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WO2012079141A1 - Silencieux acoustique de décharge pour un compresseur frigorifique - Google Patents

Silencieux acoustique de décharge pour un compresseur frigorifique Download PDF

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Publication number
WO2012079141A1
WO2012079141A1 PCT/BR2011/000476 BR2011000476W WO2012079141A1 WO 2012079141 A1 WO2012079141 A1 WO 2012079141A1 BR 2011000476 W BR2011000476 W BR 2011000476W WO 2012079141 A1 WO2012079141 A1 WO 2012079141A1
Authority
WO
WIPO (PCT)
Prior art keywords
chamber
discharge tube
muffler
acoustic
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.)
Ceased
Application number
PCT/BR2011/000476
Other languages
English (en)
Inventor
Claudio De Pellegrini
Daniel Henri Bedatty Hofmann
Edson Correa Miguel
Paulo Henrique Mareze
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.)
Whirlpool SA
Universidade Federal de Santa Catarina
Original Assignee
Whirlpool SA
Universidade Federal de Santa Catarina
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 Whirlpool SA, Universidade Federal de Santa Catarina filed Critical Whirlpool SA
Publication of WO2012079141A1 publication Critical patent/WO2012079141A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0027—Pulsation and noise damping means
    • F04B39/0055—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes
    • F04B39/0061—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes using muffler volumes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0027—Pulsation and noise damping means
    • F04B39/0055—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0027—Pulsation and noise damping means
    • F04B39/0055—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes
    • F04B39/0066—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes using sidebranch resonators, e.g. Helmholtz resonators

