EP2137412B1 - Displacement machine according to the spiral principle - Google Patents
Displacement machine according to the spiral principle Download PDFInfo
- Publication number
- EP2137412B1 EP2137412B1 EP07720172A EP07720172A EP2137412B1 EP 2137412 B1 EP2137412 B1 EP 2137412B1 EP 07720172 A EP07720172 A EP 07720172A EP 07720172 A EP07720172 A EP 07720172A EP 2137412 B1 EP2137412 B1 EP 2137412B1
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- EP
- European Patent Office
- Prior art keywords
- lubricant
- pressure
- space
- displacement machine
- machine according
- 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.)
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Classifications
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- 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
- F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
- F04C27/008—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids for other than working fluid, i.e. the sealing arrangements are not between working chambers of the machine
- F04C27/009—Shaft sealings specially adapted for pumps
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- 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
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
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- 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
- F04C2270/00—Control; Monitoring or safety arrangements
- F04C2270/21—Pressure difference
Definitions
- the present invention relates to a displacement machine for compressible media according to the preamble of claim 1.
- Verdrängermaschinen the spiral type are for example from the DE-A-3 347 081 known.
- a built-up according to this principle compressor is characterized by a low-pulsation promotion of the gaseous working fluid, eg air, and could therefore be used with advantage, inter alia, for charging purposes in internal combustion engines.
- the gaseous working fluid eg air
- a plurality of approximately crescent-shaped working spaces are trapped in the displacer chamber between the spirally-formed displacer and the two peripheral walls, moving from the inlet through the displacer chamber to the outlet, constantly reducing its volume and pressure of the working fluid is increased accordingly.
- the displacement body is driven by means of an eccentric shaft and held by a guide assembly, not shown.
- the machine consists essentially of two housing halves, in which spiral channels are incorporated.
- the displacer is mounted by means of a bearing on the eccentric of the eccentric shaft. This storage (also referred to as the main eccentric bearing) requires suitable lubrication.
- Such lubrication is for example in the EP-A-0 614 012 , which has a Verdrängermaschine of the type mentioned in the subject and discloses the preamble of claim 1, shown.
- a liquid lubricant lubricating oil
- the lubricating oil passes through a radially angeordeten channel in the main eccentric bearing.
- the lubricating oil then flows through a second, also radially disposed channel in the direction of the center of the drive shaft and there opens into a coaxially or parallel to the feed channel arranged return channel through which the lubricating oil reaches one end of the drive shaft, from where the lubricating oil by a Bore in one half of the housing can flow to the outside.
- a pressure oil lubrication as in the EP-A-0 614 012 is suitable for operation under high load of the machine, as is the case in particular at high speeds.
- Such forced lubrication allows a sufficiently large flow of oil to dissipate the heat generated at high load heat loss in the main eccentric bearing with the lubricating oil.
- the sealing of the lubricating oil-containing oil space against the pumping chamber is effected by shaft seals, which are provided both in the bearings of the drive shaft in the housing and the bearing of the displacer on the eccentric (main eccentric). Since, depending on the load case of the machine, the pressure in the delivery chamber may exceed those in the oil chamber in which collects the effluent from the bearings lubricating oil, there is a risk that in such an operating condition, the shaft seals of the shaft respectively. be lifted off the eccentric and thereby the Pumped fluid (eg air) can reach the lubricating oil side of the shaft seals and escapes through the oil return line. Especially at low speeds, where such positive displacement machines must be very dense, any further loss of fluid is disadvantageous, since in the case of use as a supercharger for internal combustion engines achievable torque can be significantly affected.
- shaft seals which are provided both in the bearings of the drive shaft in the housing and the bearing of the displacer on the eccentric (main eccentric). Since, depending on the load case of the
- the present invention is based on the object, in operation to prevent lifting of the shaft seals from the shaft at high delivery pressures of the fluid.
