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US20070059189A1 - Hermetic compressor and manufacturing method of suction muffler - Google Patents

Hermetic compressor and manufacturing method of suction muffler Download PDF

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Publication number
US20070059189A1
US20070059189A1 US10/574,858 US57485804A US2007059189A1 US 20070059189 A1 US20070059189 A1 US 20070059189A1 US 57485804 A US57485804 A US 57485804A US 2007059189 A1 US2007059189 A1 US 2007059189A1
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US
United States
Prior art keywords
suction muffler
casing
hermetic compressor
compressor according
foam
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.)
Abandoned
Application number
US10/574,858
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English (en)
Inventor
Akira Nakano
Ko Inagaki
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.)
Panasonic Corp
Original Assignee
Matsushita Electric Industrial Co Ltd
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 Matsushita Electric Industrial Co Ltd filed Critical Matsushita Electric Industrial Co Ltd
Publication of US20070059189A1 publication Critical patent/US20070059189A1/en
Assigned to MATSUSHITA ELECTRIC INDUSTRIAL CO., LTD. reassignment MATSUSHITA ELECTRIC INDUSTRIAL CO., LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: INAGAKI, KO, NAKANO, AKIRA
Assigned to PANASONIC CORPORATION reassignment PANASONIC CORPORATION CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). Assignors: MATSUSHITA ELECTRIC INDUSTRIAL CO., LTD.
Abandoned 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
    • F04B39/0061—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes using muffler volumes
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B29—WORKING OF PLASTICS; WORKING OF SUBSTANCES IN A PLASTIC STATE IN GENERAL
    • B29C—SHAPING OR JOINING OF PLASTICS; SHAPING OF MATERIAL IN A PLASTIC STATE, NOT OTHERWISE PROVIDED FOR; AFTER-TREATMENT OF THE SHAPED PRODUCTS, e.g. REPAIRING
    • B29C44/00—Shaping by internal pressure generated in the material, e.g. swelling or foaming ; Producing porous or cellular expanded plastics articles
    • B29C44/34—Auxiliary operations
    • B29C44/3469—Cell or pore nucleation
    • B29C44/348—Cell or pore nucleation by regulating the temperature and/or the pressure, e.g. suppression of foaming until the pressure is rapidly decreased
    • 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
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
    • 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
    • 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
    • F04B39/02—Lubrication
    • F04B39/0223—Lubrication characterised by the compressor type
    • F04B39/023—Hermetic compressors
    • 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
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/121—Casings
    • C—CHEMISTRY; METALLURGY
    • C08—ORGANIC MACROMOLECULAR COMPOUNDS; THEIR PREPARATION OR CHEMICAL WORKING-UP; COMPOSITIONS BASED THEREON
    • C08G—MACROMOLECULAR COMPOUNDS OBTAINED OTHERWISE THAN BY REACTIONS ONLY INVOLVING UNSATURATED CARBON-TO-CARBON BONDS
    • C08G2101/00—Manufacture of cellular products
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/14—Refrigerants with particular properties, e.g. HFC-134a
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2280/00—Materials; Properties thereof
    • F05B2280/60—Properties or characteristics given to material by treatment or manufacturing
    • F05B2280/6012—Foam
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2280/00—Materials; Properties thereof
    • F05B2280/60—Properties or characteristics given to material by treatment or manufacturing
    • F05B2280/6015—Resin
    • 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
    • Y10S417/00—Pumps
    • Y10S417/902—Hermetically sealed motor pump unit

Definitions

  • the present invention relates to a hermetic compressor for use in a refrigerator, an air conditioner, a freezing refrigerating apparatus or the like, and more particularly relates to its suction muffler and an improvement of its manufacturing method.
  • a hermetic compressor used in a freezing refrigerating apparatus or the like strongly desires that energy efficiency is high, in addition to a fact that the noise caused by an operation is low.
  • hermetic compressor As a conventional hermetic compressor, there is a hermetic compressor whose energy efficiency is improved by improving the sound attenuation effect of a suction muffler and effectively using the sound attenuation effect and consequently increasing the refrigerant circulation quantity into a compression chamber (for example, refer to the following patent document 1).
  • hermetic compressor whose energy efficiency is improved by maintaining the refrigerant gas, which is returned from a freezing cycle, at the state of a low temperature and high density and sucking into the compression room (for example, refer to the following patent document 2).
  • FIG. 17 is a sectional view of the conventional hermetic compressor
  • FIG. 18 is a sectional view of a suction muffler in FIG. 19
  • FIG. 19 is a flow velocity vector diagram showing the behavior of the refrigerant gas by using the flow vector within the suction muffler shown in FIG. 18 .
  • a hermetic vessel 1 accommodates: a motor element 5 composed of a rotator 4 and a stator 3 holding a coil portion 2 ; and a compression element 6 driven by the motor element 5 .
  • a lubricating oil 8 is stored in the hermetic vessel 1 .
  • a crank shaft 10 has: a main shaft portion 11 where the rotator 4 is press-fitted and fixed; and an eccentric portion 12 formed eccentrically to the main shaft portion 11 .
  • an oil pump 13 is placed inside the main shaft portion 11 so as to be opened in the lubricating oil 8 .
  • a cylinder block 20 formed above the motor element 5 has: a compression room 22 that is approximately cylindrical; and a shaft supporter 23 that supports the main shaft portion 11 with a shaft.
  • a piston 30 is inserted into the compression chamber 22 of the cylinder block 20 so as to be reciprocatingly slidable therein, and linked to the eccentric portion 12 by a linking device 31 .
  • a valve plate 35 for sealing the open end surface of the compression room 22 has a suck hole 38 to be linked to the compression room 22 in accordance with the opening/closing action of a suction valve 34 .
