EP0050337A1 - Dispositif d'amortissement des bruits pour installation à air comprimé - Google Patents

Dispositif d'amortissement des bruits pour installation à air comprimé Download PDF

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Publication number
EP0050337A1
EP0050337A1 EP81108445A EP81108445A EP0050337A1 EP 0050337 A1 EP0050337 A1 EP 0050337A1 EP 81108445 A EP81108445 A EP 81108445A EP 81108445 A EP81108445 A EP 81108445A EP 0050337 A1 EP0050337 A1 EP 0050337A1
Authority
EP
European Patent Office
Prior art keywords
support
hollow support
hollow
blower
drive motor
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Withdrawn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
EP81108445A
Other languages
German (de)
English (en)
Inventor
Werner Flatt
René Hostettler
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.)
Buehler AG
Original Assignee
Buehler AG
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 DE19803039334 external-priority patent/DE3039334C2/de
Application filed by Buehler AG filed Critical Buehler AG
Publication of EP0050337A1 publication Critical patent/EP0050337A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N13/00—Exhaust or silencing apparatus characterised by constructional features ; Exhaust or silencing apparatus, or parts thereof, having pertinent characteristics not provided for in, or of interest apart from, groups F01N1/00 - F01N5/00, F01N9/00, F01N11/00
    • F01N13/002—Apparatus adapted for particular uses, e.g. for portable devices driven by machines or engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N1/00—Silencing apparatus characterised by method of silencing
    • F01N1/08—Silencing apparatus characterised by method of silencing by reducing exhaust energy by throttling or whirling
    • F01N1/10—Silencing apparatus characterised by method of silencing by reducing exhaust energy by throttling or whirling in combination with sound-absorbing materials
    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • 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
    • F04C29/065—Noise dampening volumes, e.g. muffler chambers
    • F04C29/066—Noise dampening volumes, e.g. muffler chambers with means to enclose the source of noise