- the in the Fig. 1 and 2 in front view or in section shown displacement machine has a two housing halves 1a, 1b existing housing in which a displacement body 2 is mounted.
- the two housing halves 1a, 1b are bolted together in a manner not shown.
- In the presentation of the Fig. 1 is the one housing half 1a ( Fig. 2 ) away.
- the displacement body 2 has a disc 3, which carries on each side a spiraling displacement elements 4, 5.
- the displacement elements 4, 5 are formed as protruding from the disc 3 strips.
- a drive shaft 6 is provided, whose axis of rotation is denoted by 6a.
- the drive shaft 6 is mounted in the housing halves 1a, 1b by means of bearings 7 and 8 and has an eccentric disk 9, whose axis of symmetry is designated by 9a.
- the distance between the axis of rotation 6a of the drive shaft 6 and the axis of symmetry 9a of the eccentric disc 9 (eccentricity) is in the Fig. 1 denoted by e.
- a drive pulley 11 is fastened by means of a screw 10.
- the hub 13 of the disc 3 is supported by means of a bearing 12, which is a rolling bearing in the present case.
- the disk 3 and thus the displacement body 2 are driven via the drive shaft 6 and the eccentric disk 9.
- the driving force is transmitted via the bearing 12 to the hub 13 of the disk 3.
- the guide of the displacement body 2 via a rocker 14 which is rotatably mounted at one end on a shaft 15 ( Fig. 1 ).
- the rocker 14 carries a bolt 16 which is rotatably mounted in an eye 17 of the disc 3.
- the housing 1 has an inlet 18 and an outlet 19 for the conveying medium, preferably air, as well as two delivery chambers 20, 20 '.
- a passage 21 (or more passages) is provided, through which the fluid can pass from the delivery chamber 20 into the delivery chamber 20 '.
- two counterweights 22, 23 are arranged on the drive shaft 6.
- a lubricant supply system 24 (FIG. Fig. 2 ), which supplies the bearing 12 with a lubricant, preferably lubricating oil.
- This lubricant supply system 24 has a supply line 25 connected to the housing 1, which is connected to the pressure side of a pressure-controlled feed pump 26.
- a pressure-controlled feed pump 26 Such pumps with pressure control, which in Internal combustion engines are used, produce a lubricant delivery pressure, which remains within operating limits within operating limits.
- the feed pump 26 On the suction side, the feed pump 26 is connected via a suction line 27 with a lubricant container 28, which communicates via a connecting line 29 with the environment.
- the ambient air pressure always acts on the surface of the lubricant 30 in the lubricant container 28.
- the feed line 25 can, in the Fig. 2 to 4 Dashed flow restrictor 31, for example, a flow restrictor, are used.
- the drive shaft 6 has a lubricant supply passage 32 and a lubricant return passage 33 which are coaxial with the rotation axis 6a of the drive shaft 6 ( Fig. 2 and 3 ).
- a tubular guide sleeve 35 is inserted into a longitudinal bore 34 in the drive shaft 6, which has on its outer side a portion with a smaller outer diameter, which extends over part of the length of the guide sleeve 35, and with the wall the longitudinal bore 34 forms the lubricant return passage 33.
- the lubricant supply channel 32 extending in the interior of the guide sleeve 35 is in communication with an inflow channel 36, which extends in the radial direction in the eccentric disc 9 and opens into a first lubricant chamber 37 on one side of the bearing 12 ( Fig. 3 ).
- This first lubricant chamber 37 is sealed off from the delivery chamber 20 by means of an annular sealing element 38, which bears against the eccentric disk 9.
- On the other side of the bearing 12 is a second lubricant chamber 39, the is sealed relative to the delivery chamber 20 'by means of an annular sealing element 40, which also bears against the eccentric disc 9.
- This second lubricant chamber 39 communicates with the lubricant return passage 33 via a radial outflow channel 41 in the eccentric disk 9.
