EP0210349B1 - Encapsulated rolling-piston compressor - Google Patents

Encapsulated rolling-piston compressor Download PDF

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Publication number
EP0210349B1
EP0210349B1 EP86105874A EP86105874A EP0210349B1 EP 0210349 B1 EP0210349 B1 EP 0210349B1 EP 86105874 A EP86105874 A EP 86105874A EP 86105874 A EP86105874 A EP 86105874A EP 0210349 B1 EP0210349 B1 EP 0210349B1
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EP
European Patent Office
Prior art keywords
oil
rotary piston
piston compressor
crankshaft
nozzle
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
EP86105874A
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German (de)
French (fr)
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EP0210349A2 (en
EP0210349A3 (en
Inventor
Bernd Dr. Gromoll
Peter Gulden
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Siemens AG
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Siemens AG
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Publication of EP0210349A3 publication Critical patent/EP0210349A3/en
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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
    • F04C29/023—Lubricant distribution through a hollow driving shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M11/00—Component parts, details or accessories, not provided for in, or of interest apart from, groups F01M1/00 - F01M9/00
    • F01M11/06—Means for keeping lubricant level constant or for accommodating movement or position of machines or engines
    • F01M11/062—Accommodating movement or position of machines or engines, e.g. dry sumps
    • F01M11/065—Position
    • 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
    • F25B31/002—Lubrication