Definitions

  • the invention relates to an air generator device with a blower, a drive motor and a muffler unit which has at least one pressure muffler and connects the blower and motor to form a structural unit.
  • Such compressed air generator units have long been known as compact unit units, with rotary piston blowers preferably being used.
  • the relatively large structural outlay for the production of such devices soon led to the search for structural improvements in the sense of simplification.
  • the results of these developments have still not been satisfactory in terms of optimizing the three main factors for such compressed air generators, which are the manufacturing costs, the service life and the noise reduction.
  • This is very much on layered problem with such compressed air generators: for example, the noise generated is made up of many individual sources, such as the blown fan noise, the noise of the drive motor, the noise from the muffler, and also the intake noise of the air, etc.
  • Another problem lies in the various vibration generators such a unit, whereby the three aforementioned aggregates are to be mentioned as the main causes.
  • the invention is now based on the development of a new compressed air generator unit, in which there is a noticeable improvement over previously known solutions, particularly with regard to the three essential influencing factors, namely service life, noise generation and production expenditure.
  • the muffler is designed as a hollow support with a round, that is to say rounded on all sides, cross-sectional shape.
  • the air generator device according to the invention brought a significant improvement over previously known devices with regard to the three main criteria shown.
  • the hollow support is preferably designed with an oval or elliptical cross section, such cross-sectional shapes being recommended for achieving particularly good results.
  • the production of such rounded cross-sectional shapes is, compared to the production of other, such as angular shapes, easily possible on modern production machines without additional effort.
  • the cross-sectional shapes proposed by the invention can be produced very precisely in one pass on computer-controlled rollers. Since the silencer itself is designed as the connecting element of the compressed air generator unit, connecting support plates (such as special supports for the engine and blower) can be omitted. Thus, in contrast to the use of a silencer with a rectangular cross-sectional shape known in the prior art, which is arranged as an intermediate link between a drive motor and a blower on a separate support structure, the actual support function is completely taken over by the silencer in the invention.
  • the main flow of the mechanical forces can also be passed through the carrier, so that the weight and the constantly changing tensile forces between the motor and the blower (for example those of the corresponding belt pull) and the forces triggered by vibrations are well absorbed.
  • the cross-sectional shape rounded according to the invention offers surprisingly great advantages since it is only relatively short in a muffler and only acts as a "bridge girder" in a partial function.
  • the force component resulting from the weights of the unit is available as a purely static, i.e. constant force, which is easily manageable even with the heaviest units (motor or blower or both).
  • the device according to the invention has proven to be particularly expedient with regard to the design of an entire series of air generators with various fans and motors, which can be pushed into their most favorable positions.
  • the silencer was sometimes assigned a certain carrying function, but in no case was the silencer designed as the actually load-bearing element for the structural unit. This led e.g. to the fact that a thick support plate was assigned to the silencer and welded, to which the motor and the fan were then attached. The forces then had to be diverted more or less directly from the support plate to the floor via a further support structure, so that ultimately the muffler participated only to a lesser extent in the play of forces of two essential forces (drive, vibrations) for receiving or
  • the hollow beam as seen in the direction of air flow, can advantageously be divided into a first resonance chamber, a downstream absorption chamber and a second resonance chamber, which is in turn connected downstream.
  • the two resonance chambers are advantageously delimited radially outwards by the inner wall of the hollow support or at least have a free cross-sectional area corresponding to the internal dimensions of the hollow support.
  • the absorption chamber is preferably formed by an insertion unit in an inner perforated support tube, between which and the inner wall of the hollow support an intermediate layer, which preferably has a thickness of 3 to 15 cm, made of sound-absorbing material is applied.
  • the support tube is also designed with the same or a similar cross-sectional shape as the hollow support, which, however, is made smaller by the thickness of the intermediate layer than the cross-sectional shape of the hollow support.
  • the invention is shown here as a particularly simple apparatus, in addition to a "simple" hollow support only one form g leiches, punched and wrapped with insulation material mesh tube and otherwise has "nothing".
