EP0105127B1 - Umlaufverdichter - Google Patents

Umlaufverdichter Download PDF

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Publication number
EP0105127B1
EP0105127B1 EP19830107665 EP83107665A EP0105127B1 EP 0105127 B1 EP0105127 B1 EP 0105127B1 EP 19830107665 EP19830107665 EP 19830107665 EP 83107665 A EP83107665 A EP 83107665A EP 0105127 B1 EP0105127 B1 EP 0105127B1
Authority
EP
European Patent Office
Prior art keywords
oil
sealed container
lubricating oil
rotary compressor
gas
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
EP19830107665
Other languages
English (en)
French (fr)
Other versions
EP0105127A1 (de
Inventor
Kazutomo Asami
Fumio Wada
Koji Ishijima
Yukata Sato
Hidehiko Yamada
Yoshitaka Oishi
Kazuhiro Nakane
Yasunobu Horiuchi
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.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
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
Priority claimed from JP15031982A external-priority patent/JPS5939991A/ja
Priority claimed from JP14847482U external-priority patent/JPS5952198U/ja
Priority claimed from JP14847382U external-priority patent/JPS5952197U/ja
Priority claimed from JP15769782U external-priority patent/JPS5962289U/ja
Priority claimed from JP17527882U external-priority patent/JPS5979574U/ja
Priority claimed from JP17527982U external-priority patent/JPS5979575U/ja
Application filed by Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Publication of EP0105127A1 publication Critical patent/EP0105127A1/de
Application granted granted Critical
Publication of EP0105127B1 publication Critical patent/EP0105127B1/de
Expired 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
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation

Definitions

  • This invention relates to a rotary compressor comprising the features of the classifying portion of claim 1, i.e. a rotary compressor of a type, in which lubricating oil is cooled by a heat-exchanger for improving the performance and re- , liability in its operation (US-A-1,967,035; US-A-2,623,365).
  • the problem underlying the present invention is to remedy the disadvantages inherent in the conventional compressors and to provide a compressor of the type mentioned above in which the lubricating oil is forwarded to a heat-exchanger in utilization of a suction exerted when the coolant gas is discharged and which, moreover, can be assembled readily and has excellent operational performance and reliability.
  • Figure 1 is a cross-sectional view of the rotary compressor according to the first embodiment of the present invention
  • Figure 2 is a perspective view of the main part of the rotary compressor according to the first embodiment of the present invention.
  • a reference numeral 1 designates a hermetically sealed container
  • numerals 2 and 3 refer respectively to an electric motor and compression elements housed in the hermetically sealed container
  • numeral 7 refers to a crank shaft to be driven by the electric motor 2, and others.
  • the above-mentioned compression elements 3 comprise a piston 8 fitted on the crank shaft, a vane (not shown in the drawing) with its one end being in contact with the piston and performing reciprocating motion, main and end bearings 5, 6 to support the above-mentioned crank shaft 7, and a cylinder 4 provided in between the two bearings.
  • the interior of this cylinder is divided by the above-mentioned vane, as is well known, into a high pressure chamber and a low pressure chamber for the coolant so that inlet and outlet of the coolant can be repeated by the eccentric rotation of the crank shaft 7.
  • the coolant gas compressed in the above- described manner passes through a discharge port 12 and a discharge valve 13 formed in and provided on the main bearing 5, and discharged into a silencing chamber 14 provided at the outside of the main bearing to the discharge side of the coolant.
  • a numeral 15 refers to a gas passage hole through the cylinder 4 between the main bearing 5 and the end bearing 6.
  • a reference numeral 16 denotes a gas discharge tube with its fixed end being inserted into this gas passage hole, the other end of the gas discharge tube being a gas discharging end portion 16a which is opened in an oil guiding tube 17, one end of which is also opened in the lubricating oil 19 sumped in the hermetically sealed container 1.
  • This oil guiding tube (or oil feeding tube) 17 is opened, at the other end thereof, in the sealed container through a heat-exchanger 18 provided at the outside thereof.
  • the discharged gas from the compression chamber is led into a lubricating oil feeding end 17a of the oil feeding tube 17 through the discharge end portion 16a of the gas discharge tube 16.
  • the lubricating oil 19 standing at the bottom part of the sealed container 1 is drawn into the oil feeding tube 17 through a gap A formed in an overlapped portion between the gas discharge tube and the oil feeding tube, is forwarded to the heat-exchanger 18 provided outside the sealed container together with an ejected gas from the gas discharge tube, and is fed back into the sealed container 1 again through a feeding end portion 17b.
  • the lubricating oil at the inner bottom part of the sealed container circulates in the oil feeding tube, while discharging heat, whereby it keeps discharging heat transmitted from the electric motor, the compression elements, and so on.
  • the temperature of the compressor as a whole inclusive of the compression elements, the lubricating oil, and so on is lowered with the consequence that not only the performance of the compressor improves due to inhibition against preheating of the intake gas, improvement in sealing against leakage of the lubricating oil, etc., but also reliability of the device such as improvement in the lubricating property, etc. becomes effectively augmented.
  • the coolant gas as drawn into from the intake tube 9 is compressed by the piston 8 which rotates eccentrically in the cylinder 4.
  • the thus compressed coolant gas passes through the outlet valve 13 provided on the main bearing 5 to be discharged into the silencing chamber 14, further passes through the gas passage hole 15 through the main and end bearings 5, 6 and the cylinder 4 therebetween, and is led into a connecting tube 20, one end of which is joined with the gas passage hole.
  • This connecting tube for leading the discharged gas is expanded its diameter in the lubricating oil 19 standing at the inner bottom part of the sealed container 1.
  • Small holes 24 for sucking the lubricating oil are formed in the vicinity of a stepped part 23 between the small diameter part 21 and the large diameter part 22 of the connecting tube 20.
  • the other end of this connecting tube 20 is led to the heat-exchanger 18 installed outside the sealed container 1 by way of the bottom part thereof, and is again connected with another connecting tube 25 which is again opened in the sealed container 1 after the heat- exchange with the outside air.
