EP0054467B1 - Hermetisch gekapselter Kühlkompressor - Google Patents

Hermetisch gekapselter Kühlkompressor Download PDF

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Publication number
EP0054467B1
EP0054467B1 EP81401913A EP81401913A EP0054467B1 EP 0054467 B1 EP0054467 B1 EP 0054467B1 EP 81401913 A EP81401913 A EP 81401913A EP 81401913 A EP81401913 A EP 81401913A EP 0054467 B1 EP0054467 B1 EP 0054467B1
Authority
EP
European Patent Office
Prior art keywords
rotor
stator
gas
turbine
compressor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP81401913A
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English (en)
French (fr)
Other versions
EP0054467A1 (de
Inventor
Jean-Louis Naud
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.)
Lunite Hermetique SA
Original Assignee
Lunite Hermetique SA
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 Lunite Hermetique SA filed Critical Lunite Hermetique SA
Priority to AT81401913T priority Critical patent/ATE18298T1/de
Publication of EP0054467A1 publication Critical patent/EP0054467A1/de
Application granted granted Critical
Publication of EP0054467B1 publication Critical patent/EP0054467B1/de
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements
    • F25B31/02—Compressor arrangements of motor-compressor units

Definitions

  • the present invention relates to a hermetic refrigeration compressor comprising at least one compression stage actuated by an electric motor.
  • An object of the present invention is to significantly increase it by providing ⁇ means for boosting and increasing the kinetic energy of the gas, these means being arranged before the compression stage of the gas proper, inside the compressor casing.
  • the refrigerant gas sucked into a compressor can sometimes contain droplets of refrigerant, so that if precautions are not taken to eliminate them, they risk damaging the cylinder head, gaskets, valves suction, etc ... which are arranged at the inlet of the compression chambers.
  • Another object of the present invention is to prevent such a danger by proceeding with the elimination of the refrigerant droplets before they arrive at the gas suction valves.
  • these hermetic compressors especially those of the household type, must be as silent as possible. It is therefore essential to reduce engine noise and that caused by the flow of refrigerant gas as much as possible. This is why another object of the invention is to reduce the noise level of these compressors.
  • Document US-A-3 288 357 describes a hermetic refrigeration compressor having a device for separating the droplets of liquid with the refrigerant gas, and means in the form of a pipe for guiding the gas towards the inlet of the compression means . In this case, it is not intended to overpress the gas before it enters, nor to reduce the noise level of the assembly.
  • Document US-A-2 963 216 describes a hermetic refrigeration compressor in which a precise path is imposed on the fluid so that the maximum amount of gas enters the compression means and thus the performance is correct. No means for separating the various particles and no means for boosting the gas are provided.
  • a hermetic refrigeration compressor comprising, inside a sealed envelope, an electric motor with a vertical axis comprising a stator, a rotor coupled to a crankshaft and driving compression means, with cylinder and piston, of a refrigerant gas, and a suction chamber delimited by a cover covering the front faces of the rotor, and communicating on the one hand by a pipe with the inlet of the compression means and on the other hand with the volume of the gas of the casing by means of a suction opening aligned with the axis of rotation of the rotor, a hot part of the stator winding being disposed in the suction chamber, concentric with the rotor, and being projecting from at the front face of the rotor, is characterized in that it comprises a centrifugal impeller, comprising fins the lower ends of which are fixed to the said front face of the rotor and the upper ends of which project from the bo upper rd of said hot part of the stator winding, and in
  • Figure 1 shows a schematic view, in vertical section, of the hermetic refrigeration compressor according to the invention.
  • FIG. 2 represents a curve of the gas pressure pulsations obtained by the turbine and the positioning of the opening of the valves when the phasing is obtained.
  • the compressor according to the invention is housed in a sealed metal casing 10.
  • the lower part intended to be fixed on a frame, is constituted by a tank and its upper part by a cover, both having a substantially semi-cylindrical shape.
  • the tank and the cover are welded together by their edges and in such a way that the envelope 10 is sealed against the refrigerant gas filling this envelope 10.
  • the electric motor consisting of a rotor 13 and a stator 19, is placed in the upper part of the casing 10, above a body 12 made of cast iron from the compressor.
  • This rotor 13 is coupled to a crankshaft 14 which is arranged in the height direction of the casing 10.
  • the latter drives in a reciprocating rectilinear movement the compression means formed by two pistons 15 and 16 which can move in cylinders 150,160 supplied by the refrigerant gas arriving at low pressure in the casing 10 by a inlet manifold 17. These pistons 15 and 16 compress the gas to bring it to high pressure.
