EP0890026B1 - Ansauggeräuschdämpfersystem für motorkühlverdichter - Google Patents

Ansauggeräuschdämpfersystem für motorkühlverdichter Download PDF

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Publication number
EP0890026B1
EP0890026B1 EP97916494A EP97916494A EP0890026B1 EP 0890026 B1 EP0890026 B1 EP 0890026B1 EP 97916494 A EP97916494 A EP 97916494A EP 97916494 A EP97916494 A EP 97916494A EP 0890026 B1 EP0890026 B1 EP 0890026B1
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EP
European Patent Office
Prior art keywords
chamber
silencer system
silencer
compressor
ratio
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.)
Expired - Lifetime
Application number
EP97916494A
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English (en)
French (fr)
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EP0890026A1 (de
Inventor
Patrice Thomson-CSF S.C.P.I. GROLIER
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Tecumseh Europe SA
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Tecumseh Europe SA
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Publication of EP0890026A1 publication Critical patent/EP0890026A1/de
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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
    • 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
    • F04B39/0072—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes characterised by assembly or mounting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2225/00—Synthetic polymers, e.g. plastics; Rubber
    • F05C2225/08—Thermoplastics
    • 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 present invention relates to a muffler system suction for refrigeration motor compressor.
  • Refrigeration motor compressors are good devices known which generally comprise in a hermetic casing a motor driving a compressor.
  • the motor-compressor is connected so sealed to the refrigeration circuit and the compressor is therefore submerged in the refrigerant gas inside the housing.
  • the compressor is generally of the alternative type and comprises therefore a piston moving inside a cylinder and actuated by the engine.
  • the refrigerant gas is sucked inside the casing, compressed in the cylinder then pumped back to the refrigeration circuit.
  • This acoustic energy is troublesome, in particular for domestic applications.
  • silencers can for example be constituted by chambers by where the refrigerant gas passes through the inlet and outlet of the compressor. These rooms have inlet and outlet duct volumes and sections which are determined to achieve the best possible attenuation on the audible frequency band.
  • U.S. Patent No. 3,396,907 describes a system where a or several chambers are connected in series with the housing of the assembly crankshaft-connecting rod, itself connected by a tube with the suction chamber of the compressor.
  • English Patent No. 1,043,888 for its part, describes a system of discharge silencer for compressor.
  • This muffler has two uneven chambers in series on the compressor discharge tube, these chambers being obtained using folded plates and assembled by welding.
  • An object of the present invention is therefore a system of suction silencer significantly improving noise reduction of suction in a motor-compressor.
  • a system of suction silencer for motor compressor of the type comprising in a hermetic casing a compressor comprising a body, inside which a cylinder containing a piston and at least one delivery, a drive motor for said piston and a closing cylinder head frontally said cylinder through a set of valves, said system silencer comprising at least one suction silencer bringing the gas refrigerant to be compressed from the inside of the casing towards the cylinder head and comprising two chambers separated by a wall, a charge tube bringing the gas from the inside of the casing to a first of said chambers, a tube of coupling passing through said wall to ensure the passage of gas from the first to the second chamber and a supply pipe connecting the second chamber to said cylinder head, said silencer system being characterized in that the volume ratio of the two chambers is of the order of 1 and is determined to obtain attenuation of the surrounding acoustic energy with a frequency of 500 Hz and in that the total volume
  • said silencer system is also characterized in that it further comprises a chamber additional serving as resonator, connected in parallel on the path of the refrigerant gas.
  • FIG. 1 is a very schematic diagram of a system known.
  • the refrigeration circuit in principle includes a compressor in a hermetic casing CH, a condenser C, a regulator DT and a evaporator E.
  • the refrigerant gas from the evaporator is introduced into the casing CH through the conduit 70.
  • the compressor placed inside the CH casing includes a piston 18 moving inside a cylinder 13 and actuated by a electric motor via a connecting rod 19.
  • the cylinder is closed frontally by a cylinder head 5 via a set of valves 20, 21.
  • the refrigerant gas is drawn from the CH casing through a suction silencer, including a chamber 10 and a load tube 100, and connected to the suction part of the cylinder head 5.
  • a suction valve 21 After passing through a suction valve 21, the gas is compressed and discharged to a discharge silencer through a discharge valve 20 and the delivery part of the cylinder head 5.
  • the delivery silencer includes a chamber 12 adjacent to chamber 10.
  • the compressed gas is discharged to the condenser C by a conduit 17 passing through the wall of the casing CH.
  • Such a compressor already provides a sound level mitigated. However, there are still too high amplitudes in the main frequency band which is for example centered around 500 Hz for the compressor considered.
  • the invention therefore aims to an optimized silencer system which provides strong attenuation in the frequency band main.
  • it aims to set the cutoff frequency in apart from the energetic harmonics of the pulsating aspiration spectrum so obtain maximum attenuation.