  • a cylinder head 36 is fixed through the valve plate 35 to the opposite side to the compression room 22 .
  • a suction tube 37 is fixed to the hermetic vessel 1 and connected to the low pressure side (not shown) of a freezing cycle, and introduces the refrigerant gas (not shown) into the hermetic vessel 1 .
  • a suction muffler 40 is fixed because it is interposed between the valve plate 35 and the cylinder head 36 , and it is made of synthetic resin, such as polybutylene telephthalate and the like, to which glass fiber is mainly added.
  • the suction muffler 40 has a sound attenuation space 43 and also has: a second linkage path 46 where an open end 46 b is linked into the hermetic vessel 1 and an open end 46 a is opened while extended to the sound attenuation space 43 ; and a first linkage path 45 where an open end 45 b is linked to the suck hole 38 of the valve plate 35 and an open end 45 a is opened while extended to the sound attenuation space 43 .
  • FIG. 19 shows flow velocity vectors 60 indicating the behavior of the refrigerant gas within the suction muffler 40 obtained by a computer simulation.
  • the length of each vector indicates the magnitude of the flow velocity, and the orientation of the vector indicates the flow direction of the refrigerant gas.
  • respective arrows indicate an upper eddy 61 generated by the upstream flows in the refrigerant gas sucked from the open end 46 a of the second linkage path 46 , and a lower eddy 62 generated by the downstream flow in the refrigerant gas sucked from the open end 46 a of the second linkage path 46 .
  • the piston 30 reciprocates inside the compression room 22 . Due to this operation, the refrigerant gas is introduced into the hermetic vessel 1 through the suction tube 37 from the cooling system (not shown). The refrigerant gas introduced into the hermetic vessel 1 is sucked from the open end 46 b of the suction muffler 40 , and released to the sound attenuation space 43 from the open end 46 a.
  • the released refrigerant gas after colliding with the wall of the casing of the suction muffler 40 that is close and opposite to the open end 46 a as shown in FIG. 19 , generates the upper eddy 61 and the lower eddy 62 , and circulates through the sound attenuation space 43 .
  • the refrigerant gas mainly constituted by the upper eddy 61 is sucked from the open end 45 a to the first linkage path 45 and introduced into the suck hole 38 opened in the valve plate 35 .
  • the pressure pulsation of the refrigerant induced when the refrigerant is sucked into the compression room 22 is propagated in the direction opposite to the flow of the refrigerant as mentioned above and propagated from the open end 45 a to the sound attenuation space 43 .
  • the first linkage path 45 is extended into the sound attenuation space 43 where the sound attenuation effect is high, and the open end 45 a is located in the node of the sound, for example, in the 3 to 4 kHz region where the noise becomes troublesome, it is possible to obtain the high sound attenuation effect in a particular frequency band.
  • the noise pulsation attenuated in the sound attenuation space 43 is further attenuated by adjusting the dimension of the sound attenuation space 43 and the length and inner diameter of the second linkage path 46 .
  • the noise pulsation attenuated in the sound attenuation space 43 is further attenuated by adjusting the dimension of the sound attenuation space 43 and the length and inner diameter of the second linkage path 46 .
  • FIG. 20 shows a sectional view of a suction muffler of another conventional hermetic compressor.
  • Another conventional example will be described below with reference to the drawings.
  • the entire configuration except the suction muffler is similar to the above-mentioned conventional example.
  • the detailed explanation is omitted.
  • a suction muffler 50 has a resonant space 58 placed so as to surround a suction space 57 .
  • a second linkage path 56 one end is linked to the hermetic vessel 1 , and the other end is linked o the suction space 57 .
  • a first linkage path 55 an open end 55 a is opened to the suction space 57 , and the other end is linked through the suction valve 34 to the compression room 22 , and this has a linkage hole 59 to link the first linkage path 55 and the resonant space 58 .
  • the suction space 57 is surrounded by the resonant space 58 , the suction space 57 is thermally insulated by the refrigerant gas in the resonant space 58 and the wall portion constituting the casing of the resonant space 58 .
  • the refrigerant gas inside the suction space 57 is not directly heated by the refrigerant gas of a high temperature within the hermetic vessel 1 , and the refrigerant gas of a high density can be sucked into the compression room 22 .
  • the suck efficiency can be made higher.
  • the resonant space 58 is linked through the linkage hole 59 to the suction space 57 , it acts as a resonant room, and the noise can be reduced.
  • the refrigerant gas which is sucked into the suction muffler 40 through the hermetic vessel 1 from the cooling system (not shown) by the reciprocating motion of the piston 30 and released to the sound attenuation space 43 from the second linkage path 46 , as shown in FIG. 19 , does not directly flow into the first linkage path 45 , and it collides with the wall of the casing of the suction muffler 40 , which is close and opposite to the open end 46 a , and then generates the upper eddy 61 and the lower eddy 62 and circulates through the sound attenuation space 43 .
  • the heat-exchange is carried out between the refrigerant gas of the low temperature returned from the cooling system and the refrigerant gas of the high temperature within the hermetic vessel 1 .
  • the heat-exchange is carried out between the refrigerant gas of the low temperature returned from the cooling system and the refrigerant gas of the high temperature within the hermetic vessel 1 .
  • it is greatly heated.
  • the open end 45 a is close and opposite to the wall of the casing of the suction muffler 40 .
  • the wall of the casing of the close opposite suction muffler 40 is vibrated by the influence of the open end 45 a in which the pressure pulsation becomes maximum.
  • the pulsation sound of the refrigerant is radiated out of the casing of the suction muffler 40 .