  • the sound-absorbing material consists of non-combustible, fiber-like material which is inserted into the hollow support in such a way that the fibers predominantly come to lie radially to the support tube. Due to this position of the individual fibers, essentially perpendicular to the surfaces of the support tube, they offer a maxi paint resistance to compression, whereby a particularly good absorption capacity of the occurring considerable pressure forces, pressure surges etc. can be achieved, which in known silencers (in which the insulation material with fibers was usually installed lengthways to the main surfaces of the silencer) in a short period of time Pressing the insulation material together and thereby significantly worsened the sound insulation effect over long periods.
  • the length of the absorption chamber is greater than that of a resonance chamber and preferably at least half as long as that of the hollow beam.
  • a pressure safety valve is assigned directly to the second resonance chamber, with, again preferably, a non-return valve also being assigned directly to the outlet of this resonance chamber.
  • the fan and one end side of the hollow support have a common support arrangement or foot construction, which in turn can preferably be firmly connected to the floor.
  • the hollow support again preferably, can be connected to the foot construction in a hanging manner via the outlet-side connector of the housing.
  • the other end side of the hollow support can be supported or suspended via a second foot construction, the drive motor preferably being placed or ver directly on the hollow support between the two foot constructions is screwed.
  • the drive motor has tensioning means which are fastened directly to the hollow beam, these preferably being subjected to tension.
  • an intake silencer is placed directly on the blower, which in the end is thereby also designed as an integrating element of the overall unit.
  • the intake silencer is combined with an air filter, the air being sucked in, preferably again in a circular manner, from below, directly over the outside of the blower.
  • air filter for most applications, it has proven particularly expedient if the intake silencer is combined with an air filter, the air being sucked in, preferably again in a circular manner, from below, directly over the outside of the blower.
  • Particularly good results can be achieved by sucking in the air in a ring from below, since this causes the noise to spread evenly in all directions and is therefore perceived as less disturbing.
  • the measures according to the invention complement one another with a view to improving the entire air generator unit.
  • the solution according to the invention not only leads to a certain cooling of the blower, but also eliminates part of the otherwise emitted noise, since an acoustic signal propagates more heavily than with the air flow direction.
  • the compressed air generator unit shown in the figures has a pressure silencer 1, a blower 2, an intake silencer 3, a drive motor 4 and a pressure safety valve 5 and a check valve 6.
  • the muffler 1 is formed by a first resonance chamber 7, an absorption chamber 8 and a second resonance chamber 9, as can best be seen in FIG. 2.
  • the resonance chambers 7 and 9 are delimited radially in the circumferential direction directly by a hollow support 10 which has an oval shape, as is e.g. 3 can be seen.
  • the resonance chamber 7 is delimited by a cleaning closure 11, while on its other side it is connected directly to the absorption chamber 8 via a corresponding free cross section 12.
  • a support tube 13 is arranged concentrically.
  • This consists of perforated sheet 14 or a suitably rigid screen jacket. Between the perforated sheet 14 and the hollow support 10, a layer of sound-absorbing material 15 is attached.
  • a pressure safety valve 5 is arranged directly on the second resonance chamber 9. This also brings structural advantages with regard to the standardization of all individual components, whereby the fluidic design as well as that of the silencer can be improved.
  • FIG. 5 shows a sectional view of the pressure safety valve 5: this consists of a support body 20 which is screwed tightly onto a connecting flange 21, also of a support rod 22, a valve cover 23 and a compression spring 24.
  • the support rod 22 is on one end side firmly screwed into the support body 20 via nuts 25 and 26 and held in position, the guidance being ensured by two disks 27 and 28 and by a spacer sleeve 29.
  • an adjusting nut 30 and a safety nut 31 are attached, which serve to preload the compression spring 24.
  • This compression spring 24 is clamped between two spring plates 32 and 33 so that it leads to a tension between the valve cover 23 on the one hand and the support body 20 on the other hand via the support rod 22, which is also used for guiding their movement, which is screwed to the spring plate 32.
  • the valve cover 23 opens after it has been reached, thus securing the pressure muffler, but also the drive motor 4 as the blower 2 from overload.
  • the one support of the compressed air generator unit is shown.
  • Two side supports 34, 34 'are attached to the muffler by screws 35 in their upper region.
  • the two supports 34, 34 'are also connected in the lower region via one or more tie rods 36, as a result of which a firm clamping of the hollow beam 10 can be achieved overall.
  • the supports 34, 34 'are further supported on the floor by means of rubber elements 38, and, depending on the particular installation situation, the supports can additionally be attached directly to the floor by means of screws 34.
  • a tensioning rail 39 is fastened on a slide rail 40 welded longitudinally to the hollow beam 10.
  • the latter gives the drive motor 4 sufficient guidance so that it can be moved by longitudinal movement to precisely adjust the belt tension.
