EP2396552B1 - Amortisseur de bruit pour une turbomachine ou machine à piston - Google Patents

Amortisseur de bruit pour une turbomachine ou machine à piston Download PDF

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Publication number
EP2396552B1
EP2396552B1 EP09795312.9A EP09795312A EP2396552B1 EP 2396552 B1 EP2396552 B1 EP 2396552B1 EP 09795312 A EP09795312 A EP 09795312A EP 2396552 B1 EP2396552 B1 EP 2396552B1
Authority
EP
European Patent Office
Prior art keywords
disc
housing
vibration
arrangement
pipe
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.)
Not-in-force
Application number
EP09795312.9A
Other languages
German (de)
English (en)
Other versions
EP2396552A2 (fr
Inventor
Richard BÜSSOW
Ralf GÖDDE
Udo Thiel
Thomas Barwanietz
Daniela Joswig
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.)
Everllence SE
Original Assignee
MAN Diesel and Turbo SE
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 MAN Diesel and Turbo SE filed Critical MAN Diesel and Turbo SE
Publication of EP2396552A2 publication Critical patent/EP2396552A2/fr
Application granted granted Critical
Publication of EP2396552B1 publication Critical patent/EP2396552B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0027—Pulsation and noise damping means
    • F04B39/0044—Pulsation and noise damping means with vibration damping supports
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/001—Noise damping
    • F04B53/003—Noise damping by damping supports
    • 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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/12—Vibration