  • FIG 2 is a diagram of the motor compressor of Figure 1 with a suction silencer system according to the invention.
  • the same reference numbers denote the same elements on the various figures.
  • This system is based on a first concept which is the use of two coupled rooms. We therefore planned a silencer with a body 4 divided into two chambers 43 and 44 by a wall 40 and which are coupled by through a coupling tube 42 passing through the wall 40. The gas is sucked in via a charge tube 30 opening into the first chamber 43 and the second chamber 44 is connected to the part suction of the cylinder head 5 through a passage 31.
  • the effect of the two-chamber suction silencer depends essentially volume reports of the various rooms and relationships between section and length of different conduits.
  • the volume report for rooms 43 and 44 is approximately equal to 1 and preferably close to 0.9, while the total volume of room 43 + room 44 is around 7 to 11 times the displacement of the compressor.
  • the load tube 30 must have a cross section Sch (in mm 2 ) and a length Lch (in mm) such that the ratio Lch / Sch has a numerical value comprised substantially between 2 and 3 and the coupling tube 42 must have a section Sc and a length Lc such that the ratio Lc / Sc has a numerical value comprised substantially between 2 and 3.
  • the penetration length of the coupling tube 42 in the two chambers also has an effect on the transfer function of the silencer and, preferably, the penetration length, L 43 or L 44 , can be chosen in a chamber, 43 or 44, of volume V 43 or V 44 , in such a way that the ratios V 43 / L 43 and V 44 / L 44 have a numerical value comprised substantially between 0.5 and 0.9.
  • V 43 and V 44 are the complete volumes of the chambers, 43 and 44 respectively, including the volume of the coupling tube 42 therein. In all the reports mentioned in the description, the volumes are expressed in cm 3 , the lengths in mm and the sections in mm 2 .
  • the ratio of the sections of the tube load 30 at the coupling tube 42 is of the order of 0.6 and that the section of the passage 31 is approximately 2 to 2.5 times greater than that of the coupling tube.
  • a room silencer such as chamber 10 to transform it into a resonator deleting entry 100 ( Figure 1).
  • the volume of the chamber 10 is chosen to be of the order 1 to 3 times the displacement of the compressor.
  • the length Lcd and the Scd section of conduit 14 are in a ratio which has a numerical value between approximately 0.6 and 0.8.
  • the load tube 30 is arranged to so as to be as close as possible to the outlet of the conduit 70, so as to allow better guidance towards the cylinder and to avoid gas heating on contact with hot compressor elements (engine, etc ).
  • FIG. 3 represents a partial exploded view of a mode of realization of a motor-compressor according to the invention.
  • the compressor comprises a body 1, for example of cast iron, in which are arranged a cylinder 13 whose axis is substantially horizontal in the representation of the figure, and two chambers 10, 12 with their closing cups 11, 16.
  • the conduit 17 to the condenser starts from the cup 16.
  • a motor (not shown) is mounted under the body to drive by a crankshaft 190 and a connecting rod 19 the piston 18 which moves in the cylinder 13.
  • the cylinder 13 is closed frontally by a cylinder head 5 through a plate assembly valves 2.
  • the cylinder head can be machined or molded and is, for example, in aluminum although this is not limiting.
  • the valve plate assembly 2 includes a suction valve 21 and a plate 20 supporting a discharge valve 27, the movement is limited by a travel stop 28.
  • the tightness in the assembly of the valve plate assembly 2 is ensured, on the one hand, by the seal 22 on the body 1 and, on the other hand, by the seal 23 on the cylinder head 5 and a intake pipe 31 of the silencer.
  • the cylinder head 5 comes to close the assembly in including the intake pipe 31.
  • the paths of gas. Path 25 is the suction path from the supply pipe to the cylinder
  • path 26 is the discharge path from the cylinder to the breech then going back to the chamber 12 by the conduit 15, and the path 24 is the path between resonator 10 and cylinder head suction side passing through the conduit 14.
  • the silencer has a body 4 divided into two chambers by a wall 40 carrying the coupling tube 42.
  • the wall 40 is removable and is housed in slides 41 of the body 4. This greatly facilitates the mounting and adapting the silencer to the compressor in question.
  • the body 4 is closed by a cover 3 which carries on one side the load tube 30, connected to chamber 43 (FIG. 2), and on the other the supply pipe 31 which connects the second chamber 44 (FIG. 2) at the suction part of the cylinder head 5.
  • the silencer 3, 4 a thermoptastic material, for example polybutylene terephthalate.
  • the purpose of this choice is to ensure the best thermal insulation of fresh gases drawn in relation to heat sources (especially the engine).
  • a material particularly suitable for this application and of the type indicated above is the one known as VALOX (Brand filed). With a thickness of at least 2.5 mm, a reduction is obtained losses by heat transfer by a factor at least equal to 100 per compared to cast iron and at least 1000 compared to aluminum.
  • Figure 4 shows the assembled silencer.
  • the assembly of cover 3 and body 4 can be made by gluing with an epoxy adhesive hot-cured.
  • the load tube 30 has a flared inlet 32 in order to reduce pressure losses.
  • FIG. 5 is a dotted diagram showing the spectrum acoustic for the motor-compressor configuration of figure 1, made according to figure 3 but without silencer 3, 4 and with suction chamber 10.
  • the solid line curve shows, under the same conditions, the spectrum acoustics for the motor-compressor according to the invention of FIG. 3.
  • the band of third octave 500 Hz there is an improvement of more than 5 dBA without significant and annoying degradation in the rest of the spectrum. This is obviously results in a significant gain on the overall acoustic level rayon.