  • the compressed coolant gas which has been led into the connecting tube 20 through the gas passage hole 15 is further led to the heat-exchanger 18 provided outside the sealed container 1 together with the lubricating oil 19 which has been drawn into the connecting tube through the" small holes 24 which are opened at the stepped part of the connecting tube and for sucking the lubricating oil, and then is sent into the sealed container 1 again through the connecting tube 25 for the heat-exchanger 18. That is to say, owing to the lubricating oil 19 repeating its circulation together with the compressed coolant gas, while discharging heat therefrom, the heat generated from the electric motor 2 and the compression elements 3 is constantly kept discharged outside.
  • the temperature in the electric motor element 2, the compression elements 3, the lubricating oil 19, and so forth can be lowered, whereby the temperature of the compressor as a whole can be decreased.
  • the performance of the compressor improves due to inhibition against preheating of the intake gas, improvement in sealing against leakage of the lubricating oil, improvement in the operating efficiency of the motor, and so forth, and the reliability of the compressor also improves due to inhibition against deterioration of the insulating material for the electric motor.
  • the coolant gas which has been drawn in from the intake tube 9 and compressed passes through the discharge port 12 and the discharge valve 13 formed in and provided on the main bearing 5, and discharged into the silencing chamber 14 at the discharge side, after which it further passes through the gas passage hole 15 through the main and end bearings 5, 6 and the cylinder 4 therebetween, and then is led into the gas discharge tube 16, the fixed end of which is inserted into the gas passage hole.
  • a reference numeral 30 designates an oil feeding tube, one end of which is opened to the collecting section for the lubricating oil 19 in the above-mentioned sealed container 1; a numeral 31 refers to the heat-exchanger for cooling the lubricating oil, which is provided outside the sealed container; and a numeral 32 denotes the connecting tube which is opened to the side wall of the sealed container 1 so as to be communicating with the upper space of the cylinder 4.
  • This connecting tube is connected in series with the heat-exchanger 31 and the oil feeding tube 30, the other end of the above-mentioned gas discharging tube 16 being opened into this oil feeding tube 30.
  • the compressed coolant gas from the compression chamber is discharged into the oil feeding tube 30 from the end part of the gas discharge tube 16.
  • the lubricating oil standing at the bottom part of the sealed container 1 is sucked into the oil feeding tube 30 through a gap 33 formed in the overlapped section between the discharge tube 16 and the oil feeding tube 30, which passes through the heat-exchanger 31 provided outside the sealed container 1, and is again sent into the sealed container.
  • the third embodiment of the present invention causes the lubricating oil to circulate, while discharging heat through the heat-exchanger.
  • the temperature in the compression elements, the electric motor element, further the lubricating oil, and so forth becomes lowered, hence the temperature of the compressor as a whole can be decreased, and also the performance of the compressor can be improved due to inhibition against preheating of the intake gas, improvement in sealing against leakage of the lubricating oil, improvement in working efficiency of the electric motor, and others.
  • reliability of the compressor can be remarkably improved as the result of improvement in the lubricating performance, inhibition against deterioration in the insulating material for the electric motor elements, and so forth.
  • the internal space of the compressor can be reduced, which contributes to realizing reduction in size of the compressor.
  • a reference numeral 41 designates the sealed container; numerals 42, 43 respectively refer to the electric motor section and the compression elements housed in the sealed container; and a numeral 47 refers to the crank shaft to be driven by the electric motor section 42, etc., which is disposed in the horizontal direction.
  • the compression elements 43 comprise the piston 48 fitted onto the crank shaft, the vane (not shown in the drawing) with its one end being in contact with the piston, and which performs its reciprocating motion, the main and end bearings 45, 46 to support the crank shaft 47, and the cylinder 43 positioned between the two bearings.
  • the interior of this cylinder is divided, as is well known, by the above-mentioned vane into the high pressure chamber and the low pressure chamber so that the inlet and outlet of the coolant may be repeated by the eccentric rotation of the crank shaft 47.
  • the coolant gas which has been compressed in the above-mentioned manner passes through the discharging valve 53 provided on the main bearing 45, and is discharged into the silencing chamber 54 at its discharge side provided outside the main bearing 45.