  • this has a problem that the noise is increased.
  • the suction space 57 constituting the suction muffler 50 is placed so as to be surrounded by the resonant space 58 .
  • the whole of the suction space 57 is configured so as to be surrounded by the resonant space 58 .
  • this has problems that the entire dimension of the suction muffler 50 becomes bigger and the number of parts becomes greater or the molding becomes complex.
  • the present invention solves the above-mentioned conventional problems and has an object to provide the hermetic compressor in which the suck efficiency is high and the noise vibration is small, and the manufacturing method of the suction muffler.
  • the hermetic compressor of the present invention at least -a part of a casing of the suction muffler is foam-molded.
  • this due to the thermal insulating effect of bubbles generated within foamed synthetic resin, this has an action of extremely improving the thermal insulating performance under the same volume, and dropping the loss caused by heat reception, as compared with non-foamed resin, and also has an action of increasing the acoustic transmission loss because acoustic energy is absorbed by the friction between the gas within the bubble and the synthetic resin material around the bubble.
  • the hermetic compressor of the present invention can make the suck efficiency of the refrigerant gas higher and reduce the noise vibration.
  • One aspect of the present invention has a motor element inside a hermetic vessel, a compression element driven by the motor element, and a suction muffler made of synthetic resin that is linked to the compression element, and at least a part of a casing of the suction muffler is foam-molded.
  • the thermal insulating performance is extremely improved as compared with the resin of the non-foamed solid material.
  • the heat reception from the refrigerant gas of a low temperature sucked into the suction muffler can be largely reduced, thereby making the suck efficiency higher.
  • the absorption of the acoustic energy caused by the friction between the gas within the bubble and the material around the bubble increases the acoustic transmission loss, which enables the reduction in the noise vibration.
  • the bubble diameter obtained by the foam-molding is 50 ⁇ m or less.
  • the number of the bubbles is increased to make the thermal insulating effect higher.
  • the suck efficiency can be made higher.
  • the material of the foam-molding is crystal synthetic resin.
  • the chemical resistance is high, and the solubility of the resin material to the refrigerant and the lubricating oil is dropped.
  • the skin layer where the bubble does not exist substantially is formed on the surface of the foam-molding.
  • the refrigerant and the lubricating oil are hard to permeate into the suction muffler.
  • the thickness of the skin layer is 30% or less of the plate thickness in the thinnest portion.
  • the foaming magnification of the foam-molding is 1.2 times or more.
  • the excellent thermal insulating performance is obtained, it is possible to make the suck efficiency higher and obtain the excellent absorption effect of the acoustic energy.
  • the noise vibration can be further reduced.
  • the plate thickness of the wall where the maximum projection area is obtained is thicker than the plate thicknesses of the other walls.
  • the casing is produced by combining at least two parts, and the two parts are separated and divided in the direction substantially vertical to the wall where the maximum projection area of the casing is obtained.
  • the plate thicknesses of the corner of the casing and the portion having the high curvature are relatively larger than the other portions, the flow resistance of the resin at the time of the molding is dropped.
  • the molding since the molding is possible at the low pressure, the growth of the bubble through the foaming gas is impelled, and since the foaming magnification is made higher to consequently make the thermal insulating property higher, the loss caused by the heat reception is dropped.
  • the suction muffler includes a sound attenuation space formed inside the casing, a first linkage path to link the compression element and the sound attenuation space, and a second linkage path to link the hermetic vessel and the sound attenuation space, and wherein a wall of the casing, which is close to at least one of the motor element, the compression element, an open end within the sound attenuation space of the first linkage path, and an open end within the sound attenuation space of the second linkage path is designed so as to have at least one of the configuration that it is thicker than the other walls of the casing and the configuration that it is higher in foaming magnification.
  • the lubricating oil is stored in the hermetic vessel, and at least one of the walls of the casing of the suction muffler to which the lubricating oil is supplied is designed so as to have at least one of the configuration that it is thicker than the other walls of the casing and the configuration that it is higher in foaming magnification.
  • the casing of the suction muffler has a suction muffler body and a suction muffler cover, and the bonding portion between the suction muffler body and the suction muffler cover has the foaming magnification that is relatively lower as compared with the portions except the bonding portion, or it is not foam-molded. Since the vibration absorption effect through the bubble is suppressed, in addition to the above-mentioned effects, the bonding strength can be made higher.
  • the linkage path to link the inner portion of the hermetic vessel and the sound attenuation space of the suction muffler is formed integrally with the farthest element from the motor element, among the plurality of elements constituting the casing of the suction muffler.
  • a part of the casing of the suction muffler is interposed between the cylinder head and the valve plate, which constitute the compression element, and the interposed part of the casing has the relatively low foaming magnification, or it is not foam-molded.
  • the strength of the engaged portion is held, which enables the muffler to be surely held.
  • a part of the casing of said suction muffler is interposed between the cylinder head and the valve plate which constitute said compression element, and the thickness of said interposed part of said casing is thicker than the other portions.
  • the motor element is inverter-driven, which absorbs the noise associated with the fast pulsation flow of the refrigerant at the time of the fast rotation number operation where the refrigerant circulation quantity is great.
  • the noise can be further reduced.
  • the rotation number is 20 r/sec or less, which consequently suppresses the heat-exchange between the low temperature refrigerant gas sucked into the suction muffler and the heat source, such as the high temperature refrigerant gas and the like, inside the hermetic vessel when the low rotation number operation causes the drop in the refrigerant flow velocity.
  • the suck efficiency can be further reduced.
  • the refrigerant gas compressed by the compression element is R600a
  • the refrigerant circulation quantity is increased, and the noise of the high frequency in the audible region associated with the fast pulsation flow of the refrigerant gas is absorbed.
