EP0890026B1 - Suction silencer system for a refrigeration compressor - Google Patents

Suction silencer system for a refrigeration compressor 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
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Expired - Lifetime
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EP97916494A
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German (de)
French (fr)
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EP0890026A1 (en
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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    • 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.

Abstract

PCT No. PCT/FR97/00525 Sec. 371 Date Sep. 29, 1998 Sec. 102(e) Date Sep. 29, 1998 PCT Filed Mar. 25, 1997 PCT Pub. No. WO97/37130 PCT Pub. Date Oct. 9, 1997An inlet silencer system for a refrigeration motor-compressor set. An inlet silencer is formed by a casing separated by a wall into two chambers which are coupled to each other by a coupling tube. A lid bearing an intake tube introduces refrigerant gas into the first chamber and a lead-in pipe connects the second chamber to the suction part of the cylinder head. The ratio by volume between the two chambers is in the order of 1. This ratio is determined to obtain a diminishing of the acoustic energy in the range of a frequency of 500 Hz. Furthermore, a chamber which is parallel connected on the suction path is used as a resonator to improve the attenuation and the acoustic spectrum. This device can be used on low-power, hermetically sealed, single-cylinder, alternating motor-compressor sets.

Description

La présente invention se rapporte à un système de silencieux d'aspiration pour motocompresseur dé réfrigération.The present invention relates to a muffler system suction for refrigeration motor compressor.

Les motocompresseurs de réfrigération sont des dispositifs bien connus qui comportent en général dans un carter hermétique un moteur entraínant un compresseur. Le motocompresseur est raccordé de manière étanche au circuit de réfrigération et le compresseur se trouve donc immergé dans le gaz réfrigérant à l'intérieur du carter.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.

Le compresseur est en général du type alternatif et comprend donc un piston se déplaçant à l'intérieur d'un cylindré et actionné par le moteur. Le gaz réfrigérant est aspiré à l'intérieur du carter, comprimé dans le cylindre puis refoulé vers le circuit de réfrigération.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.

Les motocompresseurs rayonnent une énergie acoustique non négligeable du fait d'une part des vibrations mécaniques engendrées et, d'autre part, du bruit généré par l'écoulement du gaz, notamment le bruit d'aspiration.Motor compressors radiate non-acoustic energy negligible due on the one hand to the mechanical vibrations generated and, secondly, noise generated by the flow of gas, in particular noise suction.

Cette énergie acoustique est gênante, en particulier pour les applications domestiques.This acoustic energy is troublesome, in particular for domestic applications.

Dans les systèmes connus, on essaie de diminuer les nuisances résultant de ce niveau sonore par diverses dispositions atténuant les vibrations et par des silencieux atténuant les bruits d'écoulement des gaz Ces silencieux peuvent par exemple être constitués par des chambres par où transite lé gaz réfrigérant à l'entrée et à la sortie du compresseur. Ces chambres ont des volumes et des sections de conduit d'entrée et de sortie qui sont déterminés pour obtenir une atténuation la meilleure possible sur la bande de fréquences audibles.In known systems, we try to reduce the nuisance resulting from this noise level by various provisions reducing the vibrations and by silencers attenuating the gas flow noises These 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.

Ainsi, le brevet américain n° 3 396 907 décrit un système où une ou plusieurs chambres sont reliées en série avec le carter de l'ensemble vilebrequin-bielle, lui-même relié par un tube avec la chambre d'aspiration du compresseur.Thus, 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.

Le brevet anglais N° 1 043 888, pour sa part décrit un système de silencieux de refoulement pour compresseur. Ce silencieux comporte deux chambres inégales en série sur le tube de refoulement du compresseur, ces chambres étant obtenues à l'aide de plaques pliées et assemblées par soudure.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.