Definitions

  • the invention relates to a hermetically sealed oil-lubricated rotary piston compressor with a horizontally arranged, at least partially hollow crankshaft, in which the lubricating oil is sucked out of the oil sump by a dynamic vacuum generated in the compressed gas line and together with the compressed gas in the hollow part of the crankshaft, which is inside of the cylinder housing has radial bores for supplying oil to the mutually movable surfaces of the compressor.
  • Hermetically sealed, oil-lubricated rotary piston compressors with a horizontally arranged crankshaft are used because of their compact design in devices such as household refrigerators and air conditioning systems where the space required for installing a compressor should be as small as possible. Since the crankshaft is no longer immersed in the oil sump accumulated at the bottom of the housing, additional measures are required for the oil supply to the rotating parts of this compressor, in contrast to a rotary piston compressor with a vertical axis.
  • arrangements are also known in which the lubricating oil is sucked into the interior of the crankshaft by a negative pressure generated in the flowing compressed gas.
  • a hermetically sealed, oil-lubricated rotary piston compressor with a horizontally arranged hollow crankshaft is known (US Pat. No. 4,391,573), in which the lubricating oil is conveyed by the compressed gas discharged from the compressor into the hollow crankshaft, which is provided with radial bores within the cylinder housing through which the lubricating oil reaches the opposite movable surfaces of the compressor for lubrication and sealing.
  • the compressed gas expelled by the eccentric rotational movement of the rolling piston from the pressure chamber of the compressor via an outlet opening is guided to the end of the hollow crankshaft, which is remote from the drive side, via a line system located outside the cylinder housing, which is firmly connected to the cylinder housing.
  • Part of this line system consists of a horizontal outlet pipe which runs in the oil sump and is provided with an opening into which a vertical suction pipe opens.
  • the upper end of this suction pipe protrudes into the outlet pipe and has a bevelled opening and in this way forms a cross-sectional constriction in the outlet pipe.
  • the invention is therefore based on the object of specifying a hermetically encapsulated oil-lubricated rotary piston compressor in which the oil supply is maintained in each position by any rotation of the compressor about the horizontal axis of its crankshaft or a position parallel to it.
  • the cross-sectional constriction in the compressed gas line is a rotationally symmetrical nozzle which is interchangeably inserted in the compressed gas line.
  • the nozzle is preferably inserted coaxially to the crankshaft and is located outside the oil sump.
  • the nozzle opens into a mixing chamber in such a way that there is a suction chamber between the nozzle and the wall of the mixing chamber, which is connected to the oil suction nozzle via bores.
  • a diffuser is connected to the mixing room, in which a low-loss conversion of speed into pressure takes place.
  • the bearing of the oil suction nozzle has the shape of a spherical bearing and the oil suction nozzle can additionally perform a rotary movement about an axis perpendicular to the axis of the crankshaft within a predetermined angular range.
  • an electric motor 4 with a hollow, horizontally is attached arranged motor shaft 6 arranged in a compressor housing 2.
  • the compressor and housing are partially shown in section.
  • the motor shaft 6 also forms the likewise hollow crankshaft 6 of the rotary piston compressor 8, the cylinder housing 82 of which is firmly connected to the compressor housing 2 and is provided with an oil suction device 10.
  • This contains an oil intake 60 which is rotatably mounted about the horizontal axis 200 of the hollow crankshaft 6 and which is immersed in an oil sump 12.
  • Bushings 70 for the electrical connections of the electric motor 4 and mounting brackets 80 are located on the compressor housing 2.
  • the gas drawn in through an inlet connection 14 is compressed in the rotary piston compressor 8 and directed into the oil suction device 10 via a compressed gas line located in the cylinder housing 82. There the oil is sucked in and the compressed gas / oil mixture reaches the hollow crankshaft 6. The oil reaches the mutually movable surfaces of the compressor for lubrication and sealing through radial bores in the hollow crankshaft 6. The compressed gas emerges together with the excess oil at the engine-side end 132 of the hollow crankshaft 6. The excess oil is thrown against the compressor housing wall 16 and flows back from there to the oil sump 12.
  • the compressed gas is passed on via an outlet connection 18, which is attached to the compressor housing 2 opposite the engine-side end 132 of the hollow crankshaft 6, to a condenser, not shown in the figure.
  • the oil suction device 10 is further illustrated in FIG.
  • the rotary piston compressor 8 contains a rotary piston 20 which rotates eccentrically in the cylinder housing 82.
  • a separating slide 80 which is movably attached to the cylinder housing 82 by means of a spring, divides the space located between the cylinder housing 82 and the rotary piston 20 into a pressure chamber and a suction chamber.
  • the gas compressed by the revolving rolling piston 20 in the pressure chamber is expelled via a pressure valve 22 and conducted via a first deflection chamber 24 and a compressed gas line 26 to the open end 130 of the hollow crankshaft 6 facing away from the drive.
  • a part 262 of the compressed gas line is located in the cylinder housing 82.
  • a deflecting body 50 is fixedly connected to the cylinder housing 82 via a sealing ring 40.
  • the compressed gas is guided in the deflection body 50 through a gas line 264 to a second deflection chamber 266 and is directed there into the nozzle 104.
  • the nozzle 104 is designed as a rotating body and, in an advantageous embodiment, can form a replaceable component inserted into the deflecting body 50.
  • the nozzle 104 opens into a likewise rotationally symmetrical mixing space 110, which is adjoined by a diffuser 106, in which the speed energy is converted back into pressure energy with little loss.
  • the plane of the outlet opening 1042 of the nozzle 104, the outer wall of the nozzle 104 and part of the inner wall of the mixing space 110 form the boundary surfaces of a suction space 108.
  • Bores 112 which run radially to the axis 200 and serve to remove pressure open into this suction space 108.
  • These bores 112 start from a groove 114 with a rectangular cross section, which surrounds the deflecting body 50 in an annular manner on its outer wall.
  • the groove 114 is surrounded by a hollow shaft which bears against the outer wall of the deflecting body 50 and can be rotated about the axis 200 and which serves as a bearing 62 for the oil suction nozzle 60.
  • A, for example, cylindrical connecting piece 64 is attached to the outer surface of the bearing 62, the cylinder axis of which extends perpendicular to the axis 200.
  • the cylindrical socket 64 is hollow on the inside and its bore opens into the annular groove 114.
  • the bearing 62 and the hollow cylindrical socket 64 form the rotatably mounted oil suction socket 60.
  • the center of gravity S of the oil suction socket 60 is located outside the axis 200 in the socket 64.
  • the opening 642 and the center of gravity S of the oil suction nozzle are located such that the extension of their connecting line L intersects the axis 200 at an intersection point P.
  • the nozzle-shaped cross-sectional constriction of the nozzle 104 in the compressed gas line 26 thus creates a negative pressure in the suction chamber 108 compared to the oil chamber 120.
  • the lubricating oil is sucked through the cylindrical nozzle 64 to the pressure tapping holes 112 and from there reaches the suction chamber 108 and mixes in the mixing chamber 110 with the pressurized gas and is then conveyed as a pressurized gas / oil mixture into the diffuser 106 and from there into the hollow crankshaft 6.
  • the hollow crankshaft 6 there are oil supply bores 140 through which the oil is angled for lubrication and sealing to the walls of the parts of the rotary piston compressor 8 which are movable relative to one another.
  • FIG. 3 shows the oil suction nozzle 60 in a position in which the cylindrical nozzle 64 is not aligned parallel to the gravitational field or to an inertial field caused by rotation of the rotary piston compressor around the axis 200 or an axis parallel to it.
  • Gravity or inertial force F which generates a torque M about axis 200, acts on the oil suction port. Due to the torque M, the suction port 64 is aligned at least approximately parallel to the gravity or inertia field. Its opening 642 is thus always in the equilibrium position in the oil sump 12.
  • the nozzle 68 of the oil suction nozzle 60 has approximately the shape of a circular disk sector.
  • the distance of the center of gravity S to the axis 200 and that Torque M generated by the gravity or inertia force is accordingly increased compared to the embodiment of a cylindrical connecting piece.
  • the pressure valve 22 is accommodated in that part of the cylinder housing 82 which faces away from the drive.
  • the compressed gas reaches the deflection chamber 266 directly via the compressed gas line 26.
  • the crankshaft 6 is hollow only within the cylinder housing 82 and is provided with radial bores 140 there.
  • the diffuser 106 connects to one open end of the crankshaft 6 and is connected to the oil space 120 by means of radial outlet bores 34.
  • the pressurized gas-oil mixture flows from the diffuser 106 into the oil chamber 120 and from there, for example, through bores in the rotor of the electric motor 4, not shown in the drawing, which run parallel to the crankshaft to the outlet port 18. This simultaneously cools the electric motor 4.
  • a part 54 of the outer surface of the deflecting body 50 is formed by the outer surface of a spherical zone and is surrounded by a groove 116 in a ring.
  • the cross-sectional area of the groove 116 is, for example, an annular sector.
  • the groove 116 is connected to the suction chamber 108 by means of bores 112 running perpendicular to the axis 200.
  • the groove 116 is surrounded by a spherical bearing 66 of the oil suction nozzle 60 resting on the part 52 of the outer surface of the deflecting body 50.
  • the spherical bearing 66 can also be provided on its inner surface with an annular circumferential groove 118, into which the bore of a, for example, cylindrical connecting piece 64 opens.
  • This construction ensures that the oil suction nozzle 60 can still be freely rotated about the axis 200 by the force of gravity or inertia if it is inclined within a predetermined angular range a against the surface of the oil sump 12. In the case of cylindrical bearing surfaces with such inclinations, there is the possibility that the oil suction nozzle 60 is tilted and prevented from rotating.
  • Another advantage of the dome-shaped mounting of the oil suction nozzle 60 is that the angle of inclination ⁇ of the crankshaft 6 against the surface of the oil sump 12, up to which the opening 642 of the nozzle 6 is still in the oil sump 12, compared to the embodiment with a cylindrical bearing surface of the oil suction port 60 is enlarged.

