EP1715189A1 - 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
EP1715189A1
EP1715189A1 EP06005095A EP06005095A EP1715189A1 EP 1715189 A1 EP1715189 A1 EP 1715189A1 EP 06005095 A EP06005095 A EP 06005095A EP 06005095 A EP06005095 A EP 06005095A EP 1715189 A1 EP1715189 A1 EP 1715189A1
Authority
EP
European Patent Office
Prior art keywords
branch
silencer according
silencer
gas flow
compressor
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.)
Granted
Application number
EP06005095A
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German (de)
English (en)
Other versions
EP1715189B1 (fr
Inventor
Andreas Dr. Förster
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 AG
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
Priority claimed from EP05008836A external-priority patent/EP1715188A1/fr
Application filed by Kaeser Kompressoren GmbH filed Critical Kaeser Kompressoren GmbH
Priority to EP06005095.2A priority Critical patent/EP1715189B1/fr
Priority to US11/407,892 priority patent/US8142172B2/en
Priority to JP2006119246A priority patent/JP4976046B2/ja
Priority to CN2006100758630A priority patent/CN1851244B/zh
Publication of EP1715189A1 publication Critical patent/EP1715189A1/fr
Application granted granted Critical
Publication of EP1715189B1 publication Critical patent/EP1715189B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S181/00—Acoustics
    • Y10S181/403—Refrigerator compresssor muffler