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

Claims (17)

  1. Schalldämpfungssystem für einen Motor-Kompressor, der in einem hermetisch geschlossenen Gehäuse (CH) einen Kompressor mit einem Körper (1), in dem ein einen Kolben (18) enthaltender Zylinder (13) und mindestens eine Ausstoßkammer (12) vorhanden sind, einen Antriebsmotor für den Kolben und einen Zylinderkopf (5) enthält, der frontal den Zylinder über eine Einheit (2) von Klappen verschließt, wobei das Schalldämpfungssystem mindestens einen Ansaugschalldämpfer (3, 4) enthält, der das zu komprimierende Gas vom Inneren des Gehäuses zum Zylinderkopf bringt und zwei durch eine Wand (40) getrennte Kammern (43, 44) aufweist, wobei ein Ansaugrohr (30) das Gas vom Innenraum des Gehäuses in eine erste der Kammern bringt und ein Kopplungsrohr (42) die Wand (40) durchdringt, um das Gas von der ersten in die zweite Kammer strömen zu lassen, und wobei eine Zufuhrleitung (31) die zweite Kammer (44) mit dem Zylinderkopf (5) verbindet, dadurch gekennzeichnet, daß das Volumenverhältnis der beiden Kammern (43, 44) in der Größenordnung von 1 liegt und so bestimmt ist, daß die akustische Energie um eine Frequenz von 500 Hz herum gedämpft wird, und daß das Gesamtvolumen der beiden Kammern etwa 7 bis 11 mal so groß wie der Zylinderinhalt des Kompressors ist.
  2. Schalldämpfungssystem nach Anspruch 1, dadurch gekennzeichnet, daß das Verhältnis des Volumens der ersten Kammer (43) zum Volumen der zweiten Kammer (44) etwa 0,9 beträgt.
  3. Schalldämpfungssystem nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, daß das Ansaugrohr (30) einen solchen Querschnitt Sch und eine solche Länge Lch besitzt, daß das Verhältnis Lch/Sch einem Zahlenwert von im wesentlichen zwischen 2 und 3 entspricht.
  4. Schalldämpfungssystem nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, daß das Kopplungsrohr (42) einen solchen Querschnitt Sc und eine solche Länge Lc besitzt, daß das Verhältnis Lc/Sc einem Zahlenwert von im wesentlichen zwischen 2 und 3 entspricht, und daß die Längen L43 und L44 des Eindringens des Kopplungsrohrs in die erste Kammer (43) beziehungsweise in die zweite Kammer (44) so gewählt sind, daß das Verhältnis zwischen den Volumen einer Kammer und der Eindringlänge des Kopplungsrohrs in diese Kammer, also V43/L43 beziehungsweise V44/L44, einem Zahlenwert von im wesentlichen zwischen 0,5 und 0,9 entspricht.
  5. Schalldämpfungssystem nach Anspruch 4, dadurch gekennzeichnet, daß das Verhältnis zwischen dem Querschnitt Sch des Ansaugrohrs (30) und dem Querschnitt Sc des Kopplungsrohrs (42) auf etwa 0,6 festgelegt ist.
  6. Schalldämpfungssystem nach Anspruch 5, dadurch gekennzeichnet, daß die Zufuhrleitung (31) einen Querschnitt von etwa dem 2- bis 2,5-fachen Wert des Querschnitts des Kopplungsrohrs (42) besitzt.