Description

Die Erfindung bezieht sich auf einen hermetisch gekapselten ölgeschmierten Rollkolbenverdichter mit waagrecht angeordneter, wenigstens teilweise hohler Kurbelwelle, bei dem das Schmieröl durch einen in der Druckgasieitung erzeugten dynamischen Unterdruck aus dem Ölsumpf angesaugt wird und zusammen mit dem Druckgas in den hohlen Teil der Kurbelwelle, die innerhalb des Zylindergehäuses radiale Bohrungen zur Ölversorgung der gegeneinander beweglichen Oberflächen des Verdichers aufweist, befördert wird.The invention relates to a hermetically sealed oil-lubricated rotary piston compressor with a horizontally arranged, at least partially hollow crankshaft, in which the lubricating oil is sucked out of the oil sump by a dynamic vacuum generated in the compressed gas line and together with the compressed gas in the hollow part of the crankshaft, which is inside of the cylinder housing has radial bores for supplying oil to the mutually movable surfaces of the compressor.

Hermetisch gekapselte, ölgeschmierte Rollkolbenverdichter mit waagerecht angeordneter Kurbelwelle werden wegen ihrer kompakten Bauweise in Geräten, wie beispielsweise Haushaltkühlschränken und Klimaanlagen, eingesetzt, bei denen der für den Einbau eines Kompressors benötigte Raum möglichst klein sein soll. Da die Kurbelwelle nicht mehr in den am Boden des Gehäuses angesammelten Ölsumpf eintaucht, sind für die Ölversorgung der rotierenden Teile dieses Verdichters im Gegensatz zu einem Rollkolbenverdichter mit senkrechter Achse zusätzliche Maßnahmen erforderlich. Neben der Verwendung von Ölpumpen, die beispielsweise von der Kurbelwelle angetrieben werden, sind auch Anordnungen bekannt, bei denen durch einen, im strömenden Druckgas erzeugten, Unterdruck das Schmieröl in das Innere der Kurbelwelle gesaugt wird.Hermetically sealed, oil-lubricated rotary piston compressors with a horizontally arranged crankshaft are used because of their compact design in devices such as household refrigerators and air conditioning systems where the space required for installing a compressor should be as small as possible. Since the crankshaft is no longer immersed in the oil sump accumulated at the bottom of the housing, additional measures are required for the oil supply to the rotating parts of this compressor, in contrast to a rotary piston compressor with a vertical axis. In addition to the use of oil pumps which are driven, for example, by the crankshaft, arrangements are also known in which the lubricating oil is sucked into the interior of the crankshaft by a negative pressure generated in the flowing compressed gas.

Es ist ein hermetisch gekapselter, ölgeschmierter Rollkolbenverdichter mit waagerecht angeordneter hohler Kurbelwelle bekannt (US-PS 4 391 573), bei dem das Schmieröl von dem aus dem Verdichter ausgestoßenen Druckgas in die hohle Kurbelwelle befördert wird, die innerhalb des Zylindergehäuses mit radialen Bohrungen versehen ist, durch die das Schmieröl zur Schmierung und Abdichtung an die gegeneiannder beweglichen Oberflächen des Verdichters gelangt. Das durch die exzentrische Rotationsbewegung des Rollkolbens aus dem Druckraum des Verdichters über eine Auslaßöffnung ausgestoßene Druckgas wird über ein außerhalb des Zylindergehäuses gelegenes Leitungssystem, das fest mit dem Zylindergehäuse verbunden ist, zu dem Ende der hohlen Kurbelwelle geführt, das der Antriebsseite abgewandt ist. Ein Teil dieses Leitungssystems besteht aus einem waagerechten Auslaßrohr, das im Olsumpf verläuft und mit einer Öffnung versehen ist, in die ein senkrechtes Saugrohr einmündet. Das obere Ende dieses Saugrohres ragt in das Auslaßrohr hinein und hat eine abgeschrägte Öffnung und bildet auf diese Weise im Auslaßrohr eine Querschnittsverengung. Dadurch entsteht ein dynamischer Unterdruck und das Schmieröl wird in das Auslaßrohr gesaugt und weiter in die hohle Kurbelwelle befördert. Da das Saugrohr nahe am Boden der Kompressor-Gehäusewand des hermetisch gekapselten Rollkolbenverdichters endet, kann die Ölversorgung auch bei geringen Neigungen des Kompressors noch aufrechterhalten werden. Bei Drehung des Kompressors um die Achse der Kurbelwelle oder um eine dazu parallele Achse wird jedoch die Ölversorgung unterbrochen, wenn die Öffnung des Saugrohres sich nicht mehr im Ölsumpf befindet.A hermetically sealed, oil-lubricated rotary piston compressor with a horizontally arranged hollow crankshaft is known (US Pat. No. 4,391,573), in which the lubricating oil is conveyed by the compressed gas discharged from the compressor into the hollow crankshaft, which is provided with radial bores within the cylinder housing through which the lubricating oil reaches the opposite movable surfaces of the compressor for lubrication and sealing. The compressed gas expelled by the eccentric rotational movement of the rolling piston from the pressure chamber of the compressor via an outlet opening is guided to the end of the hollow crankshaft, which is remote from the drive side, via a line system located outside the cylinder housing, which is firmly connected to the cylinder housing. Part of this line system consists of a horizontal outlet pipe which runs in the oil sump and is provided with an opening into which a vertical suction pipe opens. The upper end of this suction pipe protrudes into the outlet pipe and has a bevelled opening and in this way forms a cross-sectional constriction in the outlet pipe. This creates a dynamic vacuum and the lubricating oil is sucked into the outlet pipe and further conveyed into the hollow crankshaft. Since the suction pipe ends close to the bottom of the compressor housing wall of the hermetically sealed rotary piston compressor, the oil supply can still be maintained even with slight inclinations of the compressor. When the compressor is rotated about the axis of the crankshaft or about an axis parallel to it, however, the oil supply is interrupted when the opening of the intake pipe is no longer in the oil sump.

