EP0561385B1 - Compresseur avec carter hermétique - Google Patents

Compresseur avec carter hermétique Download PDF

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Publication number
EP0561385B1
EP0561385B1 EP93104359A EP93104359A EP0561385B1 EP 0561385 B1 EP0561385 B1 EP 0561385B1 EP 93104359 A EP93104359 A EP 93104359A EP 93104359 A EP93104359 A EP 93104359A EP 0561385 B1 EP0561385 B1 EP 0561385B1
Authority
EP
European Patent Office
Prior art keywords
casing
compressor
lateral surface
curvature
hermetically sealed
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP93104359A
Other languages
German (de)
English (en)
Other versions
EP0561385A1 (fr
Inventor
Maurizio Bucciarelli
Fabio Giusto
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.)
ACC Compressors SpA
Original Assignee
Zanussi Elettromeccanica SpA
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Filing date
Publication date
Application filed by Zanussi Elettromeccanica SpA filed Critical Zanussi Elettromeccanica SpA
Publication of EP0561385A1 publication Critical patent/EP0561385A1/fr
Application granted granted Critical
Publication of EP0561385B1 publication Critical patent/EP0561385B1/fr
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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
    • F04B39/0033—Pulsation and noise damping means with encapsulations
    • 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
    • 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

Definitions

  • the present invention relates to a compressor, particularly for domestic refrigerating appliances, comprsing a hermetically sealed casing enclosing a motor-compressor unit of the volumetric type as defined in the preamble of claim 1.
  • Compressors of this type are well known and include a spring suspension system by means of which the motor-compressor unit is mounted within the hermetically sealed casing in a manner acting to reduce vibrations and noise generated therewithin.
  • the hermetically sealed casing performs the double function of containing a refrigerant gas which is to be compressed, and of acting as a barrier for the noise generated in its interior to thereby reduce its transmission to the ambient space.
  • the hermetically sealed casing has a substantially cylindric configuration, with a lateral surface having mounted thereon a terminal assembly or the like for the required electric connections, a partially convex bottom wall, and a cover having a partially curvilinear sectional shape which is symmetric at least in relation to a vertical center plane.
  • This configuration of the hermetically sealed casing is conducive to reconciling the mutually contradictory requirements of simplifying the construction of the compressor and of reducing the transmission of noise, particularly in the lower medium range of the audible frequencies. It is in fact known that noise in the low frequency range is particularly annoying, especially in the domestic environment.
  • an hermetic compressor housing formed from metal sheet as two housing halves is known.
  • the two halves form, when joined together, a generally ellipsoidal inner surface having a maximum radius of curvature of about one order of magnitude greater than the minimum values of curvature and deviating from the shape only when necessary for supporting the compressor motor assembly.
  • the housing inner surface is substantially symmetric about each of three mutually perpendicular axes.
  • a housing for a motor compressor having a spherical shape except for a projecting portion for encasing a protruding portion of the compressor body.
  • the central portion in the height direction has a straight line cylindrical-shape.
  • a portion connected to the straight line portion is formed of dummy spherical shape of a fixed radius ratio.
  • this object is attained in a compressor having a hermetically sealed casing as defined in claim 1.
  • the compressor according to the invention comprises a hermetically sealed metal casing 5 having walls of substantially constant thickness and composed of a casing body 6 provided with a cover 7 secured thereto in a hermetically sealing fit.
  • casing 5 encloses a motor-compressor unit of the volumetric type of a construction as described for instance in DE-A-2 835 414, mounted therein by means of a suitable spring suspension system and operable to compress a gas contained in the casing.
  • the operation of the motor-compressor unit results in the generation of noise which is transmitted to the environment through casing 5, the latter intrinsically responding in two distinct modes to the noise generated in its interior:
  • the dynamic response of the casing of a compressor of the type in question is characterized by its inherent vibration properties which may be identified in terms of modal parameters, i.e. natural frequencies, dampening coefficients, and relative deformation.
  • modal parameters i.e. natural frequencies, dampening coefficients, and relative deformation.
  • the casing should ideally be designed in such a manner that any excitation of acoustic or vibratory nature would act on the casing within the controlled range of its inertia.