  • a reference numeral 55 denotes the gas passage hole through the main and end bearings 45, 46 and the cylinder 43 disposed between them.
  • a reference numeral 56 designates a communicating port which is formed through in such a manner that one end of it is open to the lower surface of the cylinder 43, and the other end thereof is open at a position away from the open end 55a of the gas passage hole which is open to the above-mentioned end bearing 46.
  • This communicating port has a large diameter section 57 in the vicinity of the lower end of the cylinder where its diameter is expanded.
  • a reference numeral 58 indicates an ejecting pipe with its one end being inserted into this communicating port and with its other end being opened in the large diameter section 57 contiguous to the sealed container 41. This ejecting pipe forms a space gap between its outer periphery and the large diameter section.
  • a numeral 59 refers to an oil inducing path which passes through the cylinder 43 interior so as to be opposed to the side surface of the ejecting pipe 58. This oil inducing path is opened in the lubricating oil 60 standing at the inner bottom part of the sealed container 41.
  • a reference numeral 61 designates an oil feeding pipe, one end of which is connected with a bar ring 62 opened to the lower surface wall of the sealed container 41 in opposition to the above-mentioned large diameter section 57, and the other end of which is connected with the oil feeding path 63 provided in the cylinder 43 passing through the upper surface wall of the sealed container 41.
  • a numeral 64 refers to the heat-exchanger which is connected intermediate of the oil feeding pipe, and provided outside the sealed container.
  • a numeral 65 refers to an oil sump vessel substantially cup-shaped having an oil sump section between the end surfaces of the end bearing 46.
  • the oil sump vessel has a flange portion 65a to fit on the outer surface of the end bearing 46, and forms a gas flow path 66 by bulging out the above-mentioned flange portion 65a in a manner as to connecting the open end of the gas passage hole 55a in the end bearing 46 and the open end 56a of the communicating port. Moreover, these oil sump vessel 65 and the oil feeding path 63 are connected by the oil feeding pipe 61.
  • a reference numeral 67 denotes an oil feeding port passing concentrically through the above-mentioned crank shaft 47. By this oil feeding port, oil is fed to the sliding parts through a branch port 67a.
  • the discharged gas from the compression chamber passes through the silencing chamber 54 at the discharge side thereof and the gas passage hole 55, and is led into the ejecting pipe 58 in the communicating port through the gas flow path formed in the above-mentioned oil sump vessel 65.
  • the gas ejected at the large diameter section 57 is forwarded to the heat-exchanger 64 outside the sealed container together with oil drawn into the large diameter section through the space gap formed between the ejecting pipe and the large diameter section to be cooled, after which it is returned to the sealed container 41, wherein the oil is sent to the oil sump vessel 65 through the oil guiding path 63 and the oil feeding pipe 61, after which it is distributed to every sliding part, while the coolant gas is discharged into the sealed container 41 from the end surface of the crank shaft 47 at the side of the electric motor.
  • the lubricating oil at the inner bottom part of the sealed container circulates, while discharging heat, whereby it continues to discharge heat to be transmitted from the electric motor section, the compression elements, and others.
  • the temperature of the compression elements, the lubricating oil, etc. hence the temperature of the compressor as a whole, is lowered.
  • the performance of the compressor improves due to inhibition against preheating of the intake gas, improvements in the sealing property of the lubricating oil, etc., but also the effect to reliability of the operation of the device such as improvement in the lubricating performance, etc is also great.
  • a reference numeral 70 designates the gas passage hole which passes through the main bearing 45 at a position close to the discharge valve 53 and through the cylinder 44 in a shape of a letter "L", and is opened toward the lower surface of the cylinder in its radial-direction.
  • This gas passage hole is joined with the communicating port 71 of a large diameter.
  • a reference numeral 72 denotes the ejecting pipe with its one end being press-fitted into the small diameter part of the communicating port. The other end of this ejecting pipe 72 is opened in the large diameter part of the communicating port 71 in the neighborhood of the entrance into the heat-exchanger installed outside the sealed container.
  • a numeral 73 refers to the oil inducing path opened in the cylinder immersed in the lubricating oil 60 at the bottom part of the sealed container so as to intersect orthogonally with the large diameter part of the communicating port 71. This oil inducing path is communicatively connected with the space gap 74 between the inner diameter part of the communicating port 71 and the outer .diameter part of the ejecting pipe 72.