Definitions

  • the present invention refers to an acoustic muffler for attenuating the pulsation generated by the pressure transients in the gas discharge of a refrigeration compressor, for example of the reciprocating type.
  • Reciprocating compressors used in refrigeration systems are generally provided with pulsation attenuators or acoustic mufflers positioned in the gas discharge.
  • Said acoustic mufflers have the purpose of attenuating the pulsation resulting from the pressure transients generated by the process of compression and discharge of the gas to an associated refrigeration system.
  • These acoustic mufflers also allow reducing the noise irradiated, by the compressor, to the external ambient.
  • the pulsation of the gas being compressed and pumped by the compressor generates an excitation in the compressor shell and in the ducts and components of the refrigeration system to which the compressor is coupled, resulting in high noise levels of the compressor, and also of the assembly formed by the compressor and by the refrigeration system.
  • the attenuation of the pulsations in the gas discharge of a compressor is generally carried out: by restricting the refrigerant fluid flow being pumped, by reducing the diameter of the flow conduct, obtaining pulsation attenuation by restricting the path of the acoustic energy; or by providing one or more expansion volumes disposed in series with the discharge tube, making the discontinuity of the acoustic impedance to reflect pulsation acoustic waves existing in said tube, thereby attenuating the pulsation transmitted.
  • said discharge acoustic muffler comprising two chambers in series with substantially equal volumes, provides positive results in terms of pulsation attenuation, with acceptable levels of load loss, it is not efficient enough to attenuate medium and high frequencies, for example, in frequencies above about 2kHz.
  • the high pulsation levels, in frequencies above 2kHz are not adequately attenuated.
  • the impedance difference produced in both chambers is not sufficient to reflect a substantial part of the pulsation energy, allowing a greater portion of the latter to be transmitted to the elements of the compressor and refrigeration system.
  • the present invention has the object of providing an acoustic muffler, to be mounted to the gas discharge of a refrigeration compressor and which presents a compact and small-size construction, and which is capable of attenuating the noises generated by the pulsations in the gas discharge, in medium and high frequencies, generally above 2kHz, without producing load losses sufficient to impair, in a relevant manner, the energy efficiency of the compressor.
  • a discharge acoustic muffler for a refrigeration compressor of the type provided with a gas outlet which is connected to a refrigeration system by a discharge tube said acoustic muffler being mounted, in series, to the discharge tube and comprising a tubular body, with closed ends, which is internally and transversally divided by a dividing wall: in a first chamber, to the interior of which an outlet end of a first discharge tube portion is open, an inlet end of said discharge tube being connected to the gas outlet of the compressor; and in a second chamber, which is maintained in fluid communication with the first chamber, through a passage in the dividing wall, and to the interior of said second chamber being open an inlet end of a second discharge tube portion, an outlet end of the latter being connected to the refrigeration system.
  • the second chamber has a volume which represents only a fraction of the volume of the first chamber, said fraction being capable of producing, through the passage of the dividing wall, impedance differences which are sufficient to reflect at least part of the pulsation energy to be attenuated, in the frequencies produced by the compressor operation.
  • the volume of the second chamber is 9% to 10% of the volume of the first chamber, the attenuation of the pulsation energy being obtained in compressor operating frequencies lying above about 2kHz.
  • Figure 1 is a perspective view of the present acoustic muffler when mounted, in series, to the discharge tube of a compressor;
  • Figure 2 is a longitudinal sectional view of the acoustic muffler illustrated in figure 1, with the second discharge tube portion, which is defined downstream of the acoustic muffler, being only partially illustrated;
  • Figure 3 is a graph illustrating the pulsation attenuation curves, in frequencies above 2kHz, related to a prior art acoustic muffler and to the acoustic muffler of the present invention;
  • Figure 4 is a graph illustrating the curves representing the imaginary part and the real part of the impedance calculated in the connection region between the two chambers of the acoustic muffler
  • Figure 5 is a graph illustrating the different pulsation levels measured in the compressor discharge, in different frequencies, considering a prior art discharge and a discharge using the acoustic muffler of the present invention.
  • Figure 6 is a graph illustrating the different noise levels measured in the compressor discharge, in different frequencies, considering a prior art discharge and a discharge using the acoustic muffler of the present invention.
  • the present invention refers to an acoustic muffler F to be applied to a refrigeration compressor (not illustrated) , for example of the reciprocating type and which is provided with a gas outlet 1 connected to a refrigeration system 2 by a discharge tube 10 which presents a first discharge tube portion 11, having an inlet end 11a connected to the gas outlet 1 of the compressor, and an outlet end lib connected to the acoustic muffler F.
  • the discharge tube 10 further comprises a second discharge tube portion 12, having an inlet end 12a connected to the acoustic muffler F, and an outlet end 12b connected to the refrigeration system 2, in a well known prior art arrangement.
  • the first discharge tube portion 11 and the second discharge tube portion 12 are formed in any adequate material as, for example, steel or copper metal alloys. Although not illustrated in the drawings, it should be understood that the outlet end 12b of the second discharge tube portion 12 can be connected to the refrigeration system 2 by means of different tubular connecting elements, well known from the prior art such as, for example, a discharge outlet tube disposed through a wall of the shell of a refrigeration compressor of the hermetic type.
  • the acoustic muffler F object of the present invention, comprises a tubular body 20, constructed in any adequate material as, for example, metal sheet or injected plastic, being closed by end walls 21, 22 and internally and transversally divided, by a dividing wall 23, in a first chamber CI and in a second chamber C2, preferably with a cylindrical shape and coaxial to each other, which are maintained in fluid communication with each other, through a passage 23a, medianly provided in the dividing wall 23.
  • the passage 23a presents the form of a through hole, preferably circular and disposed in the center of the dividing wall 23.
  • passage 23a of the dividing wall 23 is illustrated in the form of a through hole, it can take the form of a tubular extension (not illustrated) , passing through the dividing wall 23 and axially projecting to the interior of the first chamber CI and of the second chamber C2. Nevertheless, it was observed that the use of a passage 23a in the form of a tubular extension tends to limit the versatility of the acoustic muffler F in attenuating pulsations of the discharge gas, in compressor operating frequencies above 2kHz.