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 connected components are significantly stressed due to the pressure changes, which can lead to material damage due to fatigue (fatigue fractures, etc.) as a result of cyclic stress due to the primary pressure changes and / or the oscillations excited thereby.
  • the pulsations with relevant amplitude are usually in a wide frequency range of typically 200 Hz to 10 KHz. Due to the tonal character of the pulsation (main ejection frequency and its harmonic), the radiated noises are subjectively unpleasant.
  • the Hauptausschubfrequenzen can vary significantly 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 differently 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 under the above boundary conditions therefore less suitable because either a plurality of differently tuned muffler is required to achieve a certain broadband effect or vorzuhalten several muffler variants are, then to the individual compressor variants or their later operational environment are adapted. However, this is only possible if it is not a variable frequency compressor (for example, speed control).
  • 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 is here any configuration of a flow guide to understand, in particular a trained 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 via 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 resonator volume or the resonator partial volumes can be fine-tuned. In particular, both resonance frequencies and broadband of the damper can thereby 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 arrangement of the recesses in the cover element of the branch with a small distance, preferably less than ⁇ / 10 ( ⁇ denotes the wavelength of the frequency to be attenuated, in particular a Hauptausschubfrequenz the compressor system or the vacuum pump in a preferred working range), and substantially parallel is arranged to the inlet cross-section, despite the superimposed gas flow advantageous for the damping effect of the branch high acoustic admittance of the branch.
  • 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 carried out so that a the 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 are formed for standing waves 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.
  • the branch in particular downstream of the branch further formed at least one bottleneck to be passed from the gas stream.
  • 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 silencer with the branching according to the invention may be formed in a substantially flat-cylindrical housing with two end faces and a lateral surface arranged therebetween, the inlet being provided on a first end face and the outlet on the jacket face. 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 muffler may further comprise an additional damper or an additional sound absorbing means in an optional embodiment downstream of the branch, which at least partially surrounds the branch, preferably forming an annular space.
  • the branch is thus followed by a Zuatzdämpfer, which is preferably housed in the same housing, so that a compact and functional unit is formed.
  • the additional silencer or the additional sound absorbing means may preferably be designed primarily as an absorption silencer.
  • the additional sound absorbing means surrounds the branch completely, preferably circular, more preferably substantially concentric.
  • the annular space has two opposite end-side ends, wherein the second end-side end comprises one or more openings for transferring the gas flow to the outlet. This arrangement ensures that the gas flow flows through the additional damper or the additional sound absorption medium over its entire length, so that particularly good soundproofing results are achieved.
  • the annulus may include a particular radial extension, so that it is possible to realize an absorption silencer with good damping properties.
  • the radial extension of the annular space is covered with a flow-permeable cover, which acts in particular as a flow resistance.
  • Preferred dimensions is the additional attenuator or the additional sound absorbing means tuned to a different frequency, preferably to a higher frequency than the components of the muffler upstream of the additional sound absorbing means, so that in combination can achieve a wideband effect as possible.
  • 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. Accordingly, a compressor or a vacuum pump, in particular a compressor operating according to the displacement principle or a vacuum pump operating on the displacement principle, such as a screw compressor or a screw vacuum pump, is claimed to be essential to the invention, the or a compression chamber and an outlet and a silencer connected to the outlet according to the invention.
  • the apparent peculiarity that the silencer exerts a strong effect on the sound-induced alternating flow in the outlet of the compressor or the vacuum pump itself can be explained as follows.
  • 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 the compressor or the vacuum pump can thus be positively influenced by a suitable muffler, i. be reduced in amplitude.
  • 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 flow in the inflow channel is to reduce the pulsations in the gas stream.
  • This counteracting by a reflection and / or resonance behavior can additionally be supported by dissipative measures, such as generating and utilizing dissipative damping processes in the "neck region" of the Helmholtz resonator (corresponding for example to the above-mentioned cover element, preferably in the form of a perforated plate).
  • dissipative measures such as generating and utilizing dissipative damping processes in the "neck region" of the Helmholtz resonator (corresponding for example to the above-mentioned cover element, preferably in the form of a perforated plate).
  • 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.
  • the gas flow downstream of the branch is still guided by an additional damper or by an additional sound absorption means which acts in particular as an absorption silencer.
  • 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.
  • an inventive 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 extension of the opening of the inlet 12 in the first end face 21 is an outlet 13 defining opening in the lateral surface 23 of the housing 20 is formed.
  • 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 is formed here by the already mentioned cup-shaped base body 24.
  • 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, here the lateral surface 23 and the first end surface 21, and the pot-shaped base body 24, which forms the housing 17 housed inside the housing 20 and in the present embodiment, the flat cylindrical housing 20 final second end face 22 in the form of an end plate 48 provided with ribs 49 at the same time.
  • a peripheral 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.
  • a 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 connection via a plurality of screws 37 which engage in internal threaded holes 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.
  • a cover member 19 is arranged with the a plurality of recesses 18 (see Fig. 3, 5 and 6) is provided.
  • 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, each matched to the flange 39 and the internally threaded holes 38 on the housing base 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 stream should be passed as tangentially or axially as possible to the chamber wall 41 in order to form no reflective planes for standing waves in subsequent pipes.
  • 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 by the Annular gap 53 defined constriction 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 of the compressor system.
  • FIG. 9 shows an alternative embodiment of a silencer according to the invention in a sectional view.
  • This embodiment is characterized in particular by the fact that downstream of the branch now an additional damper or an additional sound absorption means 55 is arranged, which acts primarily as an absorption silencer and still improves the sound damping properties of the overall arrangement.
  • the branch 17 comprising the cup-shaped base body 24 and provided with recesses 18 lid member 19 on this body to the explained with reference to Figures 1 to 8 embodiment designed so that the following explanation be limited to the formation of the additional sound absorbent 55 can.
  • the additional sound absorption means 55 has a cup-shaped base body 24 concentrically surrounded cylindrical annular space 52, which is widened in its central portion by a radially outwardly extending extension 56.
  • the gas stream flows via the already explained with reference to Figures 2 to 8 bottleneck 27 from the branch 17 forth in the annular space 52 at a first end face 58 and is now on the outside of the chamber wall 41 of the cup-shaped base body 24 over one or more openings, at a first front end 58 opposite the second front end 59 led to an outlet 13a.
  • the additional sound absorption means 55 thus has a first end face 58, which faces the constriction 27 or even the constriction 27 accommodates and opposite a second end face End 59, at which the gas flow is guided in the direction of the outlet 13 a on.
  • a flow-permeable cover 57 which acts as a flow resistance.
  • the flow-permeable cover 57 may for example consist of a fine-meshed wire mesh, of sintered material or of any other porous or perforated material.
  • the flow-permeable cover 57 and the radial extension 56 of the annular space 52 together form a so-called "perforated absorber" known per se, the acoustic properties of which - as known per se - include the wall thickness of the tube, its flow resistance (or its perforation). and pore size and hole and pore surface portion) and the radial extent of the extension 56 of the annular space 52 can be determined.
  • the extension 56 of the annular space 52 may additionally be filled with insulating materials, such as mineral wool or fibrous materials, for influencing the absorption properties.
  • the extension 56 of the annulus may be completely or partially filled with another suitable sound absorbing material (eg, sintered material, open cell metal foam, open celled ceramic, etc.), if it is a sufficiently dimensionally stable material acts - depending on the desired acoustic vote, the flow-permeable cover 57 also omitted or can be implemented in functional terms by the sound-absorbing filler itself.
  • An essential application advantage of the embodiment which does not use filling materials, in particular fibrous or open-pored materials in the enlargement 56 of the annular space, that is, in that the flow-permeable cover 57 covered space of the extension is empty, lies in the fact that it is not for the discharge of materials, in particular fibers or fragments may be due to disruption by pulsations.
  • outlet 13 in the optional provision of the additional sound absorbing means 55 described here can in principle also be provided as explained with reference to FIGS. 2 to 8, then only a part of the annular space 52 possibly provided with an extension 56 could act as an absorption damper or additional sound absorption means 55 , It is therefore considered expedient to provide a modified outlet 13a, as explained with reference to FIG. 9, which is arranged on or in relation to the inlet 12 behind the second end surface 22.
  • the (second) end face 22 according to the embodiment according to FIGS. 2 to 8 could be provided with openings in the region of the annular space 52 so that the gas flow can pass through the (second) end face 22 into the outlet 13a.
  • the (second) end surface 22 may be shortened in its radial extent, so that the gas stream can flow freely from the second front end 59 of the additional sound absorption means 55 into an outlet housing 60 forming the outlet 13a.
  • the outlet housing 60 is secured to the (second) end surface 22 of the cup-shaped base body 24 via bolts 61.
  • the muffler should have the lowest possible pressure loss. Therefore, the flow velocities must be limited, that is, certain flow cross sections are required.
  • the flow cross-section in the annular space 52 also has the extension 56, For example, in comparison with a tube same flow cross section, assuming the same length, a relatively large lateral surface, which is formed by the flow-permeable cover 57 of the additional sound absorbing means 55.
  • the channel damping of an absorption silencer is - in a first approximation - proportional to the quotient of absorbing occupied peripheral surface and free flow cross-section. Since the annular space 52, as shown above, has a relatively large circumferential area in relation to the flow cross section, good preconditions for the effectiveness of the additional sound absorption medium 55 are given.
  • 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 broadband sound attenuation mechanisms such as interference attenuation by reflection at successive cross sectional jumps (impedance discontinuities) or attenuation by dissipative silencers (e.g., absorption or throttling dampers), are sometimes associated with significant disadvantages for use in a compressor plant.
  • 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 absorbing media in the order of magnitude of ⁇ / 4, which leads to unacceptable layer thicknesses or construction volumes in the lower region of the above-mentioned frequency range.
  • the absorbent materials eg 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 specific 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 silencer allows a "rigid" construction, which leads to high natural frequencies and such eigenmodes, in which the bending wavelengths of the respective wall sections the outer contour is smaller than the wavelengths of the airborne sound at said natural frequencies, resulting in a low emission.
  • 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.
  • 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 before 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)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressor (AREA)
EP06005095.2A 2005-04-22 2006-03-13 Silencieux développé pour et destiné à un compresseur Expired - Lifetime EP1715189B1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
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
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
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