Der Erfindung liegt deshalb die Aufgabe zugrunde, einen hermetisch gekapselten ölgeschmierten Rollkolbenverdichter anzugeben, bei dem in jeder sich durch eine beliebige Drehung des Verdichters um die waagerechte Achse seiner Kurbelwelle oder einer dazu parallelen Achse ergebenden Lage die Ölversorgung aufrechterhalten wird.The invention is therefore based on the object of specifying a hermetically encapsulated oil-lubricated rotary piston compressor in which the oil supply is maintained in each position by any rotation of the compressor about the horizontal axis of its crankshaft or a position parallel to it.

Diese Aufgabe wird nun erfindungsgemäß gelöst mit den kennzeichnenden Merkmalen des Anspruchs 1. Durch diese Maßnahmen ist gewährleistet, daß die Öffnung des Ölsaugstutzens in jeder durch Drehung des Verdichters um die Achse der Kurbelwelle entstehenden Lage in den Ölsumpf eintaucht und somit die Schmierung des Rollkolbenverdichters aufrechterhalten ist.This object is now achieved according to the invention with the characterizing features of claim 1. These measures ensure that the opening of the oil suction nozzle is immersed in the oil sump in every position resulting from the rotation of the compressor about the axis of the crankshaft, and thus the lubrication of the rotary piston compressor is maintained .

Die Querschnittsverengung in der Druckgasleitung ist in einer vorteilhaften Ausführungsform eine rotationssymmetrische Düse, die auswechselbar in die Druckgasleitung eingesetzt ist. Die Düse ist vorzugsweise koaxial zur Kurbelwelle eingesetzt und befindet sich außerhalb des Olsumpfes. In einer weiteren vorteilhaften Ausführungsform mündet die Düse in einen Mischraum derart, daß sie zwischen Düse und Mischraumwand ein Saugraum befindet, der über Bohrungen mit dem Ölsaugstutzen verbunden ist. An den Mischraum schließt ein Diffusor an, in dem eine verlustarme Umsetzung von Geschwindigkeit in Druck erfolgt. Dadurch wird der durch die Düse entstehende dynamische Unterdruck für die Ölansaugung besonders vorteilhaft ausgenutzt und die Vermischung des Schmieröls mit dem Druckgas erleichtert.In an advantageous embodiment, the cross-sectional constriction in the compressed gas line is a rotationally symmetrical nozzle which is interchangeably inserted in the compressed gas line. The nozzle is preferably inserted coaxially to the crankshaft and is located outside the oil sump. In a further advantageous embodiment, the nozzle opens into a mixing chamber in such a way that there is a suction chamber between the nozzle and the wall of the mixing chamber, which is connected to the oil suction nozzle via bores. A diffuser is connected to the mixing room, in which a low-loss conversion of speed into pressure takes place. As a result, the dynamic vacuum generated by the nozzle is used particularly advantageously for the oil intake and the mixing of the lubricating oil with the compressed gas is facilitated.

In einer weiteren vorteilhaften Ausführungsform hat das Lager des Ölsaugstutzens die Gestalt eines Kalottenlagers und der Olsaugstutzen kann innerhalb eines vorbestimmten Winkelbereichs zusätzlich eine Drehbewegung um eine zur Achse der Kurbelwelle senkrechte Achse ausführen. Dadurch ist der Winkelbereich, innerhalb dem die Kurbelwelle gegen die Oberfläche des Ölsumpfes unter Aufrechterhaltung der Ölversorgung des Verdichters geneigt werden kann, gegenüber einer Ausführungsform mit einem zylindrischen Lager vergrößert.In a further advantageous embodiment, the bearing of the oil suction nozzle has the shape of a spherical bearing and the oil suction nozzle can additionally perform a rotary movement about an axis perpendicular to the axis of the crankshaft within a predetermined angular range. As a result, the angular range within which the crankshaft can be inclined against the surface of the oil sump while maintaining the oil supply to the compressor is increased compared to an embodiment with a cylindrical bearing.

Zur weiteren Erläuterung der Erfindung wird auf die Zeichnung Bezug genommen, in deren

  • Figur 1 ein hermetisch gekapselter Rollkolbenverdichter gemäß der Erfindung teilweise im Längsschnitt schematisch dargestellt ist und deren
  • Figur 2 eine vorteilhafte Ausführungsform der Ölsaugvorrichtung verdeutlicht. In
  • Figur 3 zur weiteren Erläuterung die Ölsaugvorrichtung im Querschnitt dargestellt ist.
  • Figur 4 zeigt eine vorteilhafte Ausführungsform des Olsaugstutzens im Schnitt und in
  • Figur 5 ist eine weitere vorteilhafte Ausführungsform des Rollkolbenverdichtes ebenfalls im Schnitt dargestellt.
To further explain the invention, reference is made to the drawing, in which
  • Figure 1 is a hermetically sealed rotary piston compressor according to the invention is partially shown in longitudinal section and schematically
  • Figure 2 illustrates an advantageous embodiment of the oil suction device. In
  • Figure 3 is shown in cross section for further explanation of the oil suction device.
  • Figure 4 shows an advantageous embodiment of the oil suction nozzle in section and in
  • Figure 5 is another advantageous embodiment of the rolling piston compression is also shown in section.