  • the noise can be further reduced.
  • Another aspect of the present invention is a manufacturing method of a suction muffler, which foam-molds at least a part of a casing of a suction muffler made of synthetic resin for a hermetic compressor, wherein in the molding course, a core-back is used to move a part of a die, enlarge a cavity and make a plate thickness thicker. Then, by enlarging the die, the pressure is dropped and the gas is expanded, thereby impelling the foaming.
  • the higher foaming magnification is obtained, the excellent thermal insulating performance is obtained, thereby enabling the suck efficiency to be made higher.
  • Another embodiment of the present invention is a manufacturing method of a suction muffler, which foam-molds at least a part of a casing of a suction muffler made of synthetic resin for a hermetic compressor, wherein a section area of a gate serving as a resin supplying portion to cavities inside a die is equal to or greater than 70% of a square of a plate thickness of the casing.
  • Another embodiment of the present invention is a manufacturing method of a suction muffler, which foam-molds at least a part of a casing of a suction muffler made of synthetic resin for a hermetic compressor, wherein two or more gates serving as resin supplying portions to cavities inside a die are installed for at least one unit.
  • the installation of the plurality of gates causes the resin to be easily permeated into the die.
  • the molding is possible under the low pressure, which impels the growth of the bubble through the foamed gas. Then, by making the foaming magnification higher and making the foaming magnification higher, the loss caused by the heat reception is reduced.
  • FIG. 1 is a sectional view of a hermetic compressor in a first embodiment 1 of the present invention
  • FIG. 2 is a sectional view of a suction muffler in the same embodiment
  • FIG. 3 is an enlarged sectional view of a wall A portion in FIG. 2 ;
  • FIG. 4 is a main portion sectional view of a corner of the hermetic compressor in the same embodiment
  • FIG. 5A is a schematic configuration view of a foam molding machine in the same embodiment
  • FIG. 5B is a schematic configuration view of a foam molding machine in the same embodiment
  • FIG. 5C is a schematic configuration view of a foam molding machine in the same embodiment
  • FIG. 6 is a front view showing a suction muffler body and a runner in the same embodiment
  • FIG. 7 is a sectional view of a suction muffler in a second embodiment of the present invention.
  • FIG. 8 is an enlarged view of a foaming portion of the suction muffler in the same embodiment
  • FIG. 9 is a rear view of a suction muffler body in the same embodiment.
  • FIG. 10 is a decomposed perspective view of the suction muffler in the same embodiment.
  • FIG. 11 is an enlarged view of a bonded section between a cover and the suction muffler in the same embodiment
  • FIG. 12A is a schematic configuration view of a supercritical foam molding machine in the same embodiment
  • FIG. 12B is a schematic configuration view of a supercritical foam molding machine in the same embodiment
  • FIG. 12C is a schematic configuration view of a supercritical foam molding machine in the same embodiment.
  • FIG. 13 is a sectional view of a hermetic compressor in a third embodiment of the present invention.
  • FIG. 14 is a decomposition view of a suction muffler in the same embodiment
  • FIG. 15A is a schematic configuration view of a supercritical foam molding machine in the same embodiment
  • FIG. 15B is a schematic configuration view of a supercritical foam molding machine in the same embodiment.
  • FIG. 15C is a schematic configuration view of a supercritical foam molding machine in the same embodiment.
  • FIG. 16 is a decomposition view of a suction muffler in a fourth embodiment of the present invention.
  • FIG. 17 is a sectional view of a conventional hermetic compressor
  • FIG. 18 is a sectional view of a suction muffler in the conventional hermetic compressor
  • FIG. 19 is a flow velocity vector view inside the suction muffler of the conventional hermetic compressor.
  • FIG. 20 is a sectional view of the suction muffler in the conventional hermetic compressor.
  • FIG. 1 is a sectional view of a hermetic compressor in the first embodiment of the present invention
  • FIG. 2 is a sectional view of a suction muffler of the hermetic compressor in the same embodiment.
  • FIG. 3 is an enlarged sectional view of a wall A-portion in FIG. 2 .
  • FIG. 4 is a main portion sectional view of a corner in the suction muffler in the same embodiment.
  • FIGS. 5A to 5 C are schematic configuration views of a foam molding machine in the same embodiment.
  • FIG. 6 is a front view showing a suction muffler body and a runner in the same embodiment.
  • a hermetic vessel 101 accommodates: a motor element 105 composed of a rotator 104 and a stator 103 holding a coil portion 102 ; and a compression element 106 driven by the motor element 105 .
  • a lubricating oil 108 is stored in the hermetic vessel 101 .
  • refrigerant gas (not shown), R600a of natural refrigerant is used.
  • the motor element 105 is driven by an inverter method including a rotation number of 20 r/sec or less.
  • a crank shaft 110 has: a main shaft portion 111 where the rotator 104 is press-fitted and fixed; and an eccentric portion 112 formed eccentrically to the main shaft portion 111 .
  • an oil pump 113 is placed so as to be opened in the lubricating oil 108 .
  • a cylinder block 120 formed above the motor element 105 has: a compression room 122 that is approximately cylindrical; and a shaft supporter 123 that supports the main shaft portion 111 with a shaft.
  • a piston 130 is inserted into the compression chamber 122 of the cylinder block 120 so as to be reciprocatingly slidable therein, and linked to the eccentric portion 112 by a linking device 131 .
  • a valve plate 135 for sealing the open end surface of the compression room 122 has a suck hole 138 to be linked to the compression room 122 in accordance with the opening/closing action of a suction valve 134 .