  • the fixation of the dividing wall 23 in the interior of the tubular body 20 can be effected by different manners, with the desired axial positioning, defined by project, being guaranteed by an inner circumferential step formed by the difference between the inner contours of the first chamber CI and of the second chamber C2, or by an alignment of inner radial projections spaced from each other and which can be obtained by deforming the material with which the tubular body 20 is formed.
  • the fixation of the dividing wall 23 in the interior of the tubular body 20 can be obtained, for example, by welding or gluing.
  • At least one of the end walls 21, 22 can be formed in a piece separated from the tubular body 20 and affixed to the latter by gluing, welding or any other adequate means .
  • the second chamber C2 is dimensioned to have a volume which represents only a fraction of the volume of the first chamber CI, which fraction is capable of producing, through the passage 23a of the dividing wall 23, impedance differences sufficient to reflect at least part of the pulsation energy to be attenuated, in the frequencies produced by the compressor operation, avoiding said part of the pulsation energy from being transmitted to the elements of the compressor and of the refrigeration system 2.
  • the volume of the second chamber C2 is 9% to 10% of the volume of the first chamber CI, so as to obtain the desired impedance difference in frequencies above 2kHz and the consequent pulsation attenuation in this frequency band.
  • Figure 3 of the drawings illustrates a graph of the attenuations obtained by the present acoustic muffler, in frequencies above 2kHz, upon a unitary excitation in the inlet of the discharge system and with the pressure being measured in the outlet of said system for each frequency step.
  • the curves in the graph which are representative of the measurements in a conventional discharge acoustic muffler and in a discharge acoustic muffler according to the present invention, show the expected yield of the proposed muffler.
  • the specific dimensioning of the volume of the first chamber CI and of the second chamber C2 is carried out as a function of the particularities of the compressor project and of the attenuation effect to be obtained.
  • the variations of the volume ratio between the two chambers CI and C2 generate impedance differences in the communication region therebetween defined by the passage 23a of the dividing wall 23.
  • the impedance differences generated in the region of the passage 23a are capable of blocking a substantial part of the pulsation energy, reducing the part of said energy which, otherwise, would be transmitted to the compressor and to the refrigeration system.
  • Figure 4 illustrates the effect mentioned above, representing the imaginary part and the real part of the impedance calculated in the region of the passage 23a which makes the connection between the first chamber CI and the second chamber C2. It should be noted that the imaginary part increases considerably from 2kHz.
  • the acoustic muffler F of the present invention has the outlet end lib of the first discharge tube portion 11 axially projecting to the interior of the first chamber CI, through the adjacent end wall 21 of the tubular body 20.
  • the extension of the first discharge tube portion 11, which projects to the interior of the first chamber CI, is aligned with the passage 23a and has the outlet end lib positioned in a region of the first chamber CI, in which the acoustic nodes are found, that is, the locations with low acoustic pressure level, for the frequency bands considered of interest in the compressor project.
  • the main acoustic modes of the first chamber CI are located at the region in which the outlet end lib is provided.
  • the excitation coming from the compressor is not amplified by the acoustic mode of the first chamber CI, guaranteeing a low energy level transmitted to the following chamber, that is, to the second chamber C2.
  • the acoustic modes of the second chamber C2 are in extremely high frequencies, above 7000Hz, in which there is little pulsation energy;
  • All the acoustic modes of the second chamber C2 have their acoustic nodes in the center thereof, which is the region where the passage 23a and also the inlet end 12a of the second discharge tube portion 12 are located.
  • the excitations are not amplified by the acoustic modes present in the second chamber C2.
  • the difference between the volumes of the first and of the second chamber CI, C2 and the dimensioning of the cross-section of the passage 23a, in the dividing wall 23, allow selecting the frequencies to be attenuated by the present acoustic muffler.
  • the acoustic muffler F of the present invention further presents the inlet end 12a of the second discharge tube portion 12 axially projecting to the interior of the second chamber C2, through the adjacent end wall 22 of the tubular body 20.
  • the extension of the second discharge tube portion 12, which projects to the interior of the second chamber C2 is axially aligned with the passage 23a and has its inlet end 12a positioned in a region of the second chamber C2, in which are found the acoustic nodes, that is, the locations of low acoustic pressure level, for the frequency bands considered of interest in the compressor project, by the same reasons regarding the gain of load loss and noise attenuation described above in relation to the extension of the first discharge tube portion 11 in the interior of the first chamber CI.
  • the two chambers CI, C2 are cylindrical and formed from the same tube, which facilitates their production and allow that the excitations and the effects produced thereby in the interior of the second chamber C2 occur in their regions in which the nodes of the acoustic mode occur, with the already previously commented advantages mentioned above.
  • the determination of the volume of each of the chambers CI, C2, of the dimensions of the extensions of the first and second discharge tube portions 11, 12, which axially project to the interior of the first and second chambers CI, C2, and also of the cross section of the discharge tube portions 11, 12 and of the passage 23a, is carried out as a function of the attenuation effect to be obtained and of the pulsation band to be attenuated in each compressor project.
  • Figure 5 illustrates a comparative graph of the pulsation levels measured at the outlet of the discharge system of a compressor of the type considered herein, with and without the acoustic muffler F of the present invention.
  • Figure 6 of the enclosed drawings illustrates a comparative graph of the noise levels generated by the same compressor, with and without the acoustic muffler F of the present invention.
  • the provision of a second chamber C2, with a much lower volume than that of the first chamber CI, allows the acoustic muffler F of the present invention to present a higher efficiency in terms of noise attenuation, without the occurrence of pulsation amplifications due to the resonances of the second chamber C2.
  • the acoustic muffler of the present invention leads to a considerable gain in noise attenuation in a wide frequency spectrum, particularly frequencies above 2kHz, which is not reached by the known acoustic mufflers.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)