In der Ausführungsform eines hermetisch gekapselten Rollkolbenverdichters gemäß Figur 1 ist ein Elektromotor 4 mit einer hohlen, waagerecht angeordneten Motorwelle 6 in einem Kompressorgehäuse 2 angeordnet. Verdichter und Gehäuse sind teilweise im Schnitt dargestellt. Die Motorwelle 6 bildet zugleich die ebenfalls hohle Kurbelwelle 6 des Rollkolbenverdichters 8, dessen mit dem Kompressorgehäuse 2 fest verbundenes Zylindergehäuse 82 mit einer Ölansaugvorrichtung 10 versehen ist. Diese enthält einen um die waagerechte Achse 200 der hohlen Kurbelwelle 6 drehbar gelagerten Ölansaugstutzen 60, der in einen Ölsumpf 12 eintaucht. Am Kompressorgehäuse 2 befinden sich Durchführungen 70 für die elektrischen Anschlüsse des Elektromotors 4 und Montagehalterungen 80.In the embodiment of a hermetically sealed rotary piston compressor according to FIG. 1, an electric motor 4 with a hollow, horizontally is attached arranged motor shaft 6 arranged in a compressor housing 2. The compressor and housing are partially shown in section. The motor shaft 6 also forms the likewise hollow crankshaft 6 of the rotary piston compressor 8, the cylinder housing 82 of which is firmly connected to the compressor housing 2 and is provided with an oil suction device 10. This contains an oil intake 60 which is rotatably mounted about the horizontal axis 200 of the hollow crankshaft 6 and which is immersed in an oil sump 12. Bushings 70 for the electrical connections of the electric motor 4 and mounting brackets 80 are located on the compressor housing 2.

Das durch einen Einlaßstutzen 14 angesaugte Gas wird im Rollkolbenverdichter 8 verdichtet und über eine im Zylindergehäuse 82 befindliche Druckgasleitung in die Ölansaugvorrichtung 10 gelenkt. Dort erfolgt die Ölansaugung und das Druckgas-ÖI-Gemisch gelangt in die hohle Kurbelwelle 6. Durch radiale Bohrungen in der hohlen Kurbelwelle 6 gelangt das Öl zur Schmierung und Abdichtung an die gegeneinander beweglichen Oberflächen des Verdichters. Das Druckgas tritt zusammen mit dem überschüssigen Öl am motorseitigen Ende 132 der hohlen Kurbelwelle 6 aus. Das überschüssige Öl wird gegen die Kompressorgehäusewand 16 geschleudert und fließt von dort aus zum Ölsumpf 12 zurück. Das Druckgas wird über einen Auslaßstutzen 18, der gegenüber dem motorseitigen Ende 132 der hohlen Kurbelwelle 6 am Kompressorgehäuse 2 angebracht ist, zu einem in der Figur nicht dargestellten Kondensator weitergeführt.The gas drawn in through an inlet connection 14 is compressed in the rotary piston compressor 8 and directed into the oil suction device 10 via a compressed gas line located in the cylinder housing 82. There the oil is sucked in and the compressed gas / oil mixture reaches the hollow crankshaft 6. The oil reaches the mutually movable surfaces of the compressor for lubrication and sealing through radial bores in the hollow crankshaft 6. The compressed gas emerges together with the excess oil at the engine-side end 132 of the hollow crankshaft 6. The excess oil is thrown against the compressor housing wall 16 and flows back from there to the oil sump 12. The compressed gas is passed on via an outlet connection 18, which is attached to the compressor housing 2 opposite the engine-side end 132 of the hollow crankshaft 6, to a condenser, not shown in the figure.