  • a cylinder head 136 is fixed through the valve plate 135 to the opposite side to the compression room 122 .
  • a suction tube 137 is fixed to the hermetic vessel 101 and connected to the low pressure side (not shown) of a freezing cycle, and introduces the refrigerant gas (not shown) into the hermetic vessel 101 .
  • a suction muffler 140 is fixed because it is interposed between the valve plate 135 and the cylinder head 136 , and it is made of synthetic resin, such as polybutylene telephthalate and the like, to which glass fiber is mainly added.
  • the suction muffler 140 has: a casing 140 C composed of a plurality of walls; a first linkage path 145 and a second linkage path 146 , and a sound attenuation space 143 is formed inside the casing 140 C.
  • a wall 147 of the casing 140 C of the suction muffler 140 which is close and opposite to open ends 145 a , 146 a within the sound attenuation space, in order to generate innumerable bubbles 150 of about 100 ⁇ m at a bubbling magnification of 1.2 times or more, a non-foaming skin layer 151 where a plate thickness is 3 to 5 mm and thicker than the other portions and bubbles are not contained in the vicinity of the surface is formed.
  • the thicknesses E, F of the skin layer are about 10 to 20% of a plate thickness G.
  • a plate thickness B of a corner 140 a of the casing 140 C of the suction muffler 140 is thicker than the plate thicknesses C, D of a flat portion.
  • the bubble 150 made by a foaming resin molding (which will be described later in detail) is generated at the size of a bubble density of about 10 7 cells/cm 3 and a bubble diameter of about 100 ⁇ m by adjusting the thickness of the wall and the molding temperature and molding pressure at the time of the foam molding. Due to the thermal insulation effect of the bubble 150 , the thermal insulation performance improvement of about 5 to 10% is attained as compared with a non-foaming solid material.
  • an injection molder 170 is provided with a raw material inserter 171 , a fusion injector 172 , a die unit 177 , a controller (not shown) for controlling the drive of the die unit 177 and the cooling temperature and the like and adjusting the bubble density and the bubble diameter.
  • the molding process for the foaming resin by using the injection molder 170 will be described below.
  • the raw material pellet of polybutylene telephthalate and the pellet of the chemical foaming agent such as azo compound represented by azodicalbonamide and the like are thrown into the raw material inserter 171 .
  • the thrown into raw material pellet and foaming agent pellet are fused at a temperature of about 250° C. or more in the fusion injector 172 , mixed by a screw 175 built in the fusion injector 172 , squeezed by the screw 175 and injected into the die unit 177 .
  • the fused resin supplied into the die unit 177 from a sprue 181 is passed through a runner 182 serving as a flowing path and supplied to a plurality of cavities 183 having the shapes of the molded products which are formed inside the die.
  • Two gates 185 , 186 serving as the inlets of the resin to the cavities 183 are placed for one part. They are selected such that the section areas of the gates 185 , 186 are thinner than the runner 182 , the thicknesses are 30 to 40% of the wall thickness, and the widths are about three times the thicknesses.
  • the friction when it is passed through the gates 185 , 186 causes the increase in the temperature and the drop in the pressure.
  • the mixed fused foaming agent is gasified within the cavity 183 , and it becomes the foaming gas in the fused raw material, and the bubble is generated.
  • the die unit 177 since the die unit 177 has the structure cooled by gas and liquid, the raw material and foaming gas which are injected into the cavities 183 defined by the die unit 177 are cooled to a constant temperature and consequently molded.
  • the controller adjusts the injection quantities and injection temperatures of the raw material and foaming agent and the cooling temperature of the die unit 177 and the like, and controls the temperature and pressure at the time of the molding.
  • it is possible to arbitrarily adjust the bubble density and bubble diameter of the foaming resin.
  • the high foaming magnification can be obtained by setting the quantity of the fusion resin injected into the cavities 183 defined by the die unit 177 to be smaller than the volume of the cavities 183 , and filling the remaining space with the expansion through the foaming.
  • the fusion resin is high in viscosity.
  • the flow is the fastest at the center of the plate thickness of the molded member. As it approaches the surface of the die unit 177 , the velocity becomes slower. The region where the resin does not substantially flow appears in the very vicinity of the surface of the die unit 177 .
  • the fusion resin is sharply cooled because it is adhered closely to the die unit 177 of the low temperature at the substantially static state.
  • the resin is hardened before the formation of the bubble.
  • the skin layer is formed in which the bubble does not exist substantially.
  • the rate of the layer having the bubbles generated between the skin layer and the skin layer becomes small, which leads to the situation that as a whole, the bubble is little and the thermal insulation property is low.
  • the thicknesses E, F of the skin layers can be limited to about 10 to 20% of the plate thickness G, and by setting the foaming magnification at about 1.2 times at the weight ratio to the solid member, the thermal insulation property can be partially improved.
  • the gap where the fusion resin can actually flow becomes extremely narrower, and the resistance against the flow of the fused resin is increased.
  • the pressure caused by the foaming gas is relatively weak.
  • the resin does not sufficiently flow.
  • the cavities 183 defined by the die unit 177 cannot be filled with the resin.
  • the large quantity of the resin is injected at the high pressure, which results in the drop in the foaming magnification.
  • the refrigerant gas introduced into the hermetic vessel 101 by the reciprocating motion of the piston is sucked from the suction muffler 140 , and released to the sound attenuation space 143 from the open end 146 a within the sound attenuation space.
  • the released refrigerant gas collides with the wall 147 of the casing 140 C of the suction muffler 140 which is close and opposite to the open end 146 a within the sound attenuation space, and then circulates through the sound attenuation space 143 .