Cependant, toutes les solutions connues jusqu'ici ne permettent pas d'obtenir une atténuation satisfaisante et il apparaít que notamment des bruits d'aspiration demeurent et sont la source d'un niveau acoustique encore trop important, en particulier dans une bande de fréquence autour de 500 Hz.However, all the solutions known so far do not allow not obtain satisfactory attenuation and it appears that in particular suction noises remain and are the source of an acoustic level still too important, especially in a frequency band around 500 Hz.

Un objet de la présente invention est donc un système de silencieux d'aspiration améliorant de manière notable l'atténuation des bruits d'aspiration dans un motocompresseur.An object of the present invention is therefore a system of suction silencer significantly improving noise reduction of suction in a motor-compressor.

Selon un premier aspect de l'invention, il est prévu un système de silencieux d'aspiration pour motocompresseur du type comportant dans un carter hermétique un compresseur comprenant un corps, à l'intérieur duquel sont ménagés un cylindre contenant un piston et au moins une chambre de refoulement, un moteur d'entraínement dudit piston et une culasse fermant frontalement ledit cylindre à travers un ensemble de clapets, ledit système de silencieux comportant au moins un silencieux d'aspiration amenant le gaz réfrigérant à comprimer de l'intérieur du carter vers la culasse et comprenant deux chambres séparées par une paroi, un tube de charge amenant le gaz de l'intérieur du carter vers une première desdites chambres, un tube de couplage traversant ladite paroi pour assurer le passage du gaz de la première vers la seconde chambre et une pipe d'amenée reliant la seconde chambre à ladite culasse, ledit système de silencieux étant caractérisé en ce que le rapport en volume des deux chambres est de l'ordre de 1 et est déterminé pour obtenir une atténuation de l'énergie acoustique aux alentours d'une fréquence de 500 Hz et en ce que le volume total des deux chambres est de l'ordre de 7 à 11 fois la cylindrée du compresseur.According to a first aspect of the invention, there is provided 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 of the two chambers is around 7 to 11 times the displacement of the compressor.

Selon un autre aspect de l'invention, ledit système de silencieux est aussi caractérisé en ce qu'il comprend en outre une chambre supplémentaire servant de résonateur, reliée en parallèle sur le trajet d'aspiration du gaz réfrigérant.According to another aspect of the invention, 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.

Grâce à ces dispositions et à d'autres particularités qui seront précisées ultérieurement, on obtient une amélioration notable du niveau sonore avec, en particulier, une forte atténuation dans la bande caractéristique du compresseur. Thanks to these provisions and other special features which will be specified later, a significant improvement in the level is obtained sound with, in particular, a strong attenuation in the band compressor characteristic.

L'invention sera mieux comprise et d'autres caractéristiques et avantages apparaítront à l'aide de la description ci-après et des dessins joints où :

  • la figure 1 représente très schématiquement un système de réfrigération avec un motocompresseur connu ;
  • la figure 2 est un schéma du motocompresseur avec un système de silencieux d'aspiration selon l'invention ;
  • la figure 3 est une vue éclatée d'une partie d'un compresseur et de son silencieux d'aspiration selon l'invention ;
  • la figure 4 représente le silencieux selon l'invention ;
  • la figure 5 est un diagramme représentant des courbes de spectre acoustique pour une configuration classique et une configuration selon l'invention.
The invention will be better understood and other characteristics and advantages will appear from the following description and the accompanying drawings, in which:
  • FIG. 1 very schematically represents a refrigeration system with a known motor-compressor;
  • Figure 2 is a diagram of the compressor with a suction silencer system according to the invention;
  • Figure 3 is an exploded view of part of a compressor and its suction silencer according to the invention;
  • FIG. 4 represents the silencer according to the invention;
  • FIG. 5 is a diagram representing acoustic spectrum curves for a conventional configuration and a configuration according to the invention.

Il existe de très nombreuses variantes de motocompresseur de réfrigération mais la plupart présentent un certain nombre de caractéristiques communes.There are many variations of but most have a number of common features.