- a radial communication passage 42 in the drive shaft 6 connects the lubricant return passage 33 with a lubricant return passage 43, which belongs to a designated at 44 lubricant recirculation.
- the lubricant return line 43 is connected to the inlet of a pressure control valve 45 whose output is connected via a return line 46 to the lubricant reservoir 28.
- Trained as a diaphragm valve pressure control valve 45 has a diaphragm 47 which divides the interior of the pressure control valve 45 into two chambers 45 a and 45 b.
- a control body 48 is mounted, which regulates in a manner to be described, the lubricant outflow from the lubricant return line 43 into the chamber 45a.
- the chamber 45a of the pressure control valve 45 opposite the chamber 45a is connected via a connecting line 49 to the delivery chamber 20 '. This means that the pressure in this chamber 45b corresponds to the working pressure in the delivery chamber 20 '.
- the delivery chamber 20 ' is sealed to the outside by means of an annular sealing element 50, which bears against the drive shaft 6.
- the conveyed by the pump 26 lubricant passes through the supply line 25, the From this first lubricant chamber 37, the lubricant flows through the bearing 12 into the second lubricant chamber 39. From the second lubricant chamber 39, the lubricant passes via the discharge channel 41, the lubricant return channel 33, the connecting channel 42 and the lubricant return line 43 into the chamber 45a of the pressure control valve 45. From this chamber 45a, the lubricant flows via the return line 46 back into the lubricant container 28th
- the membrane 47 is deflected more or less downwards in the direction of the inlet opening 46a of the return line 46.
- the distance between the control body 48 and the inlet opening 46a of the return line 46 is greater or smaller, with the result that the amount of the out of the chamber 45a in the Return line 46 flowing lubricant is controlled accordingly. In this way, the pressure in the lubricant return line 43 and thus also in the lubricant spaces 37 and 39 is changed depending on the delivery or working pressure in the delivery chamber 20 '.
- sealing elements 38, 40 Since the difference between the pressure acting on one side of the sealing elements 38, 40 pressure in the delivery chamber 20, 20 'and acting on the other side of these sealing elements 38, 40 pressure in the lubricant spaces 37, 39 is kept substantially constant, is avoided in that the sealing elements 38, 40 can lift off the eccentric disk 9 during operation.
- FIG. 4 the Fig. 3 are identical, the same reference numerals are used as in the corresponding components Fig. 3 ,
- the housing 51a and the diaphragm 47 with the control body 48 of the pressure control valve 51 is attached directly to the housing half 1a, for example by means of a snap ring 52.
- the chamber 51 'formed by the housing 51a and the diaphragm 47 is connected to the delivery chamber 20 via the connecting line 49 ' in connection.
- the lubricant return line 43 opens into a formed in the housing half 1a, part of the pressure control valve 51 forming chamber 53 which is closed by the membrane 47 and to which the return line 46 is connected.
- the control body 48 of the membrane 47 is as in the embodiment according to Fig. 3 the inlet opening 46a of the return line 46th opposite and serves to regulate the amount of the lubricant flowing through this inlet opening 46a.