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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

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BE1018044A3 (nl) * 2008-03-12 2010-04-06 Atlas Copco Airpower Nv Intaatgeluidsdemper voor een compressorinstallatie en compressorinstallatie voorzien van zulke inlaatgeluidsdemper.
US9145040B2 (en) 2012-02-23 2015-09-29 Ford Global Technologies, Llc Heat exchanger for an air conditioning system
CN109074795A (zh) * 2016-05-04 2018-12-21 松特国际公司 用于管道或腔室的声音阻尼装置
US10180140B2 (en) 2016-09-30 2019-01-15 Ingersoll-Rand Company Pulsation damper for compressors
EP3042080B1 (fr) 2013-09-05 2019-05-08 Atlas Copco Airpower Dispositif compresseur
CN114837913A (zh) * 2021-02-02 2022-08-02 上海海立电器有限公司 消音装置及压缩机
EP3356677B1 (fr) * 2015-10-02 2024-01-24 Carrier Corporation Compresseur à vis avec groupes de résonateurs
DE102009056010B4 (de) * 2009-11-26 2024-02-01 HELLA GmbH & Co. KGaA Flügelzellenpumpe
WO2025107777A1 (fr) * 2023-11-23 2025-05-30 珠海格力电器股份有限公司 Structure de séparation d'huile de compresseur et compresseur à vis