In Figur 2 ist die Ölsaugvorrichtung 10 gemäß der Erfindung weiter verdeutlicht. Der Rollkolbenverdichter 8 enthält einen im Zylindergehäuse 82 exzentrisch umlaufenden Rollkolben 20. Ein am Zylindergehäuse 82 mittels einer Feder beweglich angebrachter Trennschieber 80 teilt den zwischen Zylindergehäuse 82 und Rollkolben 20 befindlichen Raum in einen Druckraum und einen Saugraum auf. Das durch den umlaufenden Rollkolben 20 im Druckraum verdichtete Gas wird über ein Druckventil 22 ausgestoßen und über eine erste Umlenkkammer 24 und eine Druckgasleitung 26 zum vom Antrieb abgewandten offenen Ende 130 der hohlen Kurbelwelle 6 geführt. Ein Teil 262 der Druckgasleitung befindet sich im Zylindergehäuse 82. Ein Umlenkkörper 50 ist über einen Dichtring 40 mit dem Zylindergehäuse 82 fest verbunden. Das Druckgas wird im Umlenkkörper 50 durch eine Gasleitung 264 zu einer zweiten Umlenkkammer 266 geführt und dort in die Düse 104 gelenkt. Die Düse 104 ist als Rotationskörper gestaltet und kann in einer vorteilhaften Ausführungsform ein in den Umlenkkörper 50 eingesetztes auswechselbares Bauteil bilden. Die Düse 104 mündet in einen ebenfalls rotationssymmetrischen Mischraum 110, an den sich ein Diffusor 106 anschließt, in dem die Geschwindigkeitsenergie verlustarm in Druckenergie rückgewandelt wird. Die Ebene der Austrittsöffnung 1042 der Düse 104, die Außenwand der Düse 104 und ein Teil der Innenwand des Mischraumes 110 bilden die Begrenzungsflächen eines Saugraumes 108. In diesen Saugraum 108 münden radial zur Achse 200 verlaufende Bohrungen 112, die zur Druckentnahme dienen. Diese Bohrungen 112 gehen von einer Nut 114 mit rechteckigem Querschnitt aus, die den Umlenkkörper 50 an seiner Außenwand ringförmig umgibt. Die Nut 114 wird von einer an der Außenwand des Umlenkkörpers 50 anliegenden, um die Achse 200 drehbaren Hohlwelle umgeben, die als Lager 62 für den ÖIsaugstutzen 60 dient. Am Außenmantel des Lagers 62 ist ein beispielsweise zylindrischer Stutzen 64 angebracht, dessen Zylinderachse senkrecht zur Achse 200 verläuft. Der zylindrische Stutzen 64 ist innen hohl und seine Bohrung mündet in die Ringnut 114. Das Lager 62 und der hohlzylindrische Stutzen 64 bilden den drehbar gelagerten Ölsaugstutzen 60. Der Schwerpunkt S des Olsaugstutzens 60 befindet sich außerhalb der Achse 200 im Stutzen 64. Die Mitte 0 der Öffnung 642 und der Schwerpunkt S des Ölsaugstutzens sind so gelegen, daß die Verlängerung ihrer Verbindungslinie L die Achse 200 in einem Schnittpunkt P schneidet. Dadurch wird bewirkt, daß sich der Ölsaugstutzen 60 im Schwerefeld stets so ausrichtet, daß der zylindrische Stutzen 64 wenigstens annähernd in der Richtung des Schwerefeldes orientiert ist. Somit ist gewährleistet, daß in jeder Lage des Rollkolbenverdichters, die sich durch beliebige Drehung um die waagrechte Achse 200 oder einer dazu parallelen Achse ergibt, sich eine am Ende des zylindrischen Stutzens 64 befindliche Öffnung 642 im Ölsumpf 12 befindet. Der Stutzen 64 ist vorzugsweise so lang, daß sich die Öffnung 642 in einem geringen Abstand zur Innenwand des Kompressorgehäuses 2 befindet. Der Ölsaugstutzen 60 ist auf den Umlenkkörper 50 aufgeschoben und durch eine Kontervorrichtung 52 gegen ein Abrutschen gesichert. Durch die düsenförmige Querschnittsverengung der Düse 104 in der Druckgasleitung 26 entsteht somit im Saugraum 108 ein Unterdruck gegenüber dem Öiraum 120. Das Schmieröl wird über den zylindrischen Stutzen 64 zu den Druckentnahme-Bohrungen 112 gesaugt und gelangt von dort aus in den Saugraum 108 und vermischt sich im Mischraum 110 mit dem Druckgas und wird dann als Druckgas-ÖI-gemisch in den Diffusor 106 und von dort aus in die hohle Kurbelwelle 6 weiterbefördert. In der hohlen Kurbelwelle 6 befinden sich Ölversorgungsbohrungen 140 durch die das Öl zur Schmierung und Abdichtung an die Wandungen der gegeneinander beweglichen Teile des Rollkolbenverdichters 8 geiangt.The oil suction device 10 according to the invention is further illustrated in FIG. The rotary piston compressor 8 contains a rotary piston 20 which rotates eccentrically in the cylinder housing 82. A separating slide 80, which is movably attached to the cylinder housing 82 by means of a spring, divides the space located between the cylinder housing 82 and the rotary piston 20 into a pressure chamber and a suction chamber. The gas compressed by the revolving rolling piston 20 in the pressure chamber is expelled via a pressure valve 22 and conducted via a first deflection chamber 24 and a compressed gas line 26 to the open end 130 of the hollow crankshaft 6 facing away from the drive. A part 262 of the compressed gas line is located in the cylinder housing 82. A deflecting body 50 is fixedly connected to the cylinder housing 82 via a sealing ring 40. The compressed gas is guided in the deflection body 50 through a gas line 264 to a second deflection chamber 266 and is directed there into the nozzle 104. The nozzle 104 is designed as a rotating body and, in an advantageous embodiment, can form a replaceable component inserted into the deflecting body 50. The nozzle 104 opens into a likewise rotationally symmetrical mixing space 110, which is adjoined by a diffuser 106, in which the speed energy is converted back into pressure energy with little loss. The plane of the outlet opening 1042 of the nozzle 104, the outer wall of the nozzle 104 and part of the inner wall of the mixing space 110 form the boundary surfaces of a suction space 108. Bores 112 which run radially to the axis 200 and serve to remove pressure open into this suction space 108. These bores 112 start from a groove 114 with a rectangular cross section, which surrounds the deflecting body 50 in an annular manner on its outer wall. The groove 114 is surrounded by a hollow shaft which bears against the outer wall of the deflecting body 50 and can be rotated about the axis 200 and which serves as a bearing 62 for the oil suction nozzle 60. A, for example, cylindrical connecting piece 64 is attached to the outer surface of the bearing 62, the cylinder axis of which extends perpendicular to the axis 200. The cylindrical socket 64 is hollow on the inside and its bore opens into the annular groove 114. The bearing 62 and the hollow cylindrical socket 64 form the rotatably mounted oil suction socket 60. The center of gravity S of the oil suction socket 60 is located outside the axis 200 in the socket 64. The center 0 The opening 642 and the center of gravity S of the oil suction nozzle are located such that the extension of their connecting line L intersects the axis 200 at an intersection point P. This has the effect that the oil suction nozzle 60 is always aligned in the gravitational field in such a way that the cylindrical nozzle 64 is at least approximately oriented in the direction of the gravitational field. This ensures that in each position of the rotary piston compressor, which results from any rotation about the horizontal axis 200 or an axis parallel thereto, there is an opening 642 in the oil sump 12 at the end of the cylindrical connecting piece 64. The connecting piece 64 is preferably so long that the opening 642 is at a short distance from the inner wall of the compressor housing 2. The oil suction port 60 is pushed onto the deflection body 50 and secured against slipping off by a counter device 52. The nozzle-shaped cross-sectional constriction of the nozzle 104 in the compressed gas line 26 thus creates a negative pressure in the suction chamber 108 compared to the oil chamber 120. The lubricating oil is sucked through the cylindrical nozzle 64 to the pressure tapping holes 112 and from there reaches the suction chamber 108 and mixes in the mixing chamber 110 with the pressurized gas and is then conveyed as a pressurized gas / oil mixture into the diffuser 106 and from there into the hollow crankshaft 6. In the hollow crankshaft 6 there are oil supply bores 140 through which the oil is angled for lubrication and sealing to the walls of the parts of the rotary piston compressor 8 which are movable relative to one another.