- the operation of the pressure control valve 51 is the same as the already described operation of the pressure control valve 45 according to Fig. 3 ,
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Rotary Pumps (AREA)
- Lubrication Of Internal Combustion Engines (AREA)
Description
Die vorliegende Erfindung betrifft eine Verdrängermaschine für kompressible Medien gemäss Oberbegriff des Anspruches 1.The present invention relates to a displacement machine for compressible media according to the preamble of
Verdrängermaschinen der Spiralbauart sind beispielsweise aus der
Bei der in dieser
Eine solche Schmierung ist beispielsweise in der
Eine Druckölschmierung, wie sie in der
Die Abdichtung des das Schmieröl enthaltenden Ölraumes gegen den Förderraum erfolgt durch Wellendichtringe, die sowohl bei den Lagern der Antriebswelle im Gehäuse als auch beim Lager des Verdrängers auf dem Exzenter (Hauptexzenterlager) vorgesehen sind. Da je nach Lastfall der Maschine der Druck im Förderraum jenen im Ölraum, in dem sich das aus den Lagern abströmende Schmieröl sammelt, übersteigen kann, besteht die Gefahr, dass in einem solchen Betriebszustand die Wellendichtringe von der Welle resp. vom Exzenter abgehoben werden und dadurch das Fördermedium (z.B. Luft) auf die Schmierölseite der Wellendichtringe gelangen kann und durch die Ölrücklaufleitung entweicht. Insbesondere bei niedrigen Drehzahlen, wo solche Verdrängermaschinen sehr dicht sein müssen, ist jeder weitere Verlust an Fördermedium nachteilig, da dadurch im Falle des Einsatzes als Aufladeaggregat für Verbrennungsmotoren das erzielbare Drehmoment erheblich beeinträchtigt werden kann.The sealing of the lubricating oil-containing oil space against the pumping chamber is effected by shaft seals, which are provided both in the bearings of the drive shaft in the housing and the bearing of the displacer on the eccentric (main eccentric). Since, depending on the load case of the machine, the pressure in the delivery chamber may exceed those in the oil chamber in which collects the effluent from the bearings lubricating oil, there is a risk that in such an operating condition, the shaft seals of the shaft respectively. be lifted off the eccentric and thereby the Pumped fluid (eg air) can reach the lubricating oil side of the shaft seals and escapes through the oil return line. Especially at low speeds, where such positive displacement machines must be very dense, any further loss of fluid is disadvantageous, since in the case of use as a supercharger for internal combustion engines achievable torque can be significantly affected.
Der vorliegenden Erfindung liegt nun die Aufgabe zu Grunde, im Betrieb ein Abheben der Wellendichtringe von der Welle bei hohen Förderdrücken des Fördermediums zu verhindern.The present invention is based on the object, in operation to prevent lifting of the shaft seals from the shaft at high delivery pressures of the fluid.
Diese Aufgabe wird erfindungsgemäss mit einer Verdrängermaschine mit den Merkmalen des Anspruches 1 gelöst.This object is achieved according to the invention with a positive displacement machine having the features of
Dadurch, dass im Betrieb die Differenz zwischen dem Druck im Förderaum, der auf die eine Seite der Dichtelemente wirkt, und dem Druck im Schmiermittelraum, der auf die andere Seite der Dichtelemente wirkt, im wesentlich konstant halten wird, wird ein Abheben der Dichtringe wirkungsvoll vermieden, und zwar bei allen Arbeitsdrücken im Förderraum.Characterized in that the difference between the pressure in the conveying space, which acts on one side of the sealing elements, and the pressure in the lubricant chamber, which acts on the other side of the sealing elements, will keep substantially constant during operation, a lifting of the sealing rings is effectively avoided , and indeed at all working pressures in the delivery room.
Bevorzugte Weiterausgestaltungen der erfindungsgemässen Verdrängermaschine bilden Gegenstand der abhängigen Ansprüche.Preferred further developments of the displacement machine according to the invention form the subject of the dependent claims.
Im Folgenden werden anhand der Zeichnungen Ausführungsbeispiele des Erfindungsgegenstandes näher erläutert. Es zeigt rein schematisch:
- Fig. 1
- in Vorderansicht und in Richtung des Pfeils A in
Fig. 2 den antriebsseitigen Gehäuseteil, - Fig. 2
- die Verdrängermaschine gemäss
Fig. 1 in einem Längsschnitt entlang der Linie II-II inFig. 1 , - Fig. 3
- einen Ausschnitt aus der
Fig. 2 in einem gegenüber derFig. 2 vergrösserten Massstab, und - Fig. 4
- in einer der
Fig. 3 entsprechenden Darstellung eine zweite Ausführungsform eines Drucksteuerventils.
