EP1715188A1 - Silencieux développé pour et destiné à un compresseur - Google Patents

Silencieux développé pour et destiné à un compresseur Download PDF

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Publication number
EP1715188A1
EP1715188A1 EP05008836A EP05008836A EP1715188A1 EP 1715188 A1 EP1715188 A1 EP 1715188A1 EP 05008836 A EP05008836 A EP 05008836A EP 05008836 A EP05008836 A EP 05008836A EP 1715188 A1 EP1715188 A1 EP 1715188A1
Authority
EP
European Patent Office
Prior art keywords
branch
compressor
gas flow
silencer according
silencer
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.)
Withdrawn
Application number
EP05008836A
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German (de)
English (en)
Inventor
Andreas Dr. Foerster
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.)
Kaeser Kompressoren GmbH
Original Assignee
Kaeser Kompressoren 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 Kaeser Kompressoren GmbH filed Critical Kaeser Kompressoren GmbH
Priority to EP05008836A priority Critical patent/EP1715188A1/fr
Priority to EP06005095.2A priority patent/EP1715189B1/fr
Priority to US11/407,892 priority patent/US8142172B2/en
Priority to CN2006100758630A priority patent/CN1851244B/zh
Priority to JP2006119246A priority patent/JP4976046B2/ja
Publication of EP1715188A1 publication Critical patent/EP1715188A1/fr
Withdrawn legal-status Critical Current

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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
    • 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
    • F04C2220/00—Application
    • F04C2220/10—Vacuum