  • crankshaft 14 and the engine have been offset with respect to the longitudinal axis of the casing 10, as shown in FIG. 1, in order to be able to accommodate a high pressure tank 18 which serves as a discharge silencer.
  • This reservoir 18 is mounted between the stator 19 of the engine and the wall of the casing 10, and it is provided with a pipe 20 for external delivery of the compressed gas.
  • a suction chamber 21 a turbine 28 disposed above the front faces 22 and 23 of the rotor 13 and the stator 19.
  • This chamber 21 is obtained by covering these faces front 22, 23 by a cover 24, of substantially cylindrical shape for example, and the lower peripheral edge 25 of which is held contiguous with that of the stator 19.
  • This chamber 21 communicates, through a suction orifice 26, with the volume of the 'casing 10, and by an internal delivery pipe 27 with the inlet of the two cylinders 150, 160 with pistons 15 and 16.
  • the refrigerant gas arriving in the casing 10 through the inlet pipe 17 is sucked through the orifice 26 in the suction chamber 21 by means of the turbine 28, then is discharged, in the state of pressurized gas in the internal delivery pipe 27 to the compression cylinders 150, 160 respectively.
  • a cylinder head cover 31 provided with pipes connected, on the one hand, to the pipe 27 and, on the other hand, to the cylinders 150 and 160 respectively, allows the successive supplies of the cylinders 150 and 160 with pressurized refrigerant gas which allows '' achieve a significant increase in compressor efficiency.
  • the turbine 28 and the carcass of the rotor 13 can be molded in a single block.
  • part of the electric winding 29 of the stator 19 exceeds the axial face 22 of the frame of the stator 19 and advances into the chamber 21 concentrically with the turbine 28.
  • the refrigerant gas arriving by the inlet tube 17 contains droplets of refrigerant, these are sucked with the gas and projected by the turbine 28 in rotation on the hot part of the electrical winding 29 surrounding the turbine 28.
  • the droplets volatilize in refrigerant gas. Consequently, there is no longer any risk of damaging the cylinder head assembly 30 placed at the inlet of the piston cylinders 15 and 16.
  • the gas set in motion by the turbine 28 scans and cools in its passage the front surfaces 22 and 23 of the rotor 13 and the stator 19.
  • a certain amount of refrigerant gas, sucked into the suction chamber 21 by the turbine 28 is pushed into the air gap 32 of the rotor 13 and of the stator 19 which contributes to cooling the surfaces facing the latter.
  • the gas leaves between the two lower front faces of the rotor 13 and the stator 19 and bypasses the ends of the winding 29 leaving the lower front face of the stator 19 to mix with the refrigerant gas arriving through the pipe. 17 of entry into the envelope 10.
  • the suction chamber 21 also acts as a silencer by reducing towards the outside the various internal noises due in particular to the circulation of the sucked gas.
  • the length of the discharge pipe 27 is, in an exemplary embodiment, determined so as to phase the gas pulsations created by the turbine 28 with paddle blades input of the compression means, that is to say at the level of the valves 1, 2; 3, 4 suction cylinders 150, 160, and the movement of these valves 1, 2; 3, 4 suction, so that at the time of opening of these valves 1, 2; 3, 4 correspond, at the level of these, gas suppression bellies.
  • the blades of the turbine 28 are integral with the movement of the piston or pistons in their cylinder.
  • the opening of the suction valves 1,2 occurs between 60 ° and 180 ° of the angle of rotation of the motor shaft, the origin of the measurement being taken at top dead center (TDC).
  • TDC top dead center
  • a corresponding angular setting of the blades of the turbine 28 creates, for an angle of rotation substantially equal to 120 °, an overpressure at the inlet of the internal delivery pipe 27.
  • the speed of rotation of the engine, the number of blades of the turbine, the desired pressure and temperature of the refrigerant gas make it possible to easily calculate the wavelength of the pulsations thus created of this gas. We can then deduce the length of the internal delivery pipe 27.
  • FIG. 2 represents, in curve (a), the pulsations (P) of the gases at the inlet of the cylinder 150, that is to say the cyclic variation of the pressure of these gases at the level of the valves 1, 2 d suction and in curve (b), the positions (H) of opening of the valves 1, 2 as a function of the angle ⁇ of rotation of the crankshaft 14.
  • the length of the internal delivery pipe 27 is determined, taking into account the length of the pipes which extend it in the cylinder head cover 31, so that the total lengths of the tubing 27 and of the pipes which extend it and lead to the inlet of one and the other cylinder 150, 160 provide a substantial value maximum gas pressure at valves 1, 2 and 3, 4 respectively.
  • This embodiment of the means used to obtain maximum overpressure at the inlet of the cylinders 150, 160 is not limiting.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Sampling And Sample Adjustment (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Claims (5)