- Fig. 1
- in front view and in the direction of the arrow A in
Fig. 2 the drive-side housing part, - Fig. 2
- the displacement machine according to
Fig. 1 in a longitudinal section along the line II-II inFig. 1 . - Fig. 3
- a section of the
Fig. 2 in one oppositeFig. 2 enlarged scale, and - Fig. 4
- in one of the
Fig. 3 corresponding representation of a second embodiment of a pressure control valve.
Die in den
Der Verdrängerkörper 2 weist eine Scheibe 3 auf, die auf jeder Seite einen spiralförmig verlaufenden Verdrängerelemente 4, 5 trägt. Die Verdrängerelemente 4, 5 sind als von der Scheibe 3 abstehende Leisten ausgebildet. Zur Lagerung der Scheibe 3 ist eine Antriebswelle 6 vorgesehen, deren Drehachse mit 6a bezeichnet ist. Die Antriebswelle 6 ist in den Gehäusehälften 1a, 1b mittels Lagern 7 bzw. 8 gelagert und weist eine Exzenterscheibe 9 auf, deren Symmetrieachse mit 9a bezeichnet ist. Der Abstand zwischen der Drehachse 6a der Antriebswelle 6 und der Symmetrieachse 9a der Exzenterscheibe 9 (Exzentrizität) ist in der
Auf der Exzenterscheibe 9 ist mittels eines Lagers 12, das im vorliegenden Fall ein Wälzlager ist, die Nabe 13 der Scheibe 3 gelagert. Angetrieben wird die Scheibe 3 und somit der Verdrängerkörper 2 über die Antriebswelle 6 und die Exzenterscheibe 9. Dabei wird die Antriebskraft über das Lager 12 auf die Nabe 13 der Scheibe 3 übertragen. Die Führung des Verdrängerkörpers 2 erfolgt über eine Schwinge 14, die am einen Ende drehbar auf einer Welle 15 gelagert ist (
Das Gehäuse 1 weist einen Einlass 18 und einen Auslass 19 für das Fördermedium, vorzugsweise Luft, sowie zwei Förderräume 20, 20' auf. In der Scheibe 3 ist ein Durchlass 21 (oder mehrere Durchlässe) vorhanden, durch den das Fördermedium vom Förderraum 20 in den Förderraum 20' gelangen kann.The
Zum Ausgleich der beim exzentrischen Antrieb des Verdrängerkörpers 2 entstehenden Massenkräfte sind auf der Antriebswelle 6 zwei Gegengewichte 22, 23 angeordnet.To compensate for the mass forces resulting from the eccentric drive of the
Zur Schmierung des Lagers 12, das zwischen der Exzenterscheibe 9 und der Nabe 13 der Scheibe 3 angeordnet ist, ist ein Schmiermittelzuführsystem 24 (
Dieses Schmiermittelzuführssystem 24 weist eine an das Gehäuse 1 angeschlossene Zuführleitung 25 auf, die mit der Druckseite einer druckgeregelten Förderpumpe 26 verbunden ist. Solche Pumpen mit Druckregelung, die in Verbrennungsmotoren eingesetzt werden, erzeugen einen Schmiermittelförderdruck, der im Betrieb innerhalb gewisser Grenzwerte bleibt. Saugseitig ist die Förderpumpe 26 über eine Saugleitung 27 mit einem Schmiermittelbehälter 28 verbunden, der über eine Verbindungsleitung 29 mit der Umgebung in Verbindung steht. Somit wirkt auf die Oberfläche des Schmiermittels 30 im Schmiermittelbehälter 28 stets der Umgebungsluftdruck. In die Zuführleitung 25 kann ein, in den
Die Antriebswelle 6 weist einen Schmiermittelzuleitungskanal 32 und einen Schmiermittelrücklaufkanal 33 auf, die zur Drehachse 6a der Antriebswelle 6 koaxial sind (