  • the actual holder for the drive motor 4 consists of two clamping brackets 41, which comprise the hollow support 10 (see FIG. 4) and produce a non-positive connection between the drive motor 4 and the hollow support 10 via two nuts 42, 42 '.
  • an additional longitudinally grooved Jordan rail 43 is expediently arranged between the drive motor 4 and the tensioning rail 39.
  • the fastening device can be adapted to any size of the drive motor 4 and also its respective position with respect to the hollow support 10.
  • the overdrive from the drive motor 4 to the blower 2 usually takes place via pulleys 44 and 45 and via a drive belt 46 (FIG. 1). If the blower 2, drive motor 4 and belt 46 are installed, is the zwisehen a clamping rail 39 and the corresponding support 34 and the desired belt tension are bolted 34 'on both sides attached to tie bars 47 applied, then secured by respective nuts 48, after which the clamping bars are drawn 41 through the nuts 42 fixed .
  • the air flow through the intake silencer 3 is shown, the intake silencer 3 shown having a circular cross section and being closed laterally and above by a correspondingly shaped plate 49.
  • the air first enters via a circular filter 50 into a first damping section 51 directed from the bottom upwards, which is delimited radially outwards and inwards by a perforated plate 52 and 53, respectively.
  • This first damping section 51 is deflected at its upper end by 180 ° in the direction of the center of the muffler 3 and merges in its central region into a second, central, downward damping section 54, which passes directly into the blower intake side via an intake port 55 flows into.
  • This second damping section 54 is also delimited radially on the outside by a perforated plate 56, the height of which, however, protrudes above the sound-insulating material 57 interposed between it and the plate 53 and up to the insulating material 58 which is fastened or held directly on the outer end plate 49 comes to rest (to the representation of Fig. 3 is expressly referred here).
  • the air In order to be able to enter the second damping path 54 from the first damping path 51 after its diversion, the air must therefore pass through free openings in the upper region of the perforated plate 56.
  • FIG. 3 is designed similarly to that with the supports 34 from FIG. 5.
  • the hollow beam 10 is screwed to the corresponding connection points.
  • Fig. 4 shows a section through the compressed air generator unit in the area of the drive motor 4, but at the same time also in the area of the absorption chamber 8.
  • the free passage cross section through the absorption chamber 8 has an elliptical shape 66 in the illustrated embodiment, in which a ratio of large to small Semiaxis corresponding to approx 1.5: 1 is selected.
  • the free average shape and in particular the effective cross-sectional dimensions can be chosen almost without any significant loss of interference.
  • a passage cross section corresponding to the ellipse 67 shown in dashed lines in FIG. 4 or the two circular shapes 68 also shown in dashed lines could be selected. It has been shown that three decisive dimensions are important for the selection here, namely the absolute length of the absorption chamber 8, the smallest transverse dimension of the free passage and the thickness of the noise-insulating material.
  • the layer thickness of the absorption material is selected sufficiently, particularly in the area of the smallest transverse dimension.
  • a shape corresponding to the ellipse 67 can be used with maximum use of the insulation material (at Cut out from a block) or for minimal consumption of the insulation material (easy application over the entire circumference), in which case the sections that are not required can be used for the suction damper.
  • an elliptical tube behaves similarly to a circular tube.
  • elliptical shape used above is not intended to mean that a mathematically exact, "pure” elliptical shape is required here: an ellipse-like shape which is conventionally referred to as “oval” can also be used with equal advantage.
  • the hollow support 10 has a substantially circular shape, but the absorption chamber 8 has some (rounded) shape (oval, elliptical, etc., as shown in Fig. 4 with some examples).
  • Rotary piston blowers are advantageously used for such compressed air generator units because of the typical scooping characteristic of the rotary piston blower, which results in the scooping of a volume unit with each revolution of the rotary piston.
  • the scooping frequency is therefore directly proportional to the speed of the fan, the noise behavior resulting from this frequency as well as from the characteristic transfer of the scooped volume, which does not happen suddenly, as with piston pumps, by gradually opening the passage.
  • the screw compressors which are occasionally used instead of rotary lobe blowers, also have a similar noise behavior.
  • the sound-absorbing material in a tube with a rectangular (Fig. 7,9) or. with an oval (FIG. 8) cross section is packed on perforated material 15 (for example sheet metal) and thus the absorption chamber 8 is located between the support profile and the hollow support inner wall.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP81108445A 1980-10-17 1981-10-16 Dispositif d'amortissement des bruits pour installation à air comprimé Withdrawn EP0050337A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE19803039334 DE3039334C2 (de) 1980-10-17 1980-10-17 Drucklufterzeugervorrichtung
DE3039334 1980-10-17
CH7837/80 1980-10-21
CH783780 1980-10-21