Definitions

  • the invention relates to a silencer for a flow or piston machine, in particular for a screw compressor or expander, according to the preamble of claim 1.
  • a silencer is known in the fluid flows around a central damper gate, which are housed in a housing, To reduce the transmission and radiation of sound, the housing is surrounded on its outside with a sand jacket.
  • the generic US 5 507 159 A discloses a collector assembly of a refrigerator compressor, wherein in the collector located in the disc elements at the ends of which cushions for vibration damping are present.
  • JP 2000 21 2228 A there is disclosed an exhaust muffler which provides damping members for sound attenuation at the ends of disk members connecting the muffler outer mantle to the inner exhaust pipe. Further silencers are in GB 2 389 150A .
  • the object of the present invention is to provide an improved silencer for a flow or piston machine, in particular for a screw compressor.
  • a silencer according to the preamble of claim 1 is further developed by the characterizing features of claim 1.
  • Claim 10 provides a method for producing a special embodiment of the silencer according to the invention under protection, the further subclaims relate to advantageous developments.
  • the present invention is based, on the one hand, on the recognition that the previous cladding with sand does not optimally damp vibrations of the housing since the sand does not uniformly bear everywhere due to the gravitational effect. Therefore, it is proposed according to a preferred embodiment of the invention to cover the housing on its outside by a vibration-damping jacket made of dimensionally stable material, so that there is a uniform contact between the housing and the jacket.
  • a vibration-damping jacket made of dimensionally stable material, so that there is a uniform contact between the housing and the jacket.
  • the use of dimensionally stable material can also simplify the attachment of the shell to the housing.
  • the present invention takes into account the fact that structure-borne noise in silencers, as they have been used according to in-house practice, takes place in the frequency ranges relevant in the operation in substantial proportions on the inner tubes, so that the sole damping of the housing on its outside by the Sandmantel the transmission and radiation of sound is not optimally reduced. Therefore, it is proposed according to the invention, which may be particularly preferably combined with the above-described shell of dimensionally stable material, to arrange between a pipe assembly and the housing an elastic, vibration damping and disc-shaped element. As a result, the tube arrangement can be partially decoupled in terms of vibration technology and, in particular, a transmission of structure-borne noise can thus be reduced.
  • An inventive silencer is provided for a flow or piston machine, in particular a compressor, and is used with particular advantage in screw compressors, which are exposed to strong periodic vibration excitation due to their mechanism of action, It comprises a single, or preferably, multi-part housing, a tube assembly with one or, preferably, a plurality of tubes for guiding a fluid of the flow or.
  • Piston machine such as a process gas, a liquid or the like, and a disc assembly with one or, preferably a plurality of discs which are releasably clamped, for example by a screw frictionally clamped or insoluble, for example by welding, are attached to the housing and carry the tubes of the tube assembly ,
  • one or more disks may also be formed, at least in part, integrally with the housing, for example, be formed or formed.
  • At least one elastic, vibration-damping element is arranged between the tube arrangement and the housing in order to at least partially decouple the tube arrangement with respect to the housing in terms of vibration technology.
  • One or more, preferably all, elastic elements are designed so that they absorb vibrations and, for this purpose, preferably have higher damping constants with regard to relevant frequency ranges.
  • a higher damping constant can be characterized for example by a sufficiently large amplitude reduction in the frequency response of the muffler in the range of relevant frequencies.
  • an elastic element made of an elastomer, a thermoset or thermoset or sealing materials, which are also used for flange connections exist.
  • vibration-damping elements Due to the vibration decoupling resonance frequencies of the muffler and amplitude peaks in its frequency response, ie the vibration response to excitations on the frequency of the excitation shifted, and thus the transmission and emission of sound can be reduced. By vibration-damping elements, additional vibration energy can be dissipated, thus further reducing the transmission and emission of sound.
  • One or more, preferably all discs of the disc assembly have an elastic element.
  • a disk-shaped, elastic element for example made of a plastic such as polystyrene, sealing materials or other viscoelastic material, in particular made of rubber, on a metal layer of the disc, preferably insoluble, attached, for example, hereby glued, vulcanized or sprayed.