Ein radialer Verbindungskanal 42 in der Antriebswelle 6 verbindet den Schmiermittelrücklaufkanal 33 mit einer Schmiermittelrücklaufleitung 43, die zu einer mit 44 bezeichneten Schmiermittelrückführung gehört. Die Schmiermittelrücklaufleitung 43 ist mit dem Eingang eines Drucksteuerventils 45 verbunden, dessen Ausgang über eine Rücklaufleitung 46 mit dem Schmiermittelbehälter 28 verbunden ist. Das als Membranventil ausgebildete Drucksteuerventil 45 weist eine Membran 47 auf, die den Innenraum des Drucksteuerventils 45 in zwei Kammern 45a und 45b unterteilt. Etwa in der Mitte der Membran 47 und der Austrittsöffnung 46a der Rücklaufleitung 46 gegenüberliegend ist an der Membran 47 ein Steuerkörper 48 angebracht, der auf noch zu beschreibende Weise den Schmiermittelausfluss aus der Schmiermittelrücklaufleitung 43 in die Kammer 45a reguliert. Die der Kammer 45a gegenüberliegende Kammer 45b des Drucksteuerventils 45 ist über eine Verbindungsleitung 49 mit dem Förderraum 20' verbunden. Das bedeutet, dass der Druck in dieser Kammer 45b dem Arbeitsdruck im Förderraum 20' entspricht. Der Förderraum 20' ist mittels eines ringförmigen Dichtelementes 50, das an der Antriebswelle 6 anliegt, nach aussen abgedichtet.A
Das von der Förderpumpe 26 geförderte Schmiermittel gelangt über die Zuführleitung 25, den Schmiermittelzuleitungskanal 32 und den Zuflusskanal 36 zum ersten Schmiermittelraum 37. Von diesem ersten Schmiermittelraum 37 strömt das Schmiermittel durch das Lager 12 hindurch in den zweiten Schmiermittelraum 39. Vom zweiten Schmiermittelraum 39 gelangt das Schmiermittel über den Abflusskanal 41, den Schmiermittelrücklaufkanal 33, den Verbindungskanal 42 und die Schmiermittelrücklaufleitung 43 in die Kammer 45a des Drucksteuerventils 45. Von dieser Kammer 45a fliesst das Schmiermittel über die Rücklaufleitung 46 zurück in den Schmiermittelbehälter 28.The conveyed by the
Je nach Grösse des im Förderraum 20' herrschenden Förder- oder Arbeitsdruckes, der ja auch in der Kammer 45b des Drucksteuerventils 45 herrscht, wird die Membran 47 mehr oder weniger stark nach unten in Richtung zur Eintrittsöffnung 46a der Rücklaufleitung 46 ausgelenkt. Das bedeutet, dass abhängig von der Differenz der in den Kammern 45a, 45b herrschenden Drücke der Abstand zwischen dem Steuerkörper 48 und der Eintrittsöffnung 46a der Rücklaufleitung 46 grösser oder kleiner ist, was zur Folge hat, dass die Menge des aus der Kammer 45a in die Rücklaufleitung 46 ausfliessenden Schmiermittels entsprechend geregelt wird. Auf diese Weise wird der Druck in der Schmiermittelrücklaufleitung 43 und damit auch in den Schmiermittelräumen 37 und 39 in Abhängigkeit vom Förder- oder Arbeitsdruck im Förderraum 20' verändert. Steigt der Druck im Förderraum 20', so wird der Abstand zwischen dem Steuerkörper 48 und der Austrittsöffnung 43a verkleinert, was zu einem Aufstauen des zurückfliessenden Schmiermittels und damit zu einem Druckanstieg in der Schmiermittelrückführung 44 und in den Schmiermittelräumen 37, 39 führt. Somit zieht ein Druckanstieg im Förderraum 20' zwangsläufig einen Druckanstieg in den Schmiermittelräumen 37, 39 nach sich. Auf diese Weise wird erreicht, dass die Differenz der Drücke, welche auf die beiden Seiten der Dichtelemente 38 und 40 wirkt, immer etwa gleich bleibt, und zwar unabhängig davon, ob im Betrieb der Verdrängermaschine der Förderdruck im Förderraum 20' höher oder niedriger ist. Da die Differenz zwischen dem auf die eine Seite der Dichtelemente 38, 40 wirkenden Druck im Förderraum 20, 20' und dem auf die andere Seite dieser Dichtelemente 38, 40 wirkenden Druck in den Schmiermittelräumen 37, 39 im Wesentlichen konstant gehalten wird, wird vermieden, dass sich die Dichtelemente 38, 40 im Betrieb von der Exzenterscheibe 9 abheben können.Depending on the size of the conveying or working pressure prevailing in the conveying space 20 ', which indeed also prevails in the