La figure 1 est un diagramme très schématique d'un système connu. Le circuit de réfrigération comprend en principe un compresseur dans un carter hermétique CH, un condenseur C, un détendeur DT et un évaporateur E. Le gaz réfrigérant en provenance de l'évaporateur est introduit dans le carter CH par le conduit 70.Figure 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.

Le compresseur disposé à l'intérieur du carter CH comprend un piston 18 se déplaçant à l'intérieur d'un cylindre 13 et actionné par un moteur électrique par l'intermédiaire d'une bielle 19. Le cylindre est fermé frontalement par une culasse 5 par l'intermédiaire d'un ensemble de clapets 20, 21. Dans le compresseur représenté, le gaz réfrigérant est aspiré du carter CH à travers un silencieux d'aspiration, comprenant une chambre 10 et un tube de charge 100, et relié à la partie aspiration de la culasse 5. Après passage par un clapet d'aspiration 21, le gaz est comprimé et refoulé vers un silencieux de refoulement à travers un clapet de refoulement 20 et la partie refoulement de la culasse 5. Le silencieux de refoulement comprend une chambre 12 voisine de la chambre 10. Le gaz comprimé est refoulé vers le condenseur C par un conduit 17 traversant la paroi du carter CH.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. In the compressor shown, 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. 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.

Un tel motocompresseur permet déjà d'obtenir un niveau sonore atténué. Cependant, on constate encore des amplitudes trop élevées dans la bande de fréquence principale qui est par exemple centrée autour de 500 Hz pour le compresseur considéré.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.

L'invention a donc pour but un système de silencieux optimisé qui permette d'obtenir une forte atténuation dans la bande de fréquence principale. En outre, elle a pour but de placer la fréquence de coupure en dehors des harmoniques énergétiques du spectre pulsatoire d'aspiration afin d'obtenir l'atténuation maximale.The invention therefore aims to an optimized silencer system which provides strong attenuation in the frequency band main. In addition, it aims to set the cutoff frequency in apart from the energetic harmonics of the pulsating aspiration spectrum so obtain maximum attenuation.

La figure 2 est un schéma du motocompresseur de la figure 1 avec un système de silencieux d'aspiration selon l'invention. Les mêmes numéros de référence désignent les mêmes éléments sur les diverses figures. Ce système est basé sur un premier concept qui est l'utilisation de deux chambres couplées. On a donc prévu un silencieux ayant un corps 4 divisé en deux chambres 43 et 44 par une paroi 40 et qui sont couplées par l'intermédiaire d'un tube de couplage 42 traversant la paroi 40. Le gaz est aspiré par l'intermédiaire d'un tube de charge 30 débouchant dans la première chambre 43 et la deuxième chambre 44 est reliée à la partie aspiration de la culasse 5 par un passage 31.Figure 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.

D'autre part, pour améliorer encore l'amortissement, on conserve la chambre 10, mais fermée, de sorte qu'elle joue le rôle d'un résonateur (du type résonateur de Helmholtz).On the other hand, to further improve the depreciation, we keep chamber 10, but closed, so that it plays the role of a resonator (of the Helmholtz resonator type).

L'effet du silencieux d'aspiration à deux chambres dépend essentiellement des rapports de volumes des diverses chambres et des rapports entre section et longueur des différents conduits.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.

Ces différents rapports ont été définis par la Demanderesse en fonction du compresseur considéré.These different relationships have been defined by the Applicant in depending on the compressor in question.

Le rapport des volumes des chambres 43 et 44 est approximativement égal à 1 et de préférence voisin de 0,9, alors que le volume total chambre 43 + chambre 44 est de l'ordre de 7 à 11 fois la cylindrée du compresseur.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.

Par ailleurs, le tube de charge 30 doit avoir une section Sch (en mm2) et une longueur Lch (en mm) telles que le rapport Lch/Sch ait une valeur numérique comprise sensiblement entre 2 et 3 et le tube de couplage 42 doit avoir une section Sc et une longueur Lc telles que le rapport Lc/Sc ait une valeur numérique comprise sensiblement entre 2 et 3.Furthermore, 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.