  • a metal layer of the disc preferably insoluble, attached, for example, hereby glued, vulcanized or sprayed.
  • Each two Metalliagen surrounded sandwich a disc-shaped elastic element.
  • the discs are bending or völbelastisch and thus decouple the tubes relative to the housing.
  • a vibration damping member on the disks dissipates vibratory energy in both the tubes suspended from the discs and vibrational energy in the fluid impinging on the discs.
  • the tube assembly is frictionally secured to the disc assembly by, for example, tubes of the tube assembly in bores or sleeves are pushed or pushed, which are formed in slices or attached thereto.
  • elastic, preferably vibration damping elements for example made of plastic, rubber or other viscoelastic materials can be arranged in the contact region between the tube and disc.
  • one or more, preferably all tubes of the tube assembly have openings transverse to a direction of flow.
  • pipes can be made, for example, from perforated plates, wire mesh or the like. The fluid flowing through these openings reduces vibrations, and the thermodynamic property and weight of the muffler are improved.
  • damping material such as mineral wool, may be arranged to further dampen vibrations in the fluid.
  • the diameter of the tubes is chosen so small that transverse modes can be reduced in the muffler, this is the product of, in particular hydraulic, diameter D of the tube, the circle number ⁇ ; and the ejection frequency f A of the flow or piston machine advantageously at most twice, in particular at most 1.8 times the speed of sound c of the fluid of the flow or piston machine, so that the following applies: D ⁇ 1 . 8th ⁇ c f A ⁇ ⁇ ,
  • tubes are preferably distributed equidistant over the circumference of the housing.
  • the housing may be completely or partially covered on its outside with a vibration-damping jacket of dimensionally stable material.
  • This coat shifts on the one hand its mass resonance frequencies of the muffler and amplitude peaks in its frequency response, on the other he attenuates in particular higher-frequency vibrations.
  • the dimensionally stable material thereby improves the contact and thus the vibration-technical coupling with the housing.
  • dimensionally stable material has better damping properties.
  • dimensionally stable jacket material is that, in contrast to sand, it can be arranged better on the housing.
  • it may be applied to the housing in a liquid or viscous state, for example by spraying it on or immersing the housing in a bath of dimensionally stable material, and then solidifying it on the housing, for example by itself, with the addition of heat, in reaction with air. or cure by addition of crosslinking agent.
  • the dimensionally stable material is adhesive, i.e. adheres to other surfaces. This further improves the contact and thus the vibration control coupling with the housing even further and also simplifies the attachment to the housing.
  • fiber cement mortar or plastic in particular polyurethane have shown.
  • Fig. 1 shows the upper half of a muffler according to an embodiment of the present invention in longitudinal section. It comprises a three-part housing with an upstream in the flow direction front housing part 1.1, one with this via flanges, as in Fig. 1 indicated by dash-dotted lines, screwed middle part 1.2 and a downstream rear housing part 1.3, which is formed substantially symmetrically to the front housing part 1.1 and is also bolted to the central part 1.2 via flanges.
  • a disc 3 or 4 of a disc assembly is frictionally clamped
  • These discs are constructed in three parts and each comprise an elastic disc 3.3 or 4.3, which sandwiched between metal layers 3.1, 3.2 and 4.1, 4.2 added and connected to them.
  • the elastic discs 3.3, 4.3 are made of polystyrene and glued to the metal layers 3.1, 3.2 and 4.1, 4.2.
  • the disks 3, 4 have three evenly distributed over the inner circumference of the housing bores, which are penetrated by sleeves 3.4 and 4.4 respectively. These sleeves have on their inner circumference a paragraph and are welded on its outer periphery with the discs 3 and 4, as in Fig.1 indicated in a customary manner by filled triangles.
  • one-piece disc 5 is welded, which has aligned with the holes of the discs 3, 4 holes in the sleeves 5.1 are also inserted, which have on their inner circumference a central, inwardly projecting shoulder and are welded to the disc 5. This disc increases the stiffness of the muffler and in particular counteracts vibrations.
  • a dimensionally stable jacket 9 made of fiber cement mortar or polyurethane is applied.
  • the jacket 9 can be omitted from dimensionally stable material.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Exhaust Silencers (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Compressor (AREA)
  • Supercharger (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
  • Vibration Prevention Devices (AREA)