1. Hermetisch geschlossener Kältemittelkompressor, der im Inneren einer dichten Umhüllung (10) einen Elektromotor mit senkrechter Achse umfaßt, der einen Stator (19) une einen Rotor (13) aufweist, welcher an eine Kurbelwelle (14) angekoppelt ist und Kompressionsmittel für ein Kältemittelgas antreibt, die mit Zylinder (150, 160) und Kolben (15, 16) ausgestattet sind, und eine Ansaugkammer (21) umfaßt, welche durch eine Haube (24) begrenzt ist, welche die Stirnflächen (22, 23) des Rotors (13) und des Stators (19) abdeckt und einerseits über ein Röhrchen (27) mit dem Einlaß der Kompressionsmittel in Verbindung steht sowie andererseits mit dem Gasvolumen der Umhüllung (10) in Verbindung steht über eine Ansaugöffnung (26), welche mit der Drehachse des Rotors (13) ausgerichtet ist, wobei ein warmer Teil der Wicklung (29) des Stators (19) in der Ansaugkammer (21) konzentrisch zum Rotor (13) angeordnet ist un bezüglich der Stirnfläche (22) des Rotors (13) herausragt, dadurch gekennzeichnet, daß er eine Zentrifugalturbine (28) umfaßt, die Flügel aufweist, deren untere Enden an der Stirnfläche (22) des Rotors (13) befestigt sind und deren obere Enden in bezug auf den oberen Rand des genannten warmen Teiles der Wicklung (29) des Stators (19) überstehen, und daß der Einlaß des Röhrchens (27) sich gegenüber dem Umfang der Turbine (28) befindet, gegenüber der Zone der Flügel, welche bezüglich des oberen Randes des genannten warmen Teiles der Wicklung (29) des Stators (19) übersteht.
2. Kompressor nach Anspruch 1, dadurch gekennzeichnet, daß die Ansaugkammer (21) ferner über den Eisenspalt (32) des Motors mit dem Volumen der Umhüllung (10) in Verbindung steht.
3. Kompressor nach Anspruch 1, dadurch gekennzeichnet, daß der Rotor (13) und die Turbine (28) aus einem einzigen geformten Block gebildet sind.
4. Kompressor nach Anspruch 1, dadurch gekennzeichnet, daß die Wahl der Länge des internen Auslaßröhrchens (27) es gestattet, die Gasschwingungen, welche durch die Turbine (28) am Einlaß der Kompressionsmittel erzeugt werden, und die Bewegung der Ansaugventile (1, 2), welche diesen Kompressionsmitteln zugeordnet sind, in Phase zu bringen, dergestalt, daß im Zeitpunkt des Öffnens dieser Ansaugventile (1, 2) die Gase an diesen Ventilen (1, 2) ein Überdruckmaximum aufweisen.
5. Kompressor nach Anspruch 4, dadurch gekennzeichnet, daß die Kompressionsmittel wenigstens zwei Kolben-Zylinder (150, 15; 160, 16) umfassen, und daß diese zwei Baugruppen an den Auslaß des inneren Auslaßröhrchens (27) angeschlossen sind über Strömungskanäle, welche in einem Kopfteil (31) liegen, wobei die Längen dieser Strömungskanäle derart bestimmt sind, daß die Gase ein Überdruckmaximum an den Ansaugventilen (1, 2; 3, 4) jedes entsprechenden Zylinders im Zeitpunkt des Öffnens aufweisen.
EP81401913A 1980-12-12 1981-12-02 Hermetisch gekapselter Kühlkompressor Expired EP0054467B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT81401913T ATE18298T1 (de) 1980-12-12 1981-12-02 Hermetisch gekapselter kuehlkompressor.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8026412 1980-12-12
FR8026412A FR2496241A1 (fr) 1980-12-12 1980-12-12 Compresseur frigorifique hermetique