D'autre part, la longueur de pénétration du tube de couplage 42 dans les deux chambres a aussi un effet sur la fonction de transfert du silencieux et, de préférence, on peut choisir la longueur de pénétration, L43 ou L44, dans une chambre, 43 ou 44, de volume V43 ou V44, de manière telle que les rapports V43/L43 et V44/L44 aient une valeur numérique comprise sensiblement entre 0,5 et 0,9. V43 et V44 sont les volumes complets des chambres, respectivement 43 et 44, y compris le volume du tube de couplage 42 s'y trouvant. Dans tous les rapports mentionnés dans la description, les volumes sont exprimés en cm3, les longueurs en mm et les sections en mm2. On the other hand, 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 .

Enfin, il est préférable que le rapport des sections du tube de charge 30 au tube de couplage 42 soit de l'ordre de 0,6 et que la section du passage 31 soit environ 2 à 2,5 fois supérieure à celle du tube de couplage.Finally, it is preferable that 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.

Comme on l'a déjà mentionné plus haut, on améliore encore l'atténuation des bruits d'aspiration en ajoutant un résonateur relié en parallèle sur le trajet d'aspiration du gaz réfrigérant. Ceci permet d'améliorer de manière ajustable le spectre acoustique obtenu en jouant sur le volume du résonateur et les dimensions du conduit de liaison.As already mentioned above, we are further improving attenuation of suction noises by adding a resonator connected in parallel on the refrigerant gas suction path. This improves the acoustic spectrum obtained by adjusting the volume is adjustable of the resonator and the dimensions of the connecting duct.

Selon un mode de réalisation particulièrement avantageux, on peut mettre à profit, dans les cas où elle existe, la présence d'une chambre de silencieux telle que la chambre 10 pour la transformer en résonateur en supprimant l'entrée 100 (figure 1).According to a particularly advantageous embodiment, can take advantage, in cases where it exists, the presence of a room silencer such as chamber 10 to transform it into a resonator deleting entry 100 (Figure 1).

De préférence, le volume de la chambre 10 est choisi de l'ordre de 1 à 3 fois la cylindrée du compresseur. En outre, la longueur Lcd et la section Scd du conduit 14 sont dans un rapport qui a une valeur numérique comprise sensiblement entre 0,6 et 0,8.Preferably, the volume of the chamber 10 is chosen to be of the order 1 to 3 times the displacement of the compressor. In addition, 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.

Il faut noter enfin que le tube de charge 30 est disposé de manière à être aussi proche que possible du débouché du conduit 70, de manière à permettre un meilleur guidage vers le cylindre et à éviter un réchauffement des gaz au contact des éléments chauds du compresseur (moteur, etc...).Finally, it should be noted that 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 ...).

La figure 3 représente une vue éclatée partielle d'un mode de réalisation d'un motocompresseur selon l'invention. Le compresseur comprend un corps 1, par exemple en fonte, dans lequel sont disposés un cylindre 13 dont l'axe est sensiblement horizontal dans la représentation de la figure, et deux chambres 10, 12 avec leurs coupelles de fermeture 11, 16. Le conduit 17 vers le condenseur part de la coupelle 16. Un moteur (non représenté) est monté sous le corps pour entraíner par un vilebrequin 190 et une bielle 19 le piston 18 qui se déplace dans le cylindre 13. Le cylindre 13 est fermé frontalement par une culasse 5 à travers un ensemble plaque à clapets 2. La culasse peut être usinée ou moulée et est, par exemple, en aluminium bien que cela ne soit pas limitatif.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.