  • the casing should have a considerably mass which on the other hand is necessarily subject to limitations.
  • the casing could be flexible, or at least of reduced rigidity, with natural frequencies of no more than 100 Hz and thus inaudible to the human ear, but this is obviously not possible in practice, because the casing, apart from being subjected to high pressures, is by its very nature rigid and of a limited mass.
  • the most important natural frequencies of the casing are usually comprised between 1000 Hz and 5000 Hz.
  • the important natural frequencies are the prime frequencies which manifest themselves in the range of the lower frequencies (median frequencies of the audible), characterized by a greater wavelength, which are undesirably irradiated with greater facility.
  • an ideal metal casing should have a generally spherical configuration, with two types of deformation during operation of the compressor, in the first place, the expansion and contraction type, and in the second place, deformations generated by flexional waves about the lateral surface of the casing.
  • a spherical casing would have relatively bulky dimensions and would, due to its having higher natural frequencies, insufficiently dampen the noise generated by the resonance of the assembly composed of the motor-compressor unit and the casing itself.
  • a surprising condition of equilibrium between the above described mutually contradictive requirements has been obtained by designing the casing 5 with an asymmetric configuration having at any point thereof a double curvature of different magnitude relative to two ortogonal planes intersecting at the central axis 8 of the casing, and additionally having a lateral surface 9 of a substantially cambered shape, with a substantially elliptic cross-sectional shape.
  • This configuration becomes evident from considering figs. 1 to 3 in combination.
  • the vertical curvature of the lateral surface 9 is defined by a radius considerably greater than that of the associated horizontal curvature, to result in a reduction of the horizontal dimensions of the compressor as a whole.
  • the cambered shape of the lateral surface 9 in combination with the elliptic cross-sectional shape permits the natural prime frequencies of the hermetic casing 5 to be considerably dampened.
  • this shape also permits the internal volume of the casing to be minimized (in relation to the dimensions of the enclosed motor-compressor unit), and to thus improve the dampening of the noise produced by the cavity resonance of the casing 5; in combination with the vertical curvature of the lateral surface 9, this effect permits to obtain a casing 5 the minimum natural frequency of which is particularly high and therefore much less disturbing.
  • each of these curvilinear sections comprises two lateral curvature zones 11 and 12 joined to one another by a central curvature zone 13; each of the curvature zones 11 to 13 is defined by a different radius, the central curvature zone 13 having a considerably greater radius than the other ones.
  • This characteristic permits the vertical dimension of the casing 5 to be limited, and additionally results, as has been experimentally verified, in that the prime deformation of the cover 7 advantageously has a frequency of about 100 Hz higher as compared to that of a corresponding symmetric cover (at least with respect to one of said ortogonal planes).
  • a per se known metal terminal bracket 15 for the electric connections of the compressor is secured, for instance welded, to the casing 5 at the location of a so-called antinode of the prime deformation of the casing.
  • the casing 5 is rigidified in one of its most critical zones, as a result of which, and as has been experimentally verified, the casing is devoid of inherent deformations at frequencies lower than about 2700 Hz.
  • the volumetric motor-compressor unit housed within the casing 5 is preferably mounted on spring suspension assemblies of a epr se known type, taking support on at least three pedestals 16 provided on the interior lateral surface of the casing.
  • the pedestals 16 are secured, preferably welded, to the interior lateral surface of the casing 5 adjacent respective nodal zones (i.e. zones subjected to minimum displacement) of three prime deformation areas of the casing. This is effective to minimize the transmission of vibrations and the resulting noise from the motor-compressor unit to the casing 5, and from the latter to the ambient environment.
  • the compressor with hermetically sealed casing according to the invention is of a substantially simple and highly compact construction, in which the zones of potential generation and/or transmission of noise ar minimized, and in which noises still generated and/or transmitted are advantageously of relatively high frequencies and thus much less disturbing.
  • the compressor according to the invention emits substantially reduced sonar energy, with an effective qualitative improvement of the noise still emitted.

