuden ilmakanavia varten ja sen käyttö
DE19855708B4 (de) * 1998-12-03 2009-04-30 Denker, Dietrich, Prof. Dr.-Ing. Rohrkammerdämpfer

Also Published As

Publication number Publication date
EP1857682A1 (fr) 2007-11-21
ES2581731T3 (es) 2016-09-07

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