  • the refrigerant gas mainly circulating through the upper portion is sucked to the first linkage path 145 from the open end 145 a within the sound attenuation space, and compressed in the compression room 122 and discharged to the cooling system.
  • the plate thickness is set to 3 to 5 mm, thereby obtaining the thermal insulating effect which is partially high consequently, as compared with the case of foam-molding the suction muffler 140 as a whole, it is possible to obtain the effective thermal insulating effect at the small volume.
  • the action for maintaining the refrigerant gas at the state of the low temperature and high density can be effectively made higher, thereby increasing the mass flow quantity of the refrigerant gas.
  • the reduction effect of the loss caused by the heat reception is extremely large.
  • the temperature increase between the open end 146 a within the sound attenuation space and the open end 145 a within the sound attenuation space can be suppressed to 2K or less.
  • the freezing performance is improved by 1.5% as compared with the conventional suction muffler specification, and the efficiency (hereafter, referred to as COP) is improved by 1.0% or more.
  • the refrigerant gas within the suction muffler 140 becomes the intermittent flow corresponding to the reciprocating motion of the piston 130 .
  • the pressure pulsation is propagated in the direction opposite to the flow of the refrigerant gas, towards the open end 145 a within the sound attenuation space, and a reflection wave is generated towards the wall 147 which is close and opposite to the open end 145 a within the sound attenuation space.
  • this embodiment uses R600a that is the natural refrigerant, the refrigerant circulation quantity is increased as compared with the case of R134a.
  • the pulsation flow of the refrigerant gas sucked into the suction muffler 140 is fast, which easily induces the noise of the high frequency. That tendency severely appears in the rotation number of a commercial power supply frequency or more.
  • the wall 147 that is close and opposite to the open end 145 a within the sound attenuation space to which the reflection wave is radiated is foam-molded, the effect of reducing the noise in the audible region is extremely higher.
  • the suction muffler 140 uses the polybutylene telephthalat that is the crystal synthetic resin, its chemical resistance is strong.
  • the resin is not substantially fused in the refrigerant and the lubricating oil 108 , which improves the reliability and enables the stable operation of the compressor.
  • the skin layer 151 where the bubble does not exist is formed in the vicinity of the surface of the wall 147 where the suction muffler 140 is foam-molded.
  • FIG. 7 is a sectional view of a suction muffler of a hermetic compressor in the second embodiment of the present invention
  • FIG. 8 is an enlarged view of a foaming portion of the suction muffler in the same embodiment.
  • FIG. 9 is a rear view of a suction muffler body in the same embodiment
  • FIG. 10 is a decomposed perspective view of the suction muffler of the hermetic compressor in the same embodiment
  • FIG. 11 is an enlarged view of a bonding section between a cover and the suction muffler body in the same embodiment.
  • FIGS. 12A to 12 C are schematic configuration views of a supercritical foam molding machine in the same embodiment.
  • the suction muffler 240 has a casing 240 C composed of a plurality of walls, a first linkage path 245 and a second linkage path 246 , and a sound attenuation space 243 is formed inside the casing 240 C.
  • the casing 240 C of the suction muffler 240 is molded by using a supercritical foam molding (which will be described later in detail), and the micro bubbles of bubble diameters of 1 to 50 ⁇ m resides in the entire wall except the portions where film thicknesses are thin.
  • the bubbles 250 generated by the supercritical foam molding process are generated at the high densities of about 10 9 to 10 15 cells/cm3.
  • the thermal insulating performance can be improved by about 20% or more.
  • bubbles 250 are formed inside the walls of the casing 240 C.
  • the surfaces on the walls of the casing 240 C are covered by the skin layer where the bubbles 250 do not exist.
  • a suction muffler body 241 constituting the main portion of the casing 240 C has: a lubricating oil supplying path 252 formed in the shape of a rib on the outer surface of the suction muffler body 241 so as to send the lubricating oil 108 ; and a lubricating oil supplying hole 253 to suck the lubricating oil into the suction muffler 240 from the lubricating oil supplying path 252 .
  • a welding protrusion 245 b is positionally matched with a hole 242 b of a suck muffler cover 242 .
  • the suction muffler body 241 and the suck muffler cover 242 are bonded by using a supersonic welding method and the like, and the suction muffler 240 is completed.
  • the suction muffler 240 is configured so as to be bonded by a body side bonding portion 254 formed around the suction muffler body 241 and a cover side bonding portion 255 formed around the suck muffler cover 242 .
  • the plate thicknesses of the body side bonding portion 254 and cover side bonding portion 255 are both designed so as to be equal to or less than the basic wall thickness of the casing 240 C of the suction muffler 240 .
  • a supercritical foam molding machine 270 used to mold the suction muffler 240 in this embodiment is provided with a raw material inserter 271 , a supercritical gas generator 274 , a fusion injector 272 , a die unit 277 and a controller (not shown) for controlling the drive of the die unit 277 and the cooling temperature, as shown in FIGS. 12A to 12 C.
  • the inactive gas such as carbon dioxide, nitrogen and the like
  • the foaming agent such as azo-compound, flon and the like
  • the raw material pellet of the polybutylene telephthalate is thrown into the raw material inserter 271 .
  • the thrown into raw material pellet is fused at a temperature of about 250° C. or more in the fusion injector 272 .
  • the carbon dioxide or nitrogen of the physical foaming agent which becomes at the supercritical state in the supercritical gas generator 274 is injected into the fusion injector 272 , and mixed as the high pressure solution with resin raw material by a screw 275 .
  • the foaming agent at the supercritical state is injected to the die unit 277 .
  • the controller adjusts the injection quantities and injection temperatures of the raw material and foaming agent, and the pressure, and the temperature of the die unit 277 and the like, and controls the temperature and pressure at the time of the molding.