  • the external heat-exchanger 64 for cooling the lubricating oil is connected with the large diameter part of the communicating port 71 at the outer peripheral part of the cylinder through the pipe 75.
  • the other end of the heat-exchanger 64 is communicatively connected with the substantially cup-shaped oil sump vessel 77 which has been press-fitted on the outer periphery of the flanged part of the end bearing 46 through the oil guiding pipe 76 passing through the sealed container 41, whereby the lubricating oil in this oil sump vessel is distributed to each of the sliding parts through the oil feeding ports (not shown in the drawing) opened in the above-mentioned crank shaft 47. Further, the outer peripheral part of this oil sump vessel is press-fitted in and fixed on the flange portion of the end bearing 46.
  • the discharged coolant gas from the compression chamber passes through the silencing chamber 54 at the discharge side and the gas passage hole 70, and is ejected from the above-mentioned ejecting pipe 72 within the entrance portion of the heat-exchanger, i.e., within the large diameter portion of the communicating port 71. Then, it is sent into the heat-exchanger 64 provided outside the sealed container together with the lubricating oil 60 drawn thereinto through the space gap 74 at the overlapped portion between the inner diameter portion of the communicating port 71 and the outer diameter portion of the ejecting pipe 72. After the heat- exchange, the gas is sent back into the sealed container again.
  • the lubricating oil is sent back into the above-mentioned substantially cup-shaped oil sump vessel 77 through the oil guiding pipe 76 in the sealed container. After this, the lubricating oil is distributed to each of the sliding parts, while the coolant gas is discharged into the sealed container from the end surface of the crank shaft 47 at the side of the electric motor.
  • the lubricating oil at the inner bottom part of the sealed container circulates, while discharging heat, whereby it continues to discharge heat to be transmitted from the electric motor section, the compression elements, and others.
  • the temperature of the compressor as a whole including the compression elements, the lubricating oil, and so on is lowered, not only the performance of the compressor improves due to inhibition against preheating of the intake gas, improvement in the sealing property against leakage of the lubricating oil, and so forth, but also the effect to reliability of the compressor such as improvement in the lubricating performance, etc. is also great.
  • the compressor can be installed either in the horizontal direction or in the vertical direction, whereby the best mode of its use with good space saving installation can be expected.
  • This embodiment of the present invention is concerned with improvement in the construction shown in Figure 2, wherein the coolant gas discharged at the side of the main bearing 5 passes through the main bearing 5, the cylinder 4, and the end bearing 6 to reach the discharging tube 83 to decrease the pressure loss to occur among these parts and to increase the operational efficiency of the compressor which has once been lowered by the pressure loss, and, at the same time, since the oil guiding pipe 17 is positioned at the bottom part of the sealed container 1, a difference in height between the oil guiding pipe 17 and the oil feeding end 17b is large with the consequence that the lubricating oil gathers in the oil guiding pipe 17 to thereby prevent the discharged coolant gas from flowing back into the lubricating oil 19 from the oil guiding pipe 17.
  • a reference numeral 80 designates the discharge valve which is provided at the side of the end bearing (cylinder head) 6, and the discharge silencer 81 is mounted at the side of the cylinder head 6, i.e., at the lower surface side of the cylinder 4.
  • a numeral 82 refers to an intromitting port for the oil feeding pipe, which is formed in the lower side surface of the hermetically sealed container 1 where the lubricating oil 19 gathers.
  • the manner of insertion is such that, after the compression elements 3 and the electric motor element 2 have been inserted into the hermetically sealed container 1, a connecting tube 83 which has previously been set in the oil guiding pipe 17 is inserted into the bar ring hole 84 formed in the discharge silencer 81 from the oil guiding pipe intromitting port 82.
  • the diameter of the bar ring hole 84 and that of the connecting tube 83 to be inserted into this bar ring hole is substantially same, so that they are tightly fitted and sealed by insertion into the other.
  • the pipe 17 is hermetically fusion-bonded by soldering to the oil guiding pipe intromitting port.
  • the sixth embodiment of the present invention is so constructed that the oil guiding pipe 17 is directly inserted into the discharge silencer 81, the pressure loss at the connecting hole becomes eliminated in comparison with the case of the Figure 2 embodiment.
  • the coolant gas is taken out from the side surface of the hermetically sealed container, a difference in height between the oil feeding port and the oil returning port can be reduced.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Claims (10)