L'ensemble plaque à clapets 2 comprend un clapet d'aspiration 21 et une plaque 20 supportant un clapet de refoulement 27, dont le mouvement est limité par une butée de débattement 28. L'étanchéité dans l'assemblage de l'ensemble plaque à clapets 2 est assuré, d'une part, par le joint 22 sur le corps 1 et, d'autre part, par le joint 23 sur la culasse 5 et une pipe d'amenée 31 du silencieux. La culasse 5 vient fermer l'ensemble en englobant la pipe d'amenée 31. On a représenté en pointillé les trajets de gaz. Le trajet 25 est le trajet d'aspiration de la pipe d'amenée vers le cylindre, le trajet 26 est le trajet de refoulement allant du cylindre à la culasse puis repartant vers la chambre 12 par le conduit 15, et le trajet 24 est le trajet entre résonateur 10 et culasse côté aspiration passant par le conduit 14. Le silencieux comporte un corps 4 divisé en deux chambres par une paroi 40 portant le tube de couplage 42. La paroi 40 est amovible et vient se loger dans des glissières 41 du corps 4. Ceci facilite beaucoup le montage et l'adaptation du silencieux au compresseur considéré. Le corps 4 est fermé par un couvercle 3 qui porte d'un côté le tube de charge 30, relié à la chambre 43 (figure 2), et de l'autre la pipe d'amenée 31 qui relie la seconde chambre 44 (figure 2) à la partie aspiration de la culasse 5.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.

De préférence, on choisit pour réaliser le silencieux 3, 4 un matériau thermoptastique, par exemple un téréphtalate de polybutylène. Le but de ce choix est d'assurer le meilleur isolement thermique des gaz frais aspirés par rapport aux sources de chaleur (moteur notamment).Preferably, we choose to make 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).

Ceci est important pour préserver un rendement convenable du motocompresseur. En effet, en évitant un réchauffement notable des gaz aspirés, on obtient des gaz les plus denses possible et ainsi, pour une cylindrée donnée, un remplissage amélioré du cylindre par un débit massique plus important, donc un pouvoir frigorifique accru pour un régime de fonctionnement donné.This is important to maintain a proper yield of the motor-compressor. Indeed, by avoiding a significant heating of the gases sucked, we obtain the densest gases possible and thus, for a given displacement, improved filling of the cylinder by a flow rate higher mass, therefore increased refrigeration capacity for a diet of given operation.

Un matériau particulièrement adapté à cette application et du type indiqué ci-dessus est celui connu sous le nom de VALOX (Marque déposée). Avec une épaisseur d'au moins 2,5 mm, on obtient une réduction des pertes par transfert thermique par un facteur au moins égal à 100 par rapport à la fonte et au moins égal à 1000 par rapport à l'aluminium.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.

La figure 4 représente le silencieux assemblé. L'assemblage du couvercle 3 et du corps 4 peut s'effectuer par collage avec une colle époxy polymérisée à chaud. Le tube de charge 30 comporte une entrée évasée 32 dans le but de diminuer les pertes de charge. De même, dans un but similaire, on peut prévoir une partie convergente sur l'entrée du tube de couplage 42, comme représenté sur la figure 3.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. Likewise, for a purpose similar, one can provide a converging part on the entry of the tube of coupling 42, as shown in FIG. 3.

Le système de silencieux selon l'invention améliore de manière notable le comportement du motocompresseur en ce qui concerne les bruits d'aspiration. La figure 5 est un diagramme montrant en pointillé le spectre acoustique pour la configuration de motocompresseur de la figure 1, réalisé selon la figure 3 mais sans silencieux 3, 4 et avec chambre d'aspiration 10. La courbe en trait plein montre, dans les mêmes conditions, le spectre acoustique pour le motocompresseur selon l'invention de la figure 3. Dans la bande de tiers d'octave 500 Hz, on constate une amélioration de plus de 5 dBA sans dégradation notable et gênante dans le reste du spectre. Ceci se traduit évidemment par un gain notable sur le niveau acoustique global rayonné.The silencer system according to the invention improves in a way noticeable the behavior of the compressor with regard to noise suction. Figure 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. In 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.