  • the fusion resin is high in viscosity.
  • the flow is the fastest at the center of the plate thickness.
  • the velocity becomes slower.
  • the region where the resin does not substantially flow appears in the very vicinity of the surface of the die unit 277 .
  • the fusion resin is sharply cooled because it is adhered closely to the die unit 277 of the low temperature at the substantially static state.
  • the resin is hardened before the formation of the bubble.
  • the skin layer is formed in which the bubble does not exist substantially.
  • the carbon dioxide and nitrogen at the supercritical state melted into the resin material at the fused state are gasified in response to the change in the temperature and pressure, which enables the generation of the very micro bubbles of the diameters of 1 to 50 ⁇ m.
  • the micro bubbles are generated on all of the walls without any change in the basic design dimensions of the suction muffler 240 .
  • the thermal insulating performances of all of the walls close to the high temperature heat source such as the rear side wall of the suction muffler body 241 where the motor element 105 is located and the lubricating oil supplying path 252 is formed, the vicinity of the open end linked to the compression element 106 , the wall which is close and opposite to the open end 246 a within the sound attenuation space where the low temperature refrigerant gas sucked into the suction muffler 240 is released to the sound attenuation space 243 , and the like.
  • the heat reception of the refrigerant gas of the low temperature sucked into the suction muffler 240 can be largely decreased, thereby maintaining the density of the refrigerant gas low and increasing the mass flow quantity of the sucked refrigerant gas.
  • the drop in the loss caused by the heat reception from the refrigerant gas enables the increase in the suck efficiency.
  • the freezing performance is improved by 2.5%, and the COP is improved by 2.0% or more.
  • the usage of the supercritical foam molding technique in this embodiment enables the micro independent bubbles to be generated on all of the walls of the suction muffler 240 .
  • the usage of the supercritical foam molding technique in this embodiment enables the micro independent bubbles to be generated on all of the walls of the suction muffler 240 .
  • the body side bonding portion 254 and cover side bonding portion 255 of the suction muffler body 241 by making the wall thickness thinner than the basic wall thickness, it is possible to suppress the generation of the bubbles, suppress the vibration drop effect in the bonding portion and carry out the idea to keep the bonding strength through the vibration of the supersonic welding.
  • the wall thickness is thinner than the basic wall thickness in the body side bonding portion 254 and the cover side bonding portion 255 .
  • the wall thickness is thinner than the basic wall thickness in the body side bonding portion 254 and the cover side bonding portion 255 .
  • the noise drop effect in the audible region in association with the fast pulsation flow of the refrigerant gas in the high rotation number, and the heat reception drop effect within the suction muffler 240 in association with the low velocity flow of the refrigerant gas in the low rotation number of the 20 r/sec or less can be made higher as compared with the first embodiment.
  • FIG. 13 is a sectional view of a hermetic compressor in the third embodiment of the present invention
  • FIG. 14 is a decomposition view of a suction muffler in the same embodiment
  • FIGS. 15A to 15 C are schematic configuration views of a supercritical foam molding machine in the same embodiment.
  • the configuration of the hermetic compressor in this embodiment is the same configuration as the second embodiment, except the suction muffler. Thus, the explanation is omitted.
  • a suction muffler 340 is composed of three parts of a motor element side 341 , an anti-motor element side 342 and a center 343 . Most of the portions of their elements constitute a casing 340 C.
  • the suction muffler 340 where the three parts of the motor element side 341 , the anti-motor element side 342 and the center 343 are combined has a first linkage path 345 and a second linkage path 346 , and a sound attenuation space 347 is formed inside the casing 340 C.
  • the first linkage path 345 is formed on the bonding surface between the center 343 and the anti-motor element side 342
  • the second linkage path 346 is formed integrally with the part of the anti-motor element side 342 .
  • the suction muffler 340 is interposed between the cylinder head 136 and the valve plate 135 , and the thickness of this engaged portion is thicker than the other portions.
  • the above-mentioned configuration elements (including the casing 340 C) of the suction muffler 340 are molded by using the supercritical foam molding.
  • the supercritical foam molding which uses core-back is performed on the motor element side 341 .
  • the raw material pellet of the polybutylene telephthalate is thrown into a raw material inserter 371 .
  • the thrown into raw material pellet is fused at the temperature of about 250° C. or more in a fusion injector 372 .
  • the carbon dioxide or nitrogen of the physical foaming agent which becomes at the supercritical state in the supercritical gas generator 374 is injected into the fusion injector 372 , and mixed as the high pressure solution with the resin raw material by a screw 375 .
  • the foaming agent at the supercritical state is injected into a die unit 377 .
  • the processes until this are similar to the second embodiment.
  • the foaming agent at the supercritical state is gasified, thereby generating the bubble.
  • the thickness of the gate portion is 60% of the wall thickness and that the width is about three times the thickness.
  • the section area is approximately equal to the square of the wall thickness. As compared with the first embodiment, the area becomes wider, such as two times.
  • the section area of the gate portion is wider than the second embodiment, and the flow behavior of the resin is excellent.
  • the gas pressure of the physical foaming agent is kept high, in the situation that the bubble is small, the fused resin is filled into the cavity.
  • a part 377 a of the die unit is retreated in an arrow direction, and the core-back is executed to enlarge the space of the cavity.
  • the pressure inside the cavity is dropped, and the bubble is expanded.
  • the foaming magnification is increased to 30 to 40% that exceeds the supercritical foaming in which the core-back is not used.
  • the thermal insulating property of the casing 340 C of the suction muffler 340 can be further improved, thereby improving the performance.