Claims (10)

  1. Silencieux d'échappement pour un moteur à pistons ou une turbomachine, comportant :
    - un carter (1.1-1.3) ;
    - un agencement de disques comportant au moins un disque (3,4,5), qui est fixé sur le carter ; et
    - un agencement de tuyaux fixé sur l'agencement de disques comportant au moins un tuyau (2.1,2.2) pour guider un fluide du moteur à pistons, resp. de la turbomachine, dans lequel
    - entre l'agencement de tuyaux et le carter au moins un élément (3.3,4.3,6,7,8) à configuration élastique, amortissant les vibrations est disposé, et dans lequel
    - un disque (3.4) de l'agencement de disques présente un élément (3.3,4.3) à configuration élastique, amortissant les vibrations et en forme de disque, caractérisé en ce que un disque (3,4) de l'agencement de disques présente au moins une couche métallique (3.1,3.2,4.1,4.2) et un élément en forme de disque, à configuration élastique amortissant les vibrations fixé dessus, dans lequel respectivement deux couches métalliques entourent en forme de sandwich un élément en forme de disque, à configuration élastique et amortissant les vibrations.
  2. Silencieux d'échappement selon une des revendications précédentes, caractérisé en ce que entre l'agencement de disques et l'agencement de tuyaux est disposé un élément à configuration élastique, amortissant les vibrations (S,7,8).
  3. Silencieux d'échappement selon une des revendications précédentes, caractérisé en ce que l'agencement de tuyaux est fixé par friction sur l'agencement de disques.
  4. Silencieux d'échappement selon la revendication 3, caractérisé en ce que l'agencement de disques présente un manchon (3.4,4.4,5,1), dans lequel un tuyau (2.1,2.2) de l'agencement de tuyaux est renfermé par friction.
  5. Silencieux d'échappement selon une des revendications précédentes, caractérisé en ce que un tuyau (2.1) de l'agencement de tuyaux présente des ouvertures transversales à une direction d'écoulement.
  6. Silencieux d'échappement selon une des revendications précédentes, caractérisé en ce que un matériau d'amortissement est disposé à l'intérieur et/ou à l'extérieur de l'agencement de tuyaux.
  7. Silencieux d'échappement selon une des revendications précédentes, caractérisé en ce que le produit sur une circonférence (Dn) d'un tuyau de l'agencement de tuyaux et une fréquence de projection (fA) du moteur à pistons, respectivement de la turbomachine s'élève au maximum au double, notamment au maximum à 1,8 fois la vitesse du son (c) du fluide de la turbomachine, respectivement machine à pistons (D < 1,8c / {fAπ} < 2c/ fAn) .
  8. Silencieux d'échappement selon une des revendications précédentes, caractérisé par une gaine amortissant les vibrations (9) constituée d'un matériau dimensionnellement stable, qui recouvre le carter (2.2) au moins partiellement sur un côté extérieur.
  9. Silencieux d'échappement selon la revendication 8, caractérisé en ce que le matériau dimensionnellement stable comprend du mortier de ciment fibreux ou du plastique.
  10. Procédé de fabrication d'un silencieux d'échappement selon une des revendications 8 ou 9, caractérisé en ce que le matériau dimensionnellement stable est appliqué en l'état liquide sur le logement et y est fixé.
EP09795312.9A 2009-02-16 2009-11-20 Amortisseur de bruit pour une turbomachine ou machine à piston Not-in-force EP2396552B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009009168A DE102009009168A1 (de) 2009-02-16 2009-02-16 Schalldämpfer für eine Strömungs- oder Kolbenmaschine
PCT/DE2009/050064 WO2010091656A2 (fr) 2009-02-16 2009-11-20 Amortisseur de bruit pour une turbomachine ou machine à piston

Publications (2)

Publication Number Publication Date
EP2396552A2 EP2396552A2 (fr) 2011-12-21
EP2396552B1 true EP2396552B1 (fr) 2017-10-04

Family

ID=42338751

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09795312.9A Not-in-force EP2396552B1 (fr) 2009-02-16 2009-11-20 Amortisseur de bruit pour une turbomachine ou machine à piston

Country Status (6)

Country Link
US (1) US8550209B2 (fr)
EP (1) EP2396552B1 (fr)
JP (1) JP5484488B2 (fr)
CN (1) CN102317632B (fr)
DE (1) DE102009009168A1 (fr)
WO (1) WO2010091656A2 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012102349A1 (de) * 2012-03-20 2013-09-26 Bitzer Kühlmaschinenbau Gmbh Kältemittelverdichter
DE102014207023B3 (de) * 2014-04-11 2015-07-30 Magna Powertrain Hückeswagen GmbH Kraftfahrzeug-Vakuumpumpe mit Verklebung
KR20170027065A (ko) * 2015-09-01 2017-03-09 엘에스엠트론 주식회사 차량용 공명기
CN112412804B (zh) * 2020-10-13 2022-11-04 珠海格力节能环保制冷技术研究中心有限公司 一种复合形吸气口与排气口消音组件及压缩机
DE102021134652B3 (de) 2021-12-23 2023-05-11 Man Energy Solutions Se Schraubenkompressor

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Also Published As

Publication number Publication date
JP2012518107A (ja) 2012-08-09
DE102009009168A1 (de) 2010-08-19
CN102317632B (zh) 2015-11-25
JP5484488B2 (ja) 2014-05-07
US8550209B2 (en) 2013-10-08
WO2010091656A3 (fr) 2011-05-19
WO2010091656A4 (fr) 2011-07-14
WO2010091656A2 (fr) 2010-08-19
EP2396552A2 (fr) 2011-12-21
US20120048645A1 (en) 2012-03-01
CN102317632A (zh) 2012-01-11

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