Definitions

  • the invention relates to a muffler designed and determined for a compressor or a vacuum pump, in particular for a compressor operating on the displacement principle, or for a working on the principle of displacement vacuum pump or a gas stream, in particular compress an air stream, wherein the muffler an entry for the compressor leaving the gas stream and having an outlet, wherein within the muffler, a branch is provided, which comprises an inflow channel and two thereof branching off channel sections, wherein a first channel section is formed as a further main line for the gas stream and a second channel section as a closed end branch , Furthermore, the invention relates to a compressor equipped with such a silencer and to a method for reducing pulsations in a gas flow generated by a compressor.
  • the pulsations with relevant amplitude are usually in a wide frequency range of typically 200 Hz to 10 KHz. Due to the tonal nature of the pulsation (main ejection sequence and its harmonics), the emitted sounds are subjectively unpleasant.
  • the Hauptausschubftequcnzen can vary considerably within a compressor series, which consists essentially of identical components, due to various influences. On the one hand, often a speed control for delivery quantity adjustment, for example, with the aid of a frequency converter, made. Furthermore, individual compressors are often delivered with unceretzlich constructed gear ratios in the drive of the compressor stages for power / pressure adjustment. Finally, in a compressor series individual compressors are connected in operation to 50 Hz power grids, other compressors to 60 Hz power grids.
  • Narrow-band damping methods with low dissipation are therefore less suitable under the above-described boundary conditions, because either a plurality of differently tuned for a compressor
  • the object of the present invention is to propose a particularly effective, in particular also broadband, silencer for a compressor or a vacuum pump as well as a method for reducing pulsations in a gas flow generated by a compressor or a vacuum pump.
  • a central idea of the present invention is that the branch has an axial preferred direction A, which is aligned parallel to the flow direction of the gas flow in the inflow channel, such that the gas flow strikes at least substantially frontally on the end closed branch.
  • the invention is therefore based on the consideration that the sound-induced alternating flow in the gas flow is particularly well attenuated when a closed end branch is directed into the main flow of the gas stream, that the gas flow is directed frontally on the branch.
  • the continuing main line is furthermore to be designed or aligned such that the gas flow exits the branch in a direction transverse to the gas flow in the inflow channel.
  • a further main line here is any configuration of a flow guide to understand how in particular a formed between inflow and branch 360 ° annular gap or partial annular gap of less than 360 °, in particular a branching tube with a circular or polygonal cross-section, etc.
  • the branch and the inflow channel are aligned coaxially or at least substantially coaxially with each other, i. the projection of their cross-sections does not result in a significant offset but rather is essentially concentric.
  • the branch can be subdivided by inner walls into sub-volumes, which are each assigned a subset of the recesses and a corresponding section of the cover element and which act as largely independent damping elements, in particular as independent resonators, with different resonance frequencies.
  • the extent of the partial volumes in the direction of the gas flow in the inflow channel can also be different in order to achieve different reflection properties.
  • the damping behavior of the silencer on the arrangement and / or size and / or number of recesses in the cover element or the thickness of the cover element, in particular taking into account the Resonatotvolumens or the resonator sub-volumes can be fine tuned. In particular, this can both resonance frequencies and broadband of the damper can be adjusted.
  • the parameters of the recesses are selected such that, during operation of the muffler, due to the gas volumes pumped back and forth through the recesses, there are significant dissipative effects which give the muffler the desired broadbandness.
  • the main dimension of a housing housing the branch in the direction of its cylinder longitudinal axis is preferably ⁇ / 4 of the Hauptausschubfrequenz the compressor system.
  • the arrangement of the outlet channel as part of the secondary main line is preferably such that an outlet cross-section adjacent chamber wall of the branch at a shallow angle (but not perpendicular) to the longitudinal axis of the outlet channel, so that no reflective planes for standing waves are formed in subsequent pipes ,
  • the arrangement of the outlet channel is thus preferably tangential or axial to the chamber wall of the branch.
  • the longitudinal axis of the branch is arranged eccentrically to the longitudinal axis of the housing, wherein the offset is selected so that the cross section of an annular space, which forms between branch and housing, increases in the direction of the outlet.
  • cover element preferably substantially orthogonal to the preferred direction of the branch, namely according to a first alternative embodiment such that the cover element is arranged at the end of the branch facing the inflow channel and in a second alternative and in principle preferred Embodiment such that the cover element is arranged offset in relation to the inflow channel facing the end of the branch into the branch.