Bien entendu, l'invention n'est nullement limitée au mode de réalisation particulier décrit.Of course, the invention is in no way limited to the mode of particular embodiment described.

Claims (17)

  1. Inlet silencer system for motor-compressor sets of the type comprising, in a hermetically sealed capsule (CH), a compressor comprising a body (1), within which there are formed a cylinder (13) containing a piston (18) and at least one delivery chamber (12), a motor for the driving of the said piston and a cylinder head (5) closing the said cylinder frontally through a set of valves (2), the said silencer system including at least one inlet silencer (3, 4) conveying the refrigerant gas to be compressed from within the capsule towards the cylinder head and comprising two chambers (43, 44) separated by a wall (40), an intake tube (30) conveying the gas from within the capsule towards a first (43) of the said chambers, a coupling tube (42) going through the said wall (40) to provide for the passage of the gas from the first chamber to the second chamber and a lead-in pipe (31) connecting the second chamber (44) to the said cylinder head (5), the said silencer system being characterized in that the ratio by volume between the two chambers (43, 44) is of the order of 1 and is determined in order to obtain an attenuation of acoustic energy in the region of a frequency of 500 Hz, and in that the total volume of the two chambers is of the order of 7 to 11 times the cubic capacity of the compressor.
  2. Silencer system according to Claim 1, characterized in that the ratio of the volume of the said first chamber (43) to the volume of the said second chamber (44) is about 0.9.
  3. Silencer system according to one of the preceding claims, characterized in that the intake tube (30) has a section Sch and a length Lch such that the ratio Lch/Sch has a numerical value substantially ranging from 2 to 3.
  4. Silencer system according to one of the preceding claims, characterized in that the said coupling tube (42) has a section Sc and a length Lc such that the ratio Lc/Sc has a numerical value substantially ranging from 2 to 3 and in that the lengths L43 and L44 of penetration of the coupling tube respectively into the first chamber (43) and the second chamber (44) are such that the ratio between the volume of a chamber and the length of penetration into this chamber, respectively V43/L43 and V44/L44, has a numerical value substantially ranging from 0.5 to 0.9.
  5. Silencer system according to Claim 4, characterized in that the ratio between the section Sch of the intake tube (30) and the section Sc of the coupling tube (42) is chosen to be of the order of 0.6.
  6. Silencer system according to Claim 5, characterized in that the lead-in pipe (31) has a section of about 2 to 2.5 times greater than that of the coupling tube (42).
  7. Silencer system according to one of the preceding claims, characterized in that the said silencer is made of a thermoplastic material.
  8. Silencer system according to Claim 7, characterized in that the said material is a polybutylene terephthalate.
  9. Silencer system according to one of the preceding claims, characterized in that it furthermore comprises an additional chamber (10) serving as a resonator, connected in parallel to the suction path of the refrigerant gas.
  10. Silencer system according to Claim 9, characterized in that the said additional chamber (10) is connected to the suction part of the cylinder head (5) by a conduit (14).
  11. Silencer system according to Claim 10, characterized in that the said additional chamber (10) is a suction chamber positioned in the said body (1) and in that the linking conduit (14) is made through the set of valves (2) towards the cylinder head (5).
  12. Silencer system according to any one of Claims 9 to 11, characterized in that the volume of the said additional chamber (10) is of the order of 1.1 to 1.3 times the cubic capacity of the compressor.
  13. Silencer system according to Claim 12, characterized in that the said conduit (14) has a length Lcd and a section Scd such that the ratio Lcd/Scd has a numerical value ranging substantially from 0.6 to 0.8.
  14. Silencer system according to one of the preceding claims, characterized in that the said coupling tube (42) has an inlet with a shape that is convergent in the said first chamber (43) to reduce the pressure drops.
  15. Silencer system according to one of the preceding claims, characterized in that the said intake tube (30) has a flared-out opening (32) and is positioned in the vicinity of the gas inlet (70) in the hermetically sealed capsule (CH).
  16. Silencer system according to one of the preceding claims, characterized in that the said silencer comprises a body (4) divided into two chambers (43, 44) by a detachable wall (40) and a lid (3) bearing the intake tube (30) and the lead-in pipe (31).
  17. Silencer system according to Claim 16, characterized in that the said detachable wall (40) with the coupling tube (42) may be introduced and held in position in the body (4) by means of slideways (41).
EP97916494A 1996-03-29 1997-03-25 Suction silencer system for a refrigeration compressor Expired - Lifetime EP0890026B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
FR9603988A FR2746861B1 (en) 1996-03-29 1996-03-29 SUCTION MUFFLER SYSTEM FOR REFRIGERATION MOTOR COMPRESSOR
FR9603988 1996-03-29
PCT/FR1997/000525 WO1997037130A1 (en) 1996-03-29 1997-03-25 Suction silencer system for a refrigeration compressor