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CN104265634B (zh) * 2014-09-19 2016-06-01 珠海格力电器股份有限公司 一种排气轴承座、螺杆压缩机及空调机组
WO2016201166A1 (fr) * 2015-06-11 2016-12-15 Eaton Corporation Résonateur intégré de compresseur volumétrique
US9644630B2 (en) * 2015-07-23 2017-05-09 Fca Us Llc Supercharger with integrated contraction chamber for noise attenuation
RU2723469C2 (ru) 2015-08-11 2020-06-11 Кэрриер Корпорейшн Компрессор, паровая компрессионная установка и способы их эксплуатации и сборки
EP3334937B1 (fr) 2015-08-11 2024-06-26 Carrier Corporation Plénum d'économiseur de compresseur à vis pour réduction de pulsations
BE1023523B1 (nl) * 2015-09-25 2017-04-19 Atlas Copco Airpower, N.V. Werkwijze voor het koelen van een compressor of vacuümpomp en een compressor of vacuümpomp die een dergelijke werkwijze toepast
WO2018091939A1 (fr) 2016-11-15 2018-05-24 Carrier Corporation Séparateur de lubrifiant avec silencieux
CN107288878B (zh) 2017-08-18 2020-04-10 珠海格力电器股份有限公司 消声器及压缩机
CN108105090B (zh) * 2017-12-25 2024-04-02 江阴爱尔姆真空设备有限公司 双斜面螺杆转子及其加工方法
WO2020072145A1 (fr) * 2018-10-02 2020-04-09 Carrier Corporation Résonateur à plusieurs étages pour compresseur
CN110080986B (zh) * 2019-06-10 2024-09-20 珠海凌达压缩机有限公司 泵体组件、压缩机和空调
DE102021134652B3 (de) * 2021-12-23 2023-05-11 Man Energy Solutions Se Schraubenkompressor
DE102022101009A1 (de) * 2022-01-17 2023-07-20 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Schalldämpfereinheit für ein Nutzfahrzeug

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Publication number Priority date Publication date Assignee Title
BE1018044A3 (nl) * 2008-03-12 2010-04-06 Atlas Copco Airpower Nv Intaatgeluidsdemper voor een compressorinstallatie en compressorinstallatie voorzien van zulke inlaatgeluidsdemper.
DE102009056010B4 (de) * 2009-11-26 2024-02-01 HELLA GmbH & Co. KGaA Flügelzellenpumpe
US9145040B2 (en) 2012-02-23 2015-09-29 Ford Global Technologies, Llc Heat exchanger for an air conditioning system
EP3042080B1 (fr) 2013-09-05 2019-05-08 Atlas Copco Airpower Dispositif compresseur
EP3042080B2 (fr) † 2013-09-05 2022-08-10 Atlas Copco Airpower, Naamloze Vennootschap Dispositif compresseur
EP3356677B1 (fr) * 2015-10-02 2024-01-24 Carrier Corporation Compresseur à vis avec groupes de résonateurs
CN109074795A (zh) * 2016-05-04 2018-12-21 松特国际公司 用于管道或腔室的声音阻尼装置
US10180140B2 (en) 2016-09-30 2019-01-15 Ingersoll-Rand Company Pulsation damper for compressors
CN114837913A (zh) * 2021-02-02 2022-08-02 上海海立电器有限公司 消音装置及压缩机
WO2025107777A1 (fr) * 2023-11-23 2025-05-30 珠海格力电器股份有限公司 Structure de séparation d'huile de compresseur et compresseur à vis

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JP2006300070A (ja) 2006-11-02
US20060239836A1 (en) 2006-10-26
US8142172B2 (en) 2012-03-27
JP4976046B2 (ja) 2012-07-18

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