Anhand der
Bei der Ausführungsform gemäss
Die Wirkungsweise des Drucksteuerventils 51 ist dieselbe wie die bereits beschriebene Wirkungsweise des Drucksteuerventils 45 gemäss
Claims (7)
- A displacement machine for compressible media, comprising at least one spiral-shaped conveying space (20, 20') which is arranged in a fixed housing (1), a displacement body (2) which is associated with the conveying space (20, 20') and which is mounted by means of a bearing (12) on an eccentric disk (9) connected with a drive shaft (6), and pressure-oil lubrication, containing a feed pump (26) for producing a lubricant feed pressure and a lubricant supply system (24) for feeding a lubricant (30) to the bearing (12) via the drive shaft (6) and the eccentric disk (9), and sealing elements (38, 40) for sealing the lubricant space (37, 39) filled with lubricant (30) against the conveying space (20, 20') filled with working medium, characterized in that pressure-equalizing means (45, 51) are provided, which during operation substantially keep constant the difference between the pressure in the conveying space (20, 20') acting on the one side of the sealing elements (38, 40) and the pressure in the lubricant space (37, 38) acting on the other side of the sealing elements (38, 40).
- A displacement machine according to claim 1, characterized in that the pressure-equalizing means are formed by a pressure control valve (45, 51), which is subjected on the one hand to the pressure in the conveying space (20, 20') and on the other hand to the pressure in the lubricant space (37, 39).
- A displacement machine according to claim 2, characterized in that the pressure control valve (45, 51) is arranged in a lubricant recirculation (44) which is connected with the lubricant space (37, 39).
- A displacement machine according to claim 2 or 3, characterized in that the pressure control valve (45, 51) is arranged as a membrane valve.
- A displacement machine according to claims 3 and 4, characterized in that the flexible membrane (47) of the pressure control valve (45, 51) is subjected on the one side to pressure in the conveying space (20, 20') and is connected on the other side with the lubricant space (37, 39), and comprises a control body (48) which is opposite of the entrance opening (46a) of a return line (46) for the lubricant (30), wherein the control body (48) controls the lubricant return flow through the entrance opening (46a) of the return line (46) depending on the difference of the pressures in the conveying space (20, 20') and in the lubricant space (37, 39) which act on the membrane (47).
- A displacement machine according to claim 5, characterized in that a tubular guide sleeve (35) is inserted into a longitudinal bore (34) in the drive shaft (6), in the interior of which a lubricant feed conduit (32) is formed which is connected to a lubricant source (28) and is in connection with a lubricant space (38) on the one side of the bearing (12), wherein the guide sleeve (35) comprises a section on its outside with a smaller outside diameter, which section extends over a part of the length of said guide sleeve, which section forms a lubricant recirculation conduit (33) with the wall of the longitudinal bore (34) which is in connection on the one hand with a lubricant space (39) on the other side of the bearing (12) and with the lubricant recirculation line (43) on the other hand.