  • the branch is formed as a resonator, i. the silencing behavior of the branch is at least partially based on the fact that the branch in the sense of a Helmholtz resonator is preferably tuned to the main discharge frequency.
  • the subvolumes and their associated sections of the cover element and of the recesses can be tuned to a plurality of different resonance frequencies, preferably the main extension frequency and / or their harmonics.
  • the branch acts at least partially (also) as a quarter wave tube.
  • At least one constriction to be passed from the gas flow is formed within the branch, in particular downstream of the branch.
  • the bottleneck acts as an impedance jump and thus can still significantly improve the sound damping properties of the muffler according to the invention.
  • the constriction is formed in the outgoing transversely to the inflow main line.
  • the muffler with the branching according to the invention may be formed in a substantially flachzylindrischcn housing with two end faces and a lateral surface arranged therebetween, wherein on a first end face of the inlet and on the lateral surface of the outlet is provided. This creates a particularly compact and at the same time robust silencer, in which the branch constructed according to the invention can be implemented particularly well.
  • the branch comprises a cup-shaped main body or is formed from a cup-shaped main body.
  • the second end face of the preferably flat-cylindrical housing is formed by an end plate of the cup-shaped main body is particularly preferred.
  • the silencer should be connected directly to the outlet or to the outlet of the vacuum pump by means of a sufficiently short pipe section.
  • a compressor or a vacuum pump in particular a compressor operating according to the displacement principle or a vacuum pump acting on the displacement principle, such as a Schtaubenkomptessor or a screw vacuum pump claimed as essential to the invention, the or a Kompressionskamtmer and an outlet and an comprising the outlet connected to the silencer according to the invention.
  • the apparent oddity that the muffler also has a strong effect on the sound-induced alternating flow in the outlet of the compressor or the vacuum pump itself is exercised, as explained.
  • the compressor or the compressor stage of the compressor or the vacuum pump is falsely intuitively regarded as a constant source of pulsation, which is why the "retroactive effect" is initially puzzling.
  • the pulsation source "compressor stage” does not characterize the entrance of the muffler to a steady pressure waveform signal, but the compressor stage is due to their Ausschubkinematik a "sonic fast source” (analogy: movable wall, or cyclically moving piston in the pipe, etc.).
  • the pressure profile at the outlet of the compressor stage or of the compressor or the vacuum pump can thus be positively influenced by a suitable silencer, ie its amplitude can be changed.
  • a method for reducing pulsations in a gas flow generated by a compressor or a vacuum pump, in particular by the displacement principle, such as a screw compressor or a vacuum pump, is claimed, wherein the gas flow through an inlet into a silencer is led out and through an outlet from this, wherein within the silencer a branch is provided which comprises an inflow channel and two thereof branching off channel sections, wherein a first channel section as a further main line for the gas stream and a second channel section formed as a closed end branch and the method is characterized by the following measures: Generating and exploiting a counter-application of the sound-induced alternating flow by a reflection and / or resonance behavior in the branch, with an axial advantage oriented parallel to the flow direction of the gas stream in the inflow channel to reduce the pulsations in the gas stream.
  • This counteracting by a reflection and / or resonance behavior can additionally by dissipative measures, such as generating and exploiting dissipative damping processes in the "neck" of the Helmholtz resonator (For example, corresponds to the above cover element, preferably in the form of a perforated plate) are supported.
  • dissipative measures such as generating and exploiting dissipative damping processes in the "neck" of the Helmholtz resonator (For example, corresponds to the above cover element, preferably in the form of a perforated plate) are supported.
  • the gas stream is further guided in the immediate vicinity of the counter-application generated in the branch, in particular downstream of it through a constriction, in order to produce an impedance discontinuity.
  • the gas stream leaving the branching is preferably led out of the branch at such a point in which reflection-induced or resonance-induced extinction or reduction of the pulsation is present, for example near the plane of the inflow cross section.
  • FIG. 1 schematically illustrates a screw compressor 30 having an inlet channel 32 which opens into a compression chamber 29, a compression chamber 29, a compressor screw 33 mounted therein, and an outlet 31.
  • a eifindungswasher muffler 11 is connected Immediately to the outlet 31 and to a pipe section 34 .
  • the muffler 11 is designed so that it not only causes a sound attenuation of the gas flow leaving the muffler 11, but also a reaction in the inflowing gas flow, such that the pulsations of the gas flow in the outlet 31 of the compression chamber 29 are significantly reduced.