  7. Schalldämpfungssystem nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, daß der Schalldämpfer aus einem thermoplastischen Material ist.
  8. Schalldämpfungssystem nach Anspruch 7, dadurch gekennzeichnet, daß das Material ein Polybutylen-terephtalat ist.
  9. Schalldämpfungssystem nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, daß es außerdem eine zusätzliche Kammer (10) aufweist, die als Resonator wirkt und zum Ansaugverlauf des Kühlgases parallel angeschlossen ist.
  10. Schalldämpfungssystem nach Anspruch 9, dadurch gekennzeichnet, daß die zusätzliche Kammer (10) an den Saugbereich des Zylinderkopfes (5) über eine Leitung (14) angeschlossen ist.
  11. Schalldämpfungssystem nach Anspruch 10, dadurch gekennzeichnet, daß die zusätzliche Kammer (10) eine Saugkammer ist, die im Körper (1) liegt, und daß die Verbindungsleitung (14) durch die Einheit (2) von Klappen zum Zylinderkopf (5) hindurch verläuft.
  12. Schalldämpfungssystem nach einem beliebigen der Ansprüche 9 bis 11, dadurch gekennzeichnet, daß das Volumen der zusätzlichen Kammer (10) zwischen etwa 1,1 und 1,3 mal dem Zylinderinhalt des Kompressors entspricht.
  13. Schalldämpfungssystem nach Anspruch 12, dadurch gekennzeichnet, daß die Leitung (14) eine solche Länge Lcd und einen solchen Querschnitt Scd besitzt, daß das Verhältnis Lcd/Scd einem Zahlenwert von im wesentlichen zwischen 0,6 und 0,8 entspricht.
  14. Schalldämpfungssystem nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, daB das Kopplungsrohr (42) an seiner Mündung in die erste Kammer eine konvergierende Form besitzt, um die Druckverluste zu verringern.
  15. Schalldämpfungssystem nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, daß das Ansaugrohr (30) eine erweiterte Mündung (32) besitzt und in der Nähe des Einlasses (70) für das Gas in das hermetisch geschlossene Gehäuse (CH) liegt.
  16. Schalldämpfungssystem nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, daß der Schalldämpfer einen Körper (4), der durch eine entfernbare Wand (40) in zwei Kammern (43, 44) unterteilt ist, sowie einen Deckel (3) aufweist, der das Ansaugrohr (30) und die Zufuhrleitung (31) trägt.
  17. Schalldämpfungssystem nach Anspruch 16, dadurch gekennzeichnet, daß die entfernbare Wand (40) mit dem Kopplungsrohr (42) über Gleitschienen (41) in den Körper (4) eingesetzt und dort gehalten werden kann.
EP97916494A 1996-03-29 1997-03-25 Ansauggeräuschdämpfersystem für motorkühlverdichter Expired - Lifetime EP0890026B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
FR9603988 1996-03-29
FR9603988A FR2746861B1 (fr) 1996-03-29 1996-03-29 Systeme de silencieux d'aspiration pour motocompresseur de refrigeration
PCT/FR1997/000525 WO1997037130A1 (fr) 1996-03-29 1997-03-25 Systeme de silencieux d'aspiration pour motocompresseur de refrigeration

Publications (2)