  • the suction muffler 340 is separated and divided in the direction approximately vertical to the wall where the maximum projection area is obtained. Moreover, the direction where at the time of the molding, the part of the die unit is moved-to enlarge the cavity is the projection direction where the maximum projection area of the suction muffler 340 is obtained.
  • the maximum projection area implies the maximum projection area obtained when the projections from various directions are performed on the targeted member.
  • the core-back contributes to the improvement of the thermal insulating performance
  • the application to the complex part into which a pipe and the like are integrated is difficult.
  • the motor element side 341 close to the compression element 106 and the motor element 105 serving as the heat source is configured such that the relatively simple surface is main and the core-back can be effectively applied, thereby attaining the efficiency improvement.
  • the second linkage path 346 is molded integrally with the anti-motor element side 342 on the opposite side. Consequently, the number of the parts is reduced to reduce the cost.
  • the drop in the strength caused by the foaming is low as compared with the conventional foaming technique.
  • the strength is further dropped.
  • the suction muffler 340 is fixed, in the portion interposed between the valve plate 135 and the cylinder head 136 , by making the plate thickness relatively thicker, the strength can be reserved, thereby protecting the occurrence of the abnormal tone caused by the vibration of the suction muffler 340 and the leakage of the gas.
  • FIG. 16 is a decomposition view of a suction muffler of a hermetic compressor in the fourth embodiment of the present invention.
  • the configuration of the hermetic compressor in this embodiment is the same configuration as the third embodiment except the suction muffler, and the method of the supercritical foam molding is also similar. Thus, the explanation is omitted.
  • a casing 440 C of a suction muffler 440 is constituted by two parts of a suction muffler body 441 and a suction muffler cover 442 and assembled by a method of welding and the like. Also, since the suction muffler cover 442 is interposed between the cylinder head 136 and the valve plate 135 , the suction muffler 440 is fixed.
  • the suction muffler cover 442 has the sufficient strength, because the foam molding is not executed. Thus, it is possible to protect the occurrence of the abnormal tone caused by the vibration of the suction muffler 440 and the leakage of the gas.
  • the suction muffler body 441 is manufactured by the supercritical foam molding, similarly to the third embodiment. Moreover, the core-back is carried-out in the projection direction where the maximum projection area is obtained as shown by an arrow of FIG. 16 . Consequently, a plate thickness H of the wall, which occupies most of the surface area of the casing 440 C of the suction muffler 440 and is close to the motor element 105 of the high temperature and the like, is made thicker than a plate thickness I of the other walls, and the foaming magnification is made higher. Thus, the thermal insulating performance of the whole of the suction muffler 440 is improved, thereby improving the suck efficiency.
  • the hermetic compressor according to the present invention and the manufacturing method of the suction muffler can make the suck efficiency higher and also reduce the noise vibration.
  • they can be applied to the usage field, such as the air condition, the freezing refrigerating apparatus or the like.

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  • General Engineering & Computer Science (AREA)
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US10/574,858 2003-10-10 2004-10-08 Hermetic compressor and manufacturing method of suction muffler Abandoned US20070059189A1 (en)

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JP2003352032 2003-10-10
JP2003-3520321 2003-10-10
JP2004-1252321 2004-04-21
JP2004125232A JP2005133707A (ja) 2003-10-10 2004-04-21 密閉型圧縮機
PCT/JP2004/015300 WO2005035983A1 (fr) 2003-10-10 2004-10-08 Compresseur hermetique et procede de fabrication d'un silencieux d'aspiration

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EP (1) EP1671034B1 (fr)
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WO2010131061A1 (fr) * 2009-05-12 2010-11-18 JENSEN, Söby, Stefan Compresseur hermétiquement fermé et procédés associés
US20110123381A1 (en) * 2008-07-22 2011-05-26 Kangwook Lee Compressor
US20120251358A1 (en) * 2011-03-31 2012-10-04 Kabushiki Kaisha Toyota Jidoshokki Motor-driven compressor
CN111810380A (zh) * 2020-06-09 2020-10-23 珠海格力节能环保制冷技术研究中心有限公司 一种消音装置、包括其的压缩机组件及冰箱

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JP4735084B2 (ja) * 2005-07-06 2011-07-27 パナソニック株式会社 密閉型圧縮機
BRPI0611232A2 (pt) * 2005-08-04 2010-08-24 Arcelik As compressor
KR100778485B1 (ko) 2006-04-26 2007-11-21 엘지전자 주식회사 연결관 결합형 머플러 및 그를 구비한 압축기
JP4615466B2 (ja) * 2006-03-22 2011-01-19 日本トムソン株式会社 高密封シール装置を備えた直動案内ユニット
JP5034860B2 (ja) * 2007-10-22 2012-09-26 パナソニック株式会社 密閉型圧縮機
FR2939129B1 (fr) * 2008-11-28 2014-08-22 Snecma Propulsion Solide Aube de turbomachine en materiau composite et procede pour sa fabrication.
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US9181950B2 (en) * 2011-03-31 2015-11-10 Kabushiki Kaisha Toyota Jidoshokki Motor-driven compressor
CN111810380A (zh) * 2020-06-09 2020-10-23 珠海格力节能环保制冷技术研究中心有限公司 一种消音装置、包括其的压缩机组件及冰箱

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JP2005133707A (ja) 2005-05-26
KR100771755B1 (ko) 2007-10-30
EP1671034A1 (fr) 2006-06-21
DE602004010692D1 (de) 2008-01-24
DE602004010692T2 (de) 2008-12-04
EP1671034B1 (fr) 2007-12-12
WO2005035983A1 (fr) 2005-04-21
KR20060104986A (ko) 2006-10-09

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