  • the muffler 11 should be connected either directly to the outlet 31 or by means of a relatively short pipe or pipe section 34 relatively close to the outlet 31.
  • FIG. 2 shows first a sectional view of the silencer 11 along the line II-II in FIG. 3 and FIG. 3 a top view of the silencer 11.
  • the silencer 11 comprises a substantially flat-cylindrical housing 20, which consists of two separable elements, namely a housing base body 35 and a cup-shaped base body 24 used therein.
  • the flat-cylindrical housing 20 forms two end surfaces 21, 22 and a lateral surface 23 arranged therebetween.
  • substantially circular end face 21 is centrally formed an inlet 12 in the form of an opening for the inflowing gas stream; orthogonal to the extent of the opening of the inlet 12 in the first end face 21 is an opening 13 defining an outlet formed in the lateral surface 23 of the housing 20.
  • the outlet 13 can in principle be oriented arbitrarily in the lateral surface, preferably also tangentially or "obliquely axially"
  • a branch 14 is formed in the housing 20 of the muffler 11 for the gas flow, wherein the branch 14 is defined by an inflow channel 15, a branch 17 and a secondary main line 16.
  • inflow channel 15 and further main line 16 are formed only very briefly and are continued in the respectively connected lines.
  • the branch 17 is, however, completely housed within the housing 20 of the muffler 11 and here by the aforementioned cup-shaped base body 24 images.
  • the cup-shaped basic body 24 (see also FIG. 6) is inserted into the housing base body 35 from a side opposite the first end surface 21.
  • the two-part flat cylindrical housing 20 thus comprises the housing base body 35, which here forms the lateral surface 23 and the first end surface 21, and the cup-shaped base body 24, the housed in the interior of the housing 20 branch 17 and in the present embodiment at the same time the flat cylindrical housing 20 forms a final second end face 22 in the form of a fin 49 provided with ribs 49,
  • a circumferential sealing element 36 can still be effective in order to effect a seal between the two partial elements of the substantially flat-cylindrical housing 20.
  • the branch 17 forming cup-shaped base body 24 may be permanently connected to the housing base body 35, such as welded or soldered; preferred is a releasable connection, in particular a compound over a plurality of screws 37 which engage in internally threaded bores 38, which are distributed over a flange 39 formed on the housing base body 35.
  • the branch 17 formed by the cup-shaped base body 24 has in the preferred embodiment here as the housing 20 also has a cylindrical basic shape and has an opening 40 which is directed to the inlet 12 so that the gas flow from the inflow channel 15 frontally on the opening 40 or meets the branch 17.
  • the branch 17 or the cup-shaped basic body 24 is limited in the present embodiment by a cylindrical chamber wall 41.
  • a termination surface 28 is formed at the opposite end of the opening 40.
  • the end surface 28 is formed by an inner side of the end plate 48 so that the end plate 48 simultaneously forms part of the outer wall of the housing 20 as well as the end surface 28 as part of the branch 17.
  • the cross-section of the branch 17, overlying the opening 40 of the branch 17, is set back towards the end surface 23 and has a cover element 19 provided with a plurality of recesses 18 (see FIGS. 3, 5 and 6) ,
  • the cover element 19 can be formed in particular as a perforated plate.
  • the cover member 19 is mounted on columnar projections 42 to 45 via screws 46 which engage in the female threaded holes 47 in the columnar projections 42 to 45.
  • a first type of columnar projections 42 to 44 is formed on the inside of the chamber wall 41.
  • a central columnar projection 45 spaced from the chamber wall 41 is formed projectingly in the central region over the end surface 28.
  • a packing with absorbent material eg a mineral wool packing, a sintered body made of metal or ceramic, an open-pored metal foam, a ceramic foam, or the like
  • a packing with absorbent material eg a mineral wool packing, a sintered body made of metal or ceramic, an open-pored metal foam, a ceramic foam, or the like
  • Fig. 7 the pot-shaped base body is shown in a perspective view.
  • the cup-shaped base body comprises the end plate 48 which simultaneously defines the end face 22 of the housing 20 and which is provided with ribs 49 for increasing the torsional stiffness.
  • Integrally formed on the end plate 48 is the chamber wall 41 which laterally delimits the branch 17 forming a resonator chamber 26.
  • the end plate 48 further comprises on its outer periphery on the chamber wall 41 side facing a flange 50 with holes 51, respectively matched to the flange 39 and the internally threaded holes 38 on the housing body 35.
  • Fig, 8 is still a side view of the muffler 11 in the assembled State shown.
  • the pot-shaped main body 24 is preferably positioned in the housing so that its chamber wall 41 obstructs the exit of the gas flow through the continuing main line 16, in particular through the outlet 13, as little as possible.
  • the gas flow should be effected as far as possible tangentially or axially on the chamber wall 41, in order to form no reflecting planes for standing waves in subsequent pipelines.
  • the entering through the inlet 12 into the muffler 11 gas flow hits the front of the branch 17, which causes an effective damping of the sound-induced alternating flow.