In Figur 3 ist zur weiteren Erläuterung der ÖIsaugstutzen 60 in einer Lage dargestellt, in der der zylindrische Stutzen 64 nicht parallel zum Schwerefeld oder zu einem durch Rotation des Rollkolbenverdichters um die Achse 200 oder einer dazu parallelen Achse verursachten Trägheitsfeld ausgerichtet ist. Auf den Ölsaugstutzen wirkt die Schwerkraft oder die Trägheitskraft F, die ein Drehmoment M um die Achse 200 erzeugt. Durch das Drehmoment M wird der Saugstutzen 64 wenigstens annähernd parallel zum Schwere- oder Trägheitsfeld ausgerichtet. Seine Öffnung 642 befindet sich somit in der Gleichg ewichtslage stets im Ölsumpf 12.For further explanation, FIG. 3 shows the oil suction nozzle 60 in a position in which the cylindrical nozzle 64 is not aligned parallel to the gravitational field or to an inertial field caused by rotation of the rotary piston compressor around the axis 200 or an axis parallel to it. Gravity or inertial force F, which generates a torque M about axis 200, acts on the oil suction port. Due to the torque M, the suction port 64 is aligned at least approximately parallel to the gravity or inertia field. Its opening 642 is thus always in the equilibrium position in the oil sump 12.

In der vorteilhaften Ausführungsform gemäß Figur 4 hat der Stutzen 68 des Ölsaugstutzens 60 etwa die Gestalt eines Kreisscheibensektors. Der Abstand des Schwerpunktes S zur Achse 200 und das von der Schwer- bzw. Trägheitskraft erzeugte Drehmoment M wird somit gegenüber der Ausführungsform eines zylindrischen Stutzens entsprechend vergrößert. Dadurch werden Lagerreibungskräfte, welche die Ausrichtung des Olsaugstutzens 60 hemmen können, leichter überwunden.In the advantageous embodiment according to FIG. 4, the nozzle 68 of the oil suction nozzle 60 has approximately the shape of a circular disk sector. The distance of the center of gravity S to the axis 200 and that Torque M generated by the gravity or inertia force is accordingly increased compared to the embodiment of a cylindrical connecting piece. As a result, bearing friction forces which can inhibit the alignment of the oil suction nozzle 60 are overcome more easily.

In der Ausführungsform nach Figur 5 ist das Druckventil 22 in dem vom Antrieb abgewandten Teil des Zylindergehäuses 82 untergebracht. Über die Druckgasleitung 26 gelangt das Druckgas direkt zur Umlenkkammer 266. Die Kurbelwelle 6 ist nur innerhalb des Zylindergehäuses 82 hohl und dort mit radialen Bohrungen 140 versehen. Der Diffusor 106 schließt an das eine offene Ende der Kurbelwelle 6 an und ist mittels radialer Auslaß-Bohrungen 34 mit dem Ölraum 120 verbunden. Das Druckgas-ÖI-Gemisch strömt aus dem Diffusor 106 in den Ölraum 120 und von dort aus beispielsweise durch in der Zeichnung nicht dargestellte, parallel zur Kurbelwelle verlaufende Bohrungen im Läufer des Elektromotors 4 zum Auslaßstutzen 18. Dadurch erfolgt gleichzeitig eine Kühlung des Elektromotors 4.In the embodiment according to FIG. 5, the pressure valve 22 is accommodated in that part of the cylinder housing 82 which faces away from the drive. The compressed gas reaches the deflection chamber 266 directly via the compressed gas line 26. The crankshaft 6 is hollow only within the cylinder housing 82 and is provided with radial bores 140 there. The diffuser 106 connects to one open end of the crankshaft 6 and is connected to the oil space 120 by means of radial outlet bores 34. The pressurized gas-oil mixture flows from the diffuser 106 into the oil chamber 120 and from there, for example, through bores in the rotor of the electric motor 4, not shown in the drawing, which run parallel to the crankshaft to the outlet port 18. This simultaneously cools the electric motor 4.