- A displacement machine according to one of the claims 1 to 6, characterized in that the lubricant supply system comprises a flow limitation arrangement (31).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CH6292007 | 2007-04-17 | ||
PCT/CH2007/000275 WO2008124950A1 (en) | 2007-04-17 | 2007-06-01 | Displacement machine according to the spiral principle |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2137412A1 EP2137412A1 (en) | 2009-12-30 |
EP2137412B1 true EP2137412B1 (en) | 2012-12-05 |
Family
ID=38922804
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP07720172A Not-in-force EP2137412B1 (en) | 2007-04-17 | 2007-06-01 | Displacement machine according to the spiral principle |
Country Status (4)
Country | Link |
---|---|
US (1) | US8051813B2 (en) |
EP (1) | EP2137412B1 (en) |
CN (1) | CN101652569B (en) |
WO (1) | WO2008124950A1 (en) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
PE20141266A1 (en) | 2011-08-16 | 2014-10-03 | Weir Floway Inc | BEARING ASSEMBLY FOR A VERTICAL TURBINE PUMP |
WO2014183204A1 (en) * | 2013-05-17 | 2014-11-20 | Victor Juchymenko | Methods and systems for sealing rotating equipment such as expanders or compressors |
FR3079886B1 (en) * | 2018-04-05 | 2020-04-24 | Pfeiffer Vacuum | DRY TYPE VACUUM PUMP |
Family Cites Families (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
AT340031B (en) | 1976-03-03 | 1977-11-25 | Hoerbiger Ventilwerke Ag | CONTROL ARRANGEMENT FOR OLE INJECTION IN A SCREW COMPRESSOR |
DE3320086A1 (en) | 1983-06-03 | 1984-12-06 | Volkswagenwerk Ag, 3180 Wolfsburg | Bearing lubricating arrangement |
DE3344015A1 (en) | 1983-12-06 | 1985-06-13 | Pierburg Gmbh & Co Kg, 4040 Neuss | Spiral or annular piston pump |
DE3347081A1 (en) | 1983-12-24 | 1985-07-04 | Pierburg Gmbh & Co Kg, 4040 Neuss | Lobed rotor pump, annular piston pump or spiral piston pump |
EP0354342B1 (en) * | 1988-08-03 | 1994-01-05 | AGINFOR AG für industrielle Forschung | Scroll-type fluid displacement machine |
JP2817751B2 (en) * | 1992-04-13 | 1998-10-30 | 三菱電機株式会社 | Scroll fluid machine |
EP0614012B1 (en) * | 1993-01-19 | 1996-09-18 | AGINFOR AG für industrielle Forschung | Scroll type positive displacement machine |
JP3286432B2 (en) * | 1993-11-29 | 2002-05-27 | 三洋電機株式会社 | Rotary scroll compressor |
DE4341225C2 (en) * | 1993-12-03 | 2000-01-05 | Wap Reinigungssysteme | pump |
JP2001041162A (en) * | 1999-07-26 | 2001-02-13 | Hitachi Ltd | Displacement fluid machinery |
US6261069B1 (en) * | 2000-03-08 | 2001-07-17 | Stanadyne Automotive Corp. | Shaft seal with pressure equalizing shuttle |
-
2007
- 2007-06-01 WO PCT/CH2007/000275 patent/WO2008124950A1/en active Application Filing
- 2007-06-01 EP EP07720172A patent/EP2137412B1/en not_active Not-in-force
- 2007-06-01 CN CN200780052596.8A patent/CN101652569B/en not_active Expired - Fee Related
-
2009
- 2009-10-13 US US12/578,164 patent/US8051813B2/en not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
US20100034682A1 (en) | 2010-02-11 |
CN101652569A (en) | 2010-02-17 |
EP2137412A1 (en) | 2009-12-30 |
CN101652569B (en) | 2012-12-12 |
WO2008124950A1 (en) | 2008-10-23 |
US8051813B2 (en) | 2011-11-08 |
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