  • the main flow is deflected and passes through a constriction 27, which is formed here as an annular gap 53 between the end face of the chamber wall 41 and the inlet 12 associated inside of the housing base body 35, and flows through the annular space 52 in the direction of the outlet 13 and then out of the muffler 11.
  • the annular gap 53 is located substantially in the plane of the inflow channel 15, in which there is extinction or reduction of the pulsation due to reflection and resonance.
  • a partial volume 54 is formed by the front end of the chamber wall 41, the cover member 19 of the branch 17, the annular gap 53, the inlet 12 and associated portions of the inner wall of the housing body 35.
  • the flow direction through the annular gap 53 is on the entire circumference of the annular gap 53 substantially perpendicular to the flow direction in the inlet 12.
  • a flow deflection by 90 ° takes place in the annular gap 53, a flow deflection by 90 °.
  • the defined by the annular gap 53 bottleneck 27 causes an impedance jump for the impacted by sound alternating flow gas flow.
  • the branch 17 forming a resonator chamber 26 is preferably tuned to the main feed frequency or a low harmonic of the main feed rate det compressor system.
  • the preferred muffler specifically described herein is characterized by a number of features favorable for use in a compressor.
  • the muffler has a very broadband effect and achieves a good damping of the pulsations in the typical frequency range of 200 Hz to 10 KHz.
  • Conventional sound attenuation mechanisms with a broadband effect such as interference attenuation by reflection at successive cross-sectional jumps (impedance jumps) or damping by dissipative silencers (eg absorption or absorption) Throttle damper) are in part associated with considerable disadvantages for use in a compressor system.
  • Interference dampers based on impedance jumps must have significant cross-sectional ratios for good efficiency. This makes implementation in piping difficult due to the required dimensions. Throttle damper prohibit due to the pressure losses.
  • Absorption dampers generally require minimum layer thicknesses of the absorbent media on the order of ⁇ / 4, which is lower in the og. Frequency range leads to unacceptable layer thicknesses or construction volumes.
  • the absorbent materials e.g., mineral wool, porous structures
  • Another problem is the lack of temperature resistance of some absorbent materials.
  • the muffler described with reference to FIGS. 2 to 8 overcomes the aforementioned disadvantages and is characterized by a good damping behavior in the frequency range in question.
  • there is only a small differential pressure so that the resulting due to the differential pressure deterioration of the compressor efficiency when installed in a compressor system in the concretely proposed embodiment is extremely low.
  • the specifically described embodiment of the muffler is further characterized by a compact design, so that the muffler can be accommodated to save space within a compressor system and in particular long pipes are avoided.
  • the silencer according to the invention in the preferred embodiment, pressure-bearing, that is, formed intrinsically stable.
  • the concretely proposed design can easily be produced as a pressure-bearing housing (typically loadable with at least 11 bar).
  • the concretely proposed design has also proven to be very temperature resistant, so that gas temperatures can be passed through at least 250 ° C easily.
  • the muffler according to the invention is characterized in a preferred, optional embodiment in that can be completely dispensed absorbent materials such as mineral wool.
  • a relatively stiff construction is achieved in the two-part housing, so that the natural frequencies are so high that substantially no resonance excitation occurs as a result of the pulsations of the gas flow.
  • the compact design of the concrete preferred muffler allows a "rigid" construction, which leads to high fiigenfrequetlzen and such eigenforms, in which the bending wavelengths of the respective wall sections of the outer contour are smaller than the wavelengths of airborne sound at said natural frequencies, resulting in a low radiation.
  • a sound attenuation is achieved by a combination of several Schalldämpfungsfastien, namely concretely by a Helmholtz resonator with additional dissipation (flow losses in the perforated plate), a ⁇ / 4 tube, an impedance muffler and a tap of the main flow from a range of low pulsations as a result of reflection and resonance-induced extinction,
  • a part of the effectiveness of the muffler described may not only be due to the action mechanisms described, but also that the sound-induced alternating flow, ie the superimposed pressure pulsation component is reduced by a very effective dissipative perforated plate, while the main flow in front of the perforated plate of the Spreading direction of the pulsation branches and yet undergoes only a small pressure drop, because the perforated plate is not flowed through by the main flow.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP05008836A 2005-04-22 2005-04-22 Silencieux développé pour et destiné à un compresseur Withdrawn EP1715188A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP05008836A EP1715188A1 (fr) 2005-04-22 2005-04-22 Silencieux développé pour et destiné à un compresseur
EP06005095.2A EP1715189B1 (fr) 2005-04-22 2006-03-13 Silencieux développé pour et destiné à un compresseur
US11/407,892 US8142172B2 (en) 2005-04-22 2006-04-21 Silencer designed and intended for a compressor
CN2006100758630A CN1851244B (zh) 2005-04-22 2006-04-24 消声装置、压缩机或真空泵以及降低气流脉冲的方法
JP2006119246A JP4976046B2 (ja) 2005-04-22 2006-04-24 コンプレッサ用として構成され、かつ想定された消音器