Publications (1)

Publication Number Publication Date
EP0050337A1 true EP0050337A1 (fr) 1982-04-28

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ID=25702321

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Application Number Title Priority Date Filing Date
EP81108445A Withdrawn EP0050337A1 (fr) 1980-10-17 1981-10-16 Dispositif d'amortissement des bruits pour installation à air comprimé

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EP (1) EP0050337A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2161217A (en) * 1984-07-03 1986-01-08 Radmark Engineering Systems Li Air blowing unit
EP0542178A1 (fr) * 1991-11-09 1993-05-19 Peter Wilms Suppression du bruit de l'air aspiré par un compresseur
GB2268232A (en) * 1992-06-22 1994-01-05 Hick Hargreaves & Co Ltd Air blower mounted on chassis with silencer
FR2727724A1 (fr) * 1994-12-01 1996-06-07 Rivard Ets Installation de pompage de produits tels que des boues ou analogues
DE19920279A1 (de) * 1999-05-04 2000-11-30 Sachsenring Maschb Gmbh Drehkolbengebläseanlage
CN102913449A (zh) * 2012-08-04 2013-02-06 百事德机械（江苏）有限公司 鼓风机的新型安装结构

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE599977C (de) * 1933-08-04 1934-07-12 Josef Ernst Schalldaempfer, insbesondere fuer Brennkraftmaschinen, mit eingebauten schalldaempfenden Elementen
US3142354A (en) * 1960-08-09 1964-07-28 Gutehoffnungshuette Sterkrade Sound absorption device and method of manufacture
US3642095A (en) * 1968-03-22 1972-02-15 Fujii Koygo Kk Muffler
US3709321A (en) * 1971-08-19 1973-01-09 Tenneco Inc Muffler with longitudinal chamber
US3718208A (en) * 1971-07-15 1973-02-27 S Gibel Expansion chambered, pressure relief muffler
DE2653732A1 (de) * 1976-11-26 1978-06-01 Kloeckner Humboldt Deutz Ag Abgasschalldaempfer fuer brennkraftmaschinen
GB2020748A (en) * 1978-05-16 1979-11-21 Klein R Gas compressors
US4211303A (en) * 1976-02-03 1980-07-08 Recourt Martyn Elizabeth De Sound absorbing device
DE2946659A1 (de) * 1979-11-19 1981-05-27 Aerzener Maschinenfabrik Gmbh, 3251 Aerzen Grundtraeger fuer einen kompressor mit antriebsmotor

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE599977C (de) * 1933-08-04 1934-07-12 Josef Ernst Schalldaempfer, insbesondere fuer Brennkraftmaschinen, mit eingebauten schalldaempfenden Elementen
US3142354A (en) * 1960-08-09 1964-07-28 Gutehoffnungshuette Sterkrade Sound absorption device and method of manufacture
US3642095A (en) * 1968-03-22 1972-02-15 Fujii Koygo Kk Muffler
US3718208A (en) * 1971-07-15 1973-02-27 S Gibel Expansion chambered, pressure relief muffler
US3709321A (en) * 1971-08-19 1973-01-09 Tenneco Inc Muffler with longitudinal chamber
US4211303A (en) * 1976-02-03 1980-07-08 Recourt Martyn Elizabeth De Sound absorbing device
DE2653732A1 (de) * 1976-11-26 1978-06-01 Kloeckner Humboldt Deutz Ag Abgasschalldaempfer fuer brennkraftmaschinen
GB2020748A (en) * 1978-05-16 1979-11-21 Klein R Gas compressors
DE2946659A1 (de) * 1979-11-19 1981-05-27 Aerzener Maschinenfabrik Gmbh, 3251 Aerzen Grundtraeger fuer einen kompressor mit antriebsmotor

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2161217A (en) * 1984-07-03 1986-01-08 Radmark Engineering Systems Li Air blowing unit
EP0542178A1 (fr) * 1991-11-09 1993-05-19 Peter Wilms Suppression du bruit de l'air aspiré par un compresseur
GB2268232A (en) * 1992-06-22 1994-01-05 Hick Hargreaves & Co Ltd Air blower mounted on chassis with silencer
FR2727724A1 (fr) * 1994-12-01 1996-06-07 Rivard Ets Installation de pompage de produits tels que des boues ou analogues
DE19920279A1 (de) * 1999-05-04 2000-11-30 Sachsenring Maschb Gmbh Drehkolbengebläseanlage
DE19920279C2 (de) * 1999-05-04 2001-05-31 Sachsenring Maschb Gmbh Drehkolbengebläseanlage
CN102913449A (zh) * 2012-08-04 2013-02-06 百事德机械（江苏）有限公司 鼓风机的新型安装结构

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Inventor name: HOSTETTLER, RENE

Inventor name: FLATT, WERNER