Publications (2)

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

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EP97916494A Expired - Lifetime EP0890026B1 (en) 1996-03-29 1997-03-25 Suction silencer system for a refrigeration compressor

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

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DE19915918C2 (en) * 1999-04-09 2001-05-31 Danfoss Compressors Gmbh Refrigerant compressor and method for its assembly
AU2003225467A1 (en) * 2002-03-25 2003-10-08 Arcelik A.S. A compressor with suction muffler strusture
ES2235581B1 (en) * 2002-11-25 2006-03-01 Construcciones Mecanicas Pedro Gil, S.A. PERFECTION IN THE SILENCERS-BANKING FOR BLOWING GROUPS.
KR100529933B1 (en) * 2004-01-06 2005-11-22 엘지전자 주식회사 Linear compressor
KR100565012B1 (en) * 2004-07-01 2006-03-30 삼성광주전자 주식회사 Hermetic compressor
KR100593847B1 (en) * 2004-09-14 2006-06-28 삼성광주전자 주식회사 Compressor with discharge muffler
EP1828603B1 (en) * 2004-12-22 2008-04-30 ACC Austria GmbH Hermetic refrigerant compressor
US7578659B2 (en) * 2005-01-31 2009-08-25 York International Corporation Compressor discharge muffler
JP4606272B2 (en) * 2005-08-12 2011-01-05 サンデン株式会社 Cooling system electric compressor
CN101742887B (en) * 2008-11-14 2012-08-29 鸿富锦精密工业（深圳）有限公司 Device for preventing air flow from refluxing and heat dissipation module provided with same
US8306765B2 (en) * 2008-12-18 2012-11-06 Nuovo Pignone Holding S.P.A. Method and device for acoustic length testing of compressor
CN102168665A (en) * 2011-05-03 2011-08-31 芜湖欧宝机电有限公司 Cylinder seat of piston type refrigerating compressor
WO2014039149A1 (en) 2012-09-04 2014-03-13 Carrier Corporation Reciprocating refrigeration compressor wrist pin retention
CN105003416B (en) * 2015-07-31 2018-09-25 广州万宝集团有限公司 A kind of compressor air suction noise-reducing structure
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PL156570B1 (en) * 1987-11-27 1992-03-31 Zaklady Budowy Maszyn I Aparat Gas pressure pulsation and noise damper

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JP2002515102A (en) 2002-05-21
DE69708614D1 (en) 2002-01-10
DE69708614T2 (en) 2002-08-01
US5979597A (en) 1999-11-09
ES2166074T3 (en) 2002-04-01
CN1085786C (en) 2002-05-29
WO1997037130A1 (en) 1997-10-09
TR199801946T2 (en) 1999-01-18
BR9708465A (en) 2000-01-04
CN1215451A (en) 1999-04-28
FR2746861A1 (en) 1997-10-03
PL329116A1 (en) 1999-03-15
ATE209754T1 (en) 2001-12-15
FR2746861B1 (en) 1998-06-19
PL183525B1 (en) 2002-06-28
EP0890026A1 (en) 1999-01-13

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