Ein Teil 54 der Außenfläche des Umlenkkörpers 50 wird durch die Mantelfläche einer Kugelzone gebildet und ist von einer Nut 116 ringförmig umgeben. Die Querschnittsfläche der Nut 116 ist beispielsweise ein Kreisringsektor. Die Nut 116 ist mittels senkrecht zur Achse 200 verlaufender Bohrungen 112 mit dem Saugraum 108 verbunden. Die Nut 116 wird von einem auf dem Teil 52 der Außenfläche des Umlenkkörpers 50 anliegenden Kalottenlager 66 des Ölsaugstutzen 60 umgeben. Das Kalottenlager 66 kann an seiner Innenfläche ebenfalls mit einer ringförmig umlaufenden Nut 118 versehen sein, in welche die Bohrung eines beispielsweise zylindrischen Stutzens 64 mündet. Durch diesen Aufbau ist gewährleistet, daß der Ölsaugstutzen 60 auch dann noch frei durch die Schwer- oder Trägheitskraft um die Achse 200 gedreht werden kann, wenn diese innerhalb eines vorbestimmten Winkelbereiches a gegen die Oberfläche des Ölsumpfes 12 geneigt ist. Bei zylindrischen Lagerflächen besteht bei solchen Neigungen nämlich die Möglichkeit, daß sich der ÖIsaugstutzen 60 verkantet und an seiner Drehbewegung gehindert ist. Ein weiterer Vorteil der kalottenförmigen Lagerung des Ölsaugstutzens 60 besteht auch darin, daß der Neigungswinkel a der Kurbelwelle 6 gegen die Oberfläche des Ölsumpfes 12, bis zu dem sich die Öffnung 642 des Stutzens 6 noch im Ölsumpf 12 befindet, gegenüber der Ausführungsform mit einer zylindrischen Lagerfläche des ÖIsaugstutzens 60 vergrößert ist.A part 54 of the outer surface of the deflecting body 50 is formed by the outer surface of a spherical zone and is surrounded by a groove 116 in a ring. The cross-sectional area of the groove 116 is, for example, an annular sector. The groove 116 is connected to the suction chamber 108 by means of bores 112 running perpendicular to the axis 200. The groove 116 is surrounded by a spherical bearing 66 of the oil suction nozzle 60 resting on the part 52 of the outer surface of the deflecting body 50. The spherical bearing 66 can also be provided on its inner surface with an annular circumferential groove 118, into which the bore of a, for example, cylindrical connecting piece 64 opens. This construction ensures that the oil suction nozzle 60 can still be freely rotated about the axis 200 by the force of gravity or inertia if it is inclined within a predetermined angular range a against the surface of the oil sump 12. In the case of cylindrical bearing surfaces with such inclinations, there is the possibility that the oil suction nozzle 60 is tilted and prevented from rotating. Another advantage of the dome-shaped mounting of the oil suction nozzle 60 is that the angle of inclination α of the crankshaft 6 against the surface of the oil sump 12, up to which the opening 642 of the nozzle 6 is still in the oil sump 12, compared to the embodiment with a cylindrical bearing surface of the oil suction port 60 is enlarged.

Claims (7)

1. Hermetically encapsulated oil-lubricated rotary piston compressor with
- a horizontally disposed crankshaft (6), hollow at least inside the cylinder housing (82), which is open at least at one end and is provided with bores (140),
- a compressed gas line (26) which connects a compression chamber of the rotary piston compressor (8) to the open end of the hollow crankshaft (6) remote from the drive (4),
- a cross-sectional constriction (104) located in the compressed gas line (26) and
- an oil suction pipe (60) which connects the cross-sectional constriction (104) to an oil sump (12),
characterised by the following features:
- the oil suction pipe (60) is rotatably mounted about the axis (200) of the crankshaft (6),
- the centre of gravity (S) of the oil suction pipe (60) is located at a distance from the axis (200),
- the extension of the connection line between the centre of the aperture (642) of the oil suction pipe (60), which dips into the oil sump (12), and the centre of gravity (S) intersects the axis (200).
2. Rotary piston compressor according to claim 1, characterised in that a nozzle (104) and a diffusor (106) are provided.
3. Rotary piston compressor according to claim 2, characterised in that an exchangeable rotationally- symmetric nozzle (104) is provided.
4. Rotary piston compressor according to claim 3, characterised in that the nozzle (104) is arranged coaxially with the crankshaft (6).
5. Rotary piston compressor according to claim 3, characterised in that the nozzle (104) opens into a mixing chamber (110) adjacent to which is the diffusor (106).
6. Rotary piston compressor according to claim 4, characterised in that a suction chamber (108) is connected by means of bores (112) to the oil suction pipe (60).
7. Rotary piston compressor according to one of claims 1 to 6, characterised in that the oil suction pipe (60) is rotatably mounted about an axis perpendicular to the axis (200) of the crankshaft, within a predetermined angular range (a).
EP86105874A 1985-05-08 1986-04-29 Encapsulated rolling-piston compressor Expired - Lifetime EP0210349B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3516593 1985-05-08
DE3516593 1985-05-08

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EP0210349A2 EP0210349A2 (en) 1987-02-04
EP0210349A3 EP0210349A3 (en) 1988-03-30
EP0210349B1 true EP0210349B1 (en) 1990-03-21

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EP (1) EP0210349B1 (en)
JP (1) JPS61255293A (en)
DE (1) DE3669754D1 (en)

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CN103541905B (en) * 2012-07-13 2017-06-13 艾默生环境优化技术(苏州)有限公司 Compressor with a compressor housing having a plurality of compressor blades
CN103557162B (en) * 2013-10-22 2017-01-25 广东美芝制冷设备有限公司 Rotary compressor
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JPS61255293A (en) 1986-11-12
DE3669754D1 (en) 1990-04-26
US4729728A (en) 1988-03-08
EP0210349A2 (en) 1987-02-04
EP0210349A3 (en) 1988-03-30

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