1. Umlaufverdichter mit
(a) einer Verdichtungskammer, die durch Abschliessen der beiden Enden eines Zylinders mittels eines Hauptlagers (5; 45) und eines Endlagers (6; 46) gebildet ist;
(b) Verdichtungselementen (4; 43) mit einem Zylinder und einem Kolben (8; 48), der mittels einer Kurbelwelle (7; 47) exzentrisch in der Verdichtungskammer gedreht wird und die Verdichtungskammer in eine Hochdruckkammer und. eine Niederdruckkammer unterteilt; und
(c) einem dichten Gehäuse (1; 41) zur Schaffung einer Plenumkammer, in welcher die Verdichtungselemente (3; 43) untergebracht sind und Schmieröl in einem Ölsumpf im Boden des Gehäuses zum Bewirken einer Schmierung der gleitenden Teile der Verdichtungselemente steht,
(d) wobei das Schmieröl in das Gehäuse (1; 41) nach Kühlung in einem Wärmeaustauscher (18; 31; 64) außerhalb des dichten Gehäuses (1) zurückgeführt wird,

dadurch gekennzeichnet, daß
(e) das Schmieröl aus dem Ölsumpf mittels Saugwirkung gefördert wird, welche durch verdichtetes Kälte- bzw. Kühlmittelgas erzeugt wird, das aus der Verdichtungskammer ausgestoßen wird, und
(f) das verdichtete Kühlmittelgas zusammen mit dem Schmieröl durch den Wärmeaustauscher (18; 31; 64) gefördert wird.
2. Umlaufverdichter nach Anspruch 1, dadurch gekennzeichnet, daß ein Ölspeiseendabschnitt (17a) eines Ölspeiserohrs (17) zum Wärmeaustauscher (18) in das Schmieröl in dem dichten Gehäuse mündet und daß abgeführtes Gas aus der Verdichtungskammer in den offenen Ölspeiseendabschnitt (17a) ausgestoßen wird.
3. Umlaufverdichter nach Anspruch 2, dadurch gekennzeichnet, daß ein Auslaßendabschnitt (16a) eines Gasauslaßrohrs (16) passend in das Ölspeiserohr (17) eingesetzt ist, welches in das Schmieröl im dichten Gehäuse mündet, und daß ein Öleinführspalt zwischen dem Ölspeiserohr (17) und dem Gasauslaßrohr (16) gebildet ist.
4. Umlaufverdichter nach Anspruch 1, dadurch gekennzeichnet, daß ein Ölspeiserohr (20), welches aus der Verdichtungskammer ausgestoßenes Gas fördert, einen Abschnitt (22) mit aufgeweitetem Durchmesser aufweist, der in das Schmieröl im Ölsumpf des abgedichteten Gehäuses ragt, daß mindestens ein enges Loch (24) benachbart einem abgesetzten Abschnitt (23) zwischen dem Abschnitt (22) mit aufgeweitetem Durchmesser und einem Abschnitt (21) kleinen Durchmessers des Ölspeiserohrs (20) ausgebildet ist, und daß das Schmieröl durch das enge Loch angesaugt und zu einem Passieren des Wärmeaustauschers (18) außerhalb des dichten Gehäuses zusammen mit dem ausgestoßenen Kühlmittelgas veranlaßt und anschließend wieder in das dichte Gehäuse (1) zurückgeführt wird.
5. Umlaufverdichter nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß das eine Ende eines zum Wärmeaustauscher führenden Ölspeiserohrs (30) in das Schmieröl in dem dichten Gehäuse (1) mündet und daß das Auslaßrohr (16) für das verdichtete Gas in das Ölspeiserohr außerhalb des dichten Gehäuses eingeführt ist und durch Ausstoßen des verdichteten Gases das Schmieröl zu einem Passieren des Wärmeaustauschers (31) und Rückströmen in das dichte Gehäuse veranlaßt wird.
6. Umlaufverdichter nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß er entweder in vertikaler oder in horizontaler Richtung eingebaut ist.
7. Umlaufverdichter nach Anspruch 1, dadurch gekennzeichnet, daß er horizontal angeordnet ist, daß ein Verbindungskanal (56) im Zylinder (43) zum Fördern von aus der Verdichtungskammer ausgestoßenem Gas vorgesehen ist, daß ein Abschnitt (57) großen Durchmessers des Verbindungskanals (56) in das Schmieröl mündet; daß ein Ende eines Ejektorrohres (58) in den Verbindungskanal eingesetzt ist und sich in dessen Abschnitt (57) großen Durchmessers öffnet; daß ein Öleinführkanal (59) den Abschnitt (57) großen Durchmessers orthogonal schneidet und durch den Zylinder hindurchgeht und daß das Schmieröl über den Öleinführkanal (59) angesaugt und zum Passieren des außerhalb des dichten Gehäuses angeordneten Wärmetauschers (64) zusammen mit dem ausgestoßenen Gas und zum Rückströmen in das dichte Gehäuse veranlaßt wird.
8. Umlaufverdichter nach Anspruch 7, dadurch gekennzeichnet, daß ein Ölsumpfgefäß (65) mit einem Ölsumpfabschnitt zwischen dem dichten Gehäuse (41) und der Endfläche des Endlagers (46) am Endlager montiert ist, und daß eine Flanschfläche des Ölsumpfgefäßes welche das Endlager überlappt, ausgewölbt ist, um einen Gasströmungsweg (66) zu bilden.
9. Umlaufverdichter nach einem der Ansprüche 1 bis 8, dadurch gekennzeichnet, daß ein im wesentlichen becherförmig gestaltetes Ölsumpfgefäß (65; 77) zum Sammeln des Schmieröls nach dessen Kühlung vorgesehen ist, und daß der äußere Umfangsabschnitt des Ölsumpfgefäßes auf den Flanschabschnitt des Endlagers (46) aufgepreßt ist.
10. Umlaufverdichter nach Anspruch 1, dadurch gekennzeichnet, daß in einem dichten Gehäuse (1) ein Elektromotor und von dem Elektromotor getriebene Verdichterelemente (3) untergebracht sind, daß ein Auslaßventil (80) auf der Seite eines Zylinderkopfes unterhalb eines Zylinders (4) vorgesehen ist, daß ein Auslaßgeräuschdämpfer (81) zum Bilden einer Auslaßkammer am Zylinderkopf angeordnet ist, und daß ein Verbindungsrohr (83), dessen eines Ende in ein Ölspeiserohr (17), welches an der unteren Seitenfläche des dichten Gehäuses (1) in den Ölsumpf mündet, mit dem Auslaßgeräuschdämpfer (81) kommunizierend verbunden ist.
EP19830107665 1982-08-30 1983-08-04 Umlaufverdichter Expired EP0105127B1 (de)