Publication Number Publication Date
EP0890026A1 EP0890026A1 (de) 1999-01-13
EP0890026B1 true EP0890026B1 (de) 2001-11-28

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EP97916494A Expired - Lifetime EP0890026B1 (de) 1996-03-29 1997-03-25 Ansauggeräuschdämpfersystem für motorkühlverdichter

Country Status (12)

Country Link
US (1) US5979597A (de)
EP (1) EP0890026B1 (de)
JP (1) JP2002515102A (de)
CN (1) CN1085786C (de)
AT (1) ATE209754T1 (de)
BR (1) BR9708465A (de)
DE (1) DE69708614T2 (de)
ES (1) ES2166074T3 (de)
FR (1) FR2746861B1 (de)
PL (1) PL183525B1 (de)
TR (1) TR199801946T2 (de)
WO (1) WO1997037130A1 (de)

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AU2726599A (en) 1999-02-26 2000-09-21 Embraco Europe S.R.L. Intake silencer for sealed refrigerant compressor
DE19915918C2 (de) * 1999-04-09 2001-05-31 Danfoss Compressors Gmbh Kältemittelkompressor und Verfahren zu seiner Montage
TR200402417T1 (tr) * 2002-03-25 2005-10-21 Arçeli̇k Anoni̇m Şi̇rketi̇ Bir kompresör ve üretim yöntemi
ES2235581B1 (es) * 2002-11-25 2006-03-01 Construcciones Mecanicas Pedro Gil, S.A. Perfeccionamientos en los silenciadores-bancada para grupos soplantes.
KR100529933B1 (ko) * 2004-01-06 2005-11-22 엘지전자 주식회사 리니어 압축기
KR100565012B1 (ko) * 2004-07-01 2006-03-30 삼성광주전자 주식회사 밀폐형 압축기
KR100593847B1 (ko) * 2004-09-14 2006-06-28 삼성광주전자 주식회사 토출머플러를 갖춘 압축기
EP1828603B1 (de) * 2004-12-22 2008-04-30 ACC Austria GmbH Hermetischer kältemittelverdichter
US7578659B2 (en) * 2005-01-31 2009-08-25 York International Corporation Compressor discharge muffler
JP4606272B2 (ja) * 2005-08-12 2011-01-05 サンデン株式会社 冷却システムの電動圧縮機
CN101742887B (zh) * 2008-11-14 2012-08-29 鸿富锦精密工业（深圳）有限公司 防止气流回流装置及具有此装置的散热模块
US8306765B2 (en) * 2008-12-18 2012-11-06 Nuovo Pignone Holding S.P.A. Method and device for acoustic length testing of compressor
CN102168665A (zh) * 2011-05-03 2011-08-31 芜湖欧宝机电有限公司 一种活塞式制冷压缩机的气缸座
CN104583591B (zh) 2012-09-04 2017-04-19 开利公司 往复式制冷压缩机肘销固持
CN105003416B (zh) * 2015-07-31 2018-09-25 广州万宝集团有限公司 一种压缩机吸气消音结构
CN107939644A (zh) * 2017-12-06 2018-04-20 常熟市天银机电股份有限公司 制冷压缩机吸气消音器

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IT1179810B (it) * 1984-10-31 1987-09-16 Aspera Spa Gruppo motocompressore ermetico per circuiti frigoriferi
PL156570B1 (en) * 1987-11-27 1992-03-31 Zaklady Budowy Maszyn I Aparat Gas pressure pulsation and noise damper

Also Published As

Publication number Publication date
FR2746861A1 (fr) 1997-10-03
PL329116A1 (en) 1999-03-15
DE69708614D1 (de) 2002-01-10
TR199801946T2 (xx) 1999-01-18
EP0890026A1 (de) 1999-01-13
CN1215451A (zh) 1999-04-28
FR2746861B1 (fr) 1998-06-19
JP2002515102A (ja) 2002-05-21
ES2166074T3 (es) 2002-04-01
US5979597A (en) 1999-11-09
CN1085786C (zh) 2002-05-29
WO1997037130A1 (fr) 1997-10-09
BR9708465A (pt) 2000-01-04
PL183525B1 (pl) 2002-06-28
DE69708614T2 (de) 2002-08-01
ATE209754T1 (de) 2001-12-15

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