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP05008836A EP1715188A1 (fr) 2005-04-22 2005-04-22 Silencieux développé pour et destiné à un compresseur

Publications (1)

Publication Number Publication Date
EP1715188A1 true EP1715188A1 (fr) 2006-10-25

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EP05008836A Withdrawn EP1715188A1 (fr) 2005-04-22 2005-04-22 Silencieux développé pour et destiné à un compresseur

Country Status (2)

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EP (1) EP1715188A1 (fr)
CN (1) CN1851244B (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10180140B2 (en) 2016-09-30 2019-01-15 Ingersoll-Rand Company Pulsation damper for compressors
WO2021219307A1 (fr) * 2020-04-29 2021-11-04 Pfeiffer Vacuum Pompe à vide primaire et installation
FR3109806A1 (fr) * 2020-04-29 2021-11-05 Pfeiffer Vacuum Technology AG Pompe à vide primaire et Installation
FR3112176A1 (fr) * 2020-10-09 2022-01-07 Pfeiffer Vacuum Pompe à vide primaire et Installation
CN114576167A (zh) * 2020-11-30 2022-06-03 复盛实业(上海)有限公司 一种压缩机的机体
EP3356677B1 (fr) * 2015-10-02 2024-01-24 Carrier Corporation Compresseur à vis avec groupes de résonateurs

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CN102297135B (zh) * 2010-06-25 2013-09-04 宝山钢铁股份有限公司 大功率双叶逆流冷却式罗茨真空泵非线性消声方法和消声器
EP3540207B1 (fr) * 2013-12-09 2021-09-29 Dayco IP Holdings, LLC Unité d'atténuation de bruit pour systèmes moteur
RU2737072C2 (ru) 2015-08-11 2020-11-24 Кэрриер Корпорейшн Компрессор, способ его использования и система паровой компрессии
CN110486351B (zh) * 2019-09-11 2022-04-05 襄阳元创汽车零部件实业有限公司 一种500t送料机排气消音器及其操作方法

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Publication number Priority date Publication date Assignee Title
US2990907A (en) * 1959-06-11 1961-07-04 Wilhelm S Everett Acoustic filter
FR2498681A1 (fr) * 1981-01-28 1982-07-30 Sonica Dispositif de detente silencieuse de gaz sous pression
US5101931A (en) * 1990-05-23 1992-04-07 Copeland Corporation Discharge muffler and method
JPH0828479A (ja) * 1994-07-12 1996-01-30 Kobe Steel Ltd スクリュ冷凍機
JP2005009458A (ja) * 2003-06-20 2005-01-13 Toshiba Kyaria Kk 圧縮機

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Publication number Priority date Publication date Assignee Title
TW366388B (en) * 1997-08-13 1999-08-11 Honda Motor Co Ltd Intake silencer system

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2990907A (en) * 1959-06-11 1961-07-04 Wilhelm S Everett Acoustic filter
FR2498681A1 (fr) * 1981-01-28 1982-07-30 Sonica Dispositif de detente silencieuse de gaz sous pression
US5101931A (en) * 1990-05-23 1992-04-07 Copeland Corporation Discharge muffler and method
JPH0828479A (ja) * 1994-07-12 1996-01-30 Kobe Steel Ltd スクリュ冷凍機
JP2005009458A (ja) * 2003-06-20 2005-01-13 Toshiba Kyaria Kk 圧縮機

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Title
PATENT ABSTRACTS OF JAPAN vol. 1996, no. 05 31 May 1996 (1996-05-31) *
PATENT ABSTRACTS OF JAPAN vol. 2003, no. 12 5 December 2003 (2003-12-05) *

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3356677B1 (fr) * 2015-10-02 2024-01-24 Carrier Corporation Compresseur à vis avec groupes de résonateurs
US10180140B2 (en) 2016-09-30 2019-01-15 Ingersoll-Rand Company Pulsation damper for compressors
WO2021219307A1 (fr) * 2020-04-29 2021-11-04 Pfeiffer Vacuum Pompe à vide primaire et installation
FR3109806A1 (fr) * 2020-04-29 2021-11-05 Pfeiffer Vacuum Technology AG Pompe à vide primaire et Installation
FR3112176A1 (fr) * 2020-10-09 2022-01-07 Pfeiffer Vacuum Pompe à vide primaire et Installation
CN114576167A (zh) * 2020-11-30 2022-06-03 复盛实业(上海)有限公司 一种压缩机的机体

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CN1851244B (zh) 2012-05-02
CN1851244A (zh) 2006-10-25

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