Applications Claiming Priority (12)

Application Number Priority Date Filing Date Title
JP150319/82 1982-08-30
JP15031982A JPS5939991A (ja) 1982-08-30 1982-08-30 回転式圧縮機
JP14847482U JPS5952198U (ja) 1982-09-30 1982-09-30 横置形回転式圧縮機
JP14847382U JPS5952197U (ja) 1982-09-30 1982-09-30 回転式圧縮機
JP148473/82 1982-09-30
JP148474/82 1982-09-30
JP15769782U JPS5962289U (ja) 1982-10-19 1982-10-19 回転式圧縮機の潤滑油冷却装置
JP157697/82 1982-10-19
JP17527882U JPS5979574U (ja) 1982-11-19 1982-11-19 回転式圧縮機
JP175278/82 1982-11-19
JP17527982U JPS5979575U (ja) 1982-11-19 1982-11-19 密閉形回転式圧縮機
JP175279/82 1982-11-19

Publications (2)

Publication Number Publication Date
EP0105127A1 EP0105127A1 (de) 1984-04-11
EP0105127B1 true EP0105127B1 (de) 1987-06-16

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Application Number Title Priority Date Filing Date
EP19830107665 Expired EP0105127B1 (de) 1982-08-30 1983-08-04 Umlaufverdichter

Country Status (5)

Country Link
EP (1) EP0105127B1 (de)
AU (1) AU548548B2 (de)
DE (1) DE3372117D1 (de)
DK (1) DK156672C (de)
MX (2) MX153949A (de)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS618492A (ja) * 1984-06-25 1986-01-16 Mitsubishi Electric Corp 回転式圧縮機
JPS61210285A (ja) * 1985-03-14 1986-09-18 Toshiba Corp 回転式圧縮機
AU585439B2 (en) * 1987-04-14 1989-06-15 Mitsubishi Denki Kabushiki Kaisha Rotary compressor
CN114017334B (zh) * 2021-11-08 2023-09-05 广东美芝制冷设备有限公司 旋转压缩机及具有其的制冷设备

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Publication number Priority date Publication date Assignee Title
GB382227A (en) * 1931-05-15 1932-10-20 Bosch Robert Improvements in or relating to refrigerating machines
US1967035A (en) * 1933-05-08 1934-07-17 Lipman Patents Corp Motor compressor unit
US2178425A (en) * 1937-02-18 1939-10-31 Gen Electric Refrigerating machine
US2623365A (en) * 1947-07-14 1952-12-30 Leonard J Daniel Refrigerator pump

Also Published As

Publication number Publication date
DK389183D0 (da) 1983-08-25
DK389183A (da) 1984-03-01
DK156672B (da) 1989-09-18
DK156672C (da) 1990-02-12
DE3372117D1 (en) 1987-07-23
AU1760783A (en) 1984-03-08
EP0105127A1 (de) 1984-04-11
MX158883A (es) 1989-03-29
AU548548B2 (en) 1985-12-19
MX153949A (es) 1987-02-24

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