Abstract

L'invention concerne un silencieux acoustique (F) monté sur un tube de décharge (10) d'un compresseur et comportant un corps tubulaire (20) qui est divisé à l'intérieur par une paroi de séparation (23) : en une première chambre (C1) connectée, par une première partie (11) du tube de décharge, à une sortie de gaz (1) du compresseur ; et en une seconde chambre (C2) maintenue en communication fluidique avec la première chambre (C1) au travers d'un passage (23a) dans la paroi de séparation (23) et connectée, par une seconde partie (12) du tube de décharge, à un système de réfrigération (2). La seconde chambre (C2) a un volume qui ne représente qu'une fraction du volume de la première chambre (C1), de manière à produire, au travers du passage (23a), des différences d'impédance en mesure de réfléchir au moins une partie de l'énergie de pulsation devant être atténuée dans les fréquences d'exploitation du compresseur.
PCT/BR2011/000476 2010-12-15 2011-12-15 Silencieux acoustique de décharge pour un compresseur frigorifique Ceased WO2012079141A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
BRPI1005459-6 2010-12-15
BRPI1005459 BRPI1005459A2 (pt) 2010-12-15 2010-12-15 filtro acéstico de descarga para um compressor de refrigeraÇço

Publications (1)

Publication Number Publication Date
WO2012079141A1 true WO2012079141A1 (fr) 2012-06-21

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Application Number Title Priority Date Filing Date
PCT/BR2011/000476 Ceased WO2012079141A1 (fr) 2010-12-15 2011-12-15 Silencieux acoustique de décharge pour un compresseur frigorifique

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BR (1) BRPI1005459A2 (fr)
WO (1) WO2012079141A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105201780A (zh) * 2014-06-05 2015-12-30 泰州乐金电子冷机有限公司 冰箱用手握式吸气管
CN108343590A (zh) * 2018-01-26 2018-07-31 广州万宝集团压缩机有限公司 一种压缩机排气消音器结构
CN109441777A (zh) * 2018-12-11 2019-03-08 珠海格力节能环保制冷技术研究中心有限公司 气缸座结构及具有其的压缩机

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3750840A (en) * 1968-10-08 1973-08-07 Danfoss As Sound absorber for compressors
US4111278A (en) 1977-02-09 1978-09-05 Copeland Corporation Discharge muffler
US5196654A (en) 1991-03-19 1993-03-23 Bristol Compressors Compressor discharge muffler construction
US20090022605A1 (en) * 2007-07-16 2009-01-22 Jung Hyoun Kim Hermetic compressor

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3750840A (en) * 1968-10-08 1973-08-07 Danfoss As Sound absorber for compressors
US4111278A (en) 1977-02-09 1978-09-05 Copeland Corporation Discharge muffler
US5196654A (en) 1991-03-19 1993-03-23 Bristol Compressors Compressor discharge muffler construction
US20090022605A1 (en) * 2007-07-16 2009-01-22 Jung Hyoun Kim Hermetic compressor

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105201780A (zh) * 2014-06-05 2015-12-30 泰州乐金电子冷机有限公司 冰箱用手握式吸气管
CN108343590A (zh) * 2018-01-26 2018-07-31 广州万宝集团压缩机有限公司 一种压缩机排气消音器结构
CN108343590B (zh) * 2018-01-26 2020-06-16 广州万宝集团压缩机有限公司 一种压缩机排气消音器结构
CN109441777A (zh) * 2018-12-11 2019-03-08 珠海格力节能环保制冷技术研究中心有限公司 气缸座结构及具有其的压缩机

Also Published As

Publication number Publication date
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