Publications (2)

Publication Number Publication Date
EP0054467A1 EP0054467A1 (de) 1982-06-23
EP0054467B1 true EP0054467B1 (de) 1986-02-26

Family

ID=9249002

Family Applications (1)

Application Number Title Priority Date Filing Date
EP81401913A Expired EP0054467B1 (de) 1980-12-12 1981-12-02 Hermetisch gekapselter Kühlkompressor

Country Status (6)

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EP (1) EP0054467B1 (de)
AT (1) ATE18298T1 (de)
DE (1) DE3173920D1 (de)
DK (1) DK549781A (de)
ES (1) ES8301351A1 (de)
FR (1) FR2496241A1 (de)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1329658C (zh) * 2002-08-19 2007-08-01 乐金电子(天津)电器有限公司 双容量压缩机

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB652215A (en) * 1947-10-07 1951-04-18 James Harold Evans Thermo-pump heating systems

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR892138A (fr) * 1942-03-12 1944-03-29 Hermes Patentverwertungs Gmbh Machine frigorifique à compression
US2509377A (en) * 1946-03-16 1950-05-30 Trask Allen Compressor
US2963216A (en) * 1958-10-09 1960-12-06 Westinghouse Electric Corp Refrigerating apparatus
US2963218A (en) * 1959-07-03 1960-12-06 Worthington Corp Enclosed motor-compressor unit
US3075106A (en) * 1961-03-09 1963-01-22 Gen Electric Dynamoelectric machine
US3288357A (en) * 1961-08-31 1966-11-29 Copeland Refrigeration Corp Refrigeration motor-compressor
US3145914A (en) * 1962-08-03 1964-08-25 Worthington Corp Enclosed motor compressor unit
US3239132A (en) * 1964-02-03 1966-03-08 Trane Co Compressor
US3387774A (en) * 1966-11-21 1968-06-11 Copeland Refrigeration Corp Means for inhibiting noise and slugging in refrigerant compressors
US3465949A (en) * 1967-10-23 1969-09-09 Lennox Ind Inc Pressurizing arrangement for a compressor
US3462075A (en) * 1967-11-06 1969-08-19 Lennox Ind Inc Hermetic compressor construction
US3498530A (en) * 1968-02-21 1970-03-03 Tecumseh Products Co Hermetic compressor crankcase construction
US3864064A (en) * 1973-03-12 1975-02-04 Sundstrand Corp Suction muffler tube for compressor
US3876339A (en) * 1973-08-06 1975-04-08 Sundstrand Corp Reciprocating piston gas compressor
US3942912A (en) * 1974-10-04 1976-03-09 Lennox Industries Inc. Method for controlling the operation of two-speed, refrigerant motor compressors
GB1600301A (en) * 1977-02-10 1981-10-14 Copeland Corp Manufacture of refigeration motor/compressor units

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB652215A (en) * 1947-10-07 1951-04-18 James Harold Evans Thermo-pump heating systems

Also Published As

Publication number Publication date
EP0054467A1 (de) 1982-06-23
ES507898A0 (es) 1982-11-16
ATE18298T1 (de) 1986-03-15
DK549781A (da) 1982-06-13
DE3173920D1 (en) 1986-04-03
FR2496241A1 (fr) 1982-06-18
FR2496241B1 (de) 1984-06-22
ES8301351A1 (es) 1982-11-16

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