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

Claims (5)

  1. Compresseur comprenant un groupe motocompresseur du type volumétrique monté au moyen d'ensembles de suspension à ressort à l'intérieur d'un carter métallique hermétique ayant une épaisseur de paroi pratiquement constante et composé d'un corps de carter et d'un couvercle, le carter (5) ayant en tout point une double courbure de valeur différente par rapport à deux plans verticaux orthogonaux l'un à l'autre et se coupant sur l'axe central (8) dudit carter, et ayant une surface latérale (9) de forme pratiquement cambrée,
    caractérisé en ce que ledit carter (5) a une forme asymétrique par rapport aux deux plans et que ladite surface latérale (9) a une coupe transversale pratiquement elliptique.
  2. Compresseur selon la revendication 1, caractérisé en ce que ledit couvercle (7) dudit carter hermétique (5) est configuré, par rapport auxdits plans orthogonaux, avec des sections curvilignes asymétriques respectives se raccordant à ladite surface latérale (9) du carter, chacune desdites sections curvilignes comprenant deux zones de courbure latérales (11, 12) raccordées entre elles par une zone de courbure centrale (13), chacune desdites zones de courbure (11, 12, 13) étant définie par un rayon différent, ladite zone de courbure centrale (13) ayant un rayon sensiblement plus grand que le rayon des autres zones (11, 12).
  3. Compresseur selon la revendication 1 ou la revendication 2, caractérisé en ce que ledit corps (6) dudit carter (5) a un fond complètement convexe (14) comprenant des sections curvilignes différentes par rapport auxdits plans orthogonaux, lesdites sections se raccordant directement à ladite surface latérale (9) du carter (5).
  4. Compresseur selon l'une des revendications 1 à 3, caractérisé en ce qu'il comprend en outre un support de bornes métallique pour les connexions électriques dudit compresseur, ledit support (15) étant fixé sur ledit carter (5) à l'emplacement d'un anti-noeud de la déformation par vibrations primaires du carter.
  5. Compresseur selon l'une des revendications 1 à 4, caractérisé en ce que ledit groupe motocompresseur volumétrique est monté sur des ensembles de suspension à ressorts s'appuyant sur au moins trois bases prévues sur la surface latérale intérieure dudit carter, ces bases (16) étant fixées sur la surface latérale intérieure dudit carter (5) à proximité de zones nodales respectives de trois zones de déformation par vibrations primaires dudit carter (5).
EP93104359A 1992-03-18 1993-03-17 Compresseur avec carter hermétique Expired - Lifetime EP0561385B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ITPN920012U 1992-03-18
IT92PN000012U IT229034Y1 (it) 1992-03-18 1992-03-18 Compressore con contenitore ermetico

Publications (2)

Publication Number Publication Date
EP0561385A1 EP0561385A1 (fr) 1993-09-22
EP0561385B1 true EP0561385B1 (fr) 1996-10-09

Family

ID=11394627

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93104359A Expired - Lifetime EP0561385B1 (fr) 1992-03-18 1993-03-17 Compresseur avec carter hermétique

Country Status (5)

Country Link
EP (1) EP0561385B1 (fr)
AT (1) ATE144026T1 (fr)
DE (1) DE69305207T2 (fr)
ES (1) ES2095508T3 (fr)
IT (1) IT229034Y1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT1274243B (it) * 1993-11-12 1997-07-15 Necchi Compressori Contenitore per motocompressore ermetico
JPH10318140A (ja) 1997-05-21 1998-12-02 Matsushita Refrig Co Ltd 密閉型電動圧縮機

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6027831B2 (ja) * 1979-07-13 1985-07-01 松下電器産業株式会社 密閉型電動圧縮機
US4384635A (en) * 1980-06-11 1983-05-24 Tecumseh Products Company Continuous curvature noise suppressing compressor housing

Also Published As

Publication number Publication date
ATE144026T1 (de) 1996-10-15
DE69305207T2 (de) 1997-02-20
IT229034Y1 (it) 1998-06-24
DE69305207D1 (de) 1996-11-14
EP0561385A1 (fr) 1993-09-22
ITPN920012V0 (it) 1992-03-18
ITPN920012U1 (it) 1993-09-18
ES2095508T3 (es) 1997-02-16

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