EP0666422B1 - Bearings and drive connection for the rotors of a screw compressor - Google Patents
Bearings and drive connection for the rotors of a screw compressor Download PDFInfo
- Publication number
- EP0666422B1 EP0666422B1 EP95101024A EP95101024A EP0666422B1 EP 0666422 B1 EP0666422 B1 EP 0666422B1 EP 95101024 A EP95101024 A EP 95101024A EP 95101024 A EP95101024 A EP 95101024A EP 0666422 B1 EP0666422 B1 EP 0666422B1
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- EP
- European Patent Office
- Prior art keywords
- rotor
- rotors
- bearing
- bearings
- compressor
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
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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
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/02—Arrangements of bearings
Definitions
- the invention relates to a rotor compressor with meshing engagement between a screw-toothed rib rotor and a screw-toothed slot rotor.
- the screw rotor compressor as a positive displacement machine not only transports the pumped medium from the suction to the pressure side, but also compresses it in this way by reducing the tooth space. If the rotors or rotors rotate in the housing, they disengage at the control edge on the suction side, so that a cross section and a volume open for suction. With further rotation, the rotors come back into engagement on their control edges. The cross section of the work space moving in the axial direction is reduced to the control edge on the pressure side of the housing, at which the compressed medium is pushed out.
- Screw rotor compressors can be driven directly at the engine speed or via a built-in gear.
- Compressors with high compression ratios (final pressure / suction pressure) above about 4.0 are oil-injected into the working area on the suction side in order to increase the compression temperature limit a maximum of 100 ° C. In these machines, there is an oil film between the rotors. In contrast to compressors without oil injection, there is no need for a differential gear that protects the rotors from contact.
- the gap to the housing should be kept as small as possible in order to reduce leakages of the compressed medium.
- the narrow sealing gaps required for this are achieved by precisely adjusting the rotor position to the housing, taking into account the expected operating conditions. For safety reasons, a slightly larger gap is chosen than is theoretically necessary. This safety gap difference inevitably increases the degree of leakage and reduces the compressor efficiency.
- the rotors of the known screw rotor compressors have pins arranged on both sides, which are mounted in axial and radial bearings in the housing.
- a disadvantage of this design is the high deflection of the rotors and the simultaneous occurrence of high torsional and bending stresses on the driven rotor journal.
- the bearing pins are made as large as possible. The consequence of this is that the bearing diameter and the bearing spacing must also be chosen to be correspondingly large.
- the invention is therefore based on the object of reducing the load on the driven journals in a screw rotor compressor and giving the rotors a higher overall rigidity, reducing the sealing gaps between the end faces of the rotors and the housing parts to a minimum, thereby increasing the efficiency of the compressor increase and design a drive so that the tightness of the compressor is improved.
- the screw rotor compressor has internal rotor bearings.
- the bearing journals, hereinafter referred to as journals, for the main and secondary rotors are parts of the suction-side and pressure-side bearing housings, respectively, and therefore consist of the same material, e.g. B. Cast steel.
- the one-piece journals protrude into the bores of the rotors, which are equipped with plain or roller bearings to support the journals.
- Either axial and radial bearings on the suction side and radial bearings on the pressure side or radial bearings on the suction side and axial and radial bearings on the pressure side can be used for the bearing.
- the drive of the screw rotor compressor can be arranged on one of the rotors on the suction or pressure side.
- a torsion shaft is provided for the drive, which is guided through a bore in the suction or pressure-side bearing housing and one of the four pins.
- the compressor is driven by a coupling at the outer end of the torsion shaft.
- the torsion shaft is not loaded by bending forces, but only by torsional forces.
- sealing washers according to the invention can be used both in screw rotor compressors with the rotor mounted on the outside and in the machines according to the invention, the rotors of which are mounted on housing journals arranged inside the rotors.
- a PTFE (polytetrafluoroethylene) mica mixture is proposed as the material for the sealing washers. Sealing washers made from this extremely durable plastic-mineral mixture, known under the name Fluorsint, have already proven themselves. Of course, the proposed invention extends to any other materials or material mixtures with the same or similar properties.
- the sealing washers are screwed or glued to the suction and pressure side housing parts. They can also be inserted with a positive fit.
- the bearing housing (3) of the drive side shown in FIG. 1 is equipped on its inside with a pin (14) for engaging in the bore in the rotor (12) and with a further pin (14) for engaging in the rotor (12a).
- the pressure-side bearing housing (15) also has pins (14) on its inside. One of these pins engages in the bore in the rotor (12) and the other in the bore in the rotor (12a).
- the rotors (12, 12a) according to the invention within the compressor housing (11) only consist of the screw-toothed rib rotor and the screw-toothed slot rotor, in the ends of which central bores for receiving the pins (14) are made.
- the drive of the compressor is located on the suction side on the rotor (12), the screw-toothed rib rotor.
- the rotors (12, 12a) are supported on the pressure-side pins by radial bearings (16, 17). On the suction side, the rotors (12, 12a) are mounted on the pins (14) in radial bearings (6, 22) and axial bearings (9, 21).
- the rotor (12) is driven on the suction side by means of a torsion shaft (4).
- This torsion shaft is guided through a bore in the drive-side bearing housing (3) and the pin (14) and points on the inside End a thickening (4a), which is located in a recess in the bore.
- the thickened end (4a) of the torsion shaft (4) can be inserted into the recess in the bore when mounting the compressor.
- the drive-side bearing housing (3) is then pushed over the torsion shaft (4) and the pin (14) with the bearings (6, 9) is pushed into the rotor (12).
- a positive connection is thereby established between the torsion shaft (4) and the rotor (12).
- a shaft seal (2) for the torsion shaft (4) is arranged inside the drive-side bearing housing (3).
- the coupling flange (1) belonging to the compressor is placed on the outer end of the torsion shaft (4) and is held by a nut (23).
- FIG. 2 shows that the rotor (12) is driven on the suction side via a gear transmission.
- a gear output gear (25) can be seen on the side of the rotor (12), which engages in a gear input gear (27) with a drive shaft (26).
- the drive shaft is mounted in radial bearings (13, 18) on the inside of the gearbox of the compressor housing (11) and on the outside of the gearbox of the bearing housing (3) on the drive side.
- the inside of the drive-side bearing housing (3) is equipped with a pin (14) for engaging in the bore in the rotor (12) and with a further pin (14) for engaging in the rotor (12a).
- the pressure-side bearing housing (15) also has pins (14) on its inside. One of these pins (14) engages in the bore in the rotor (12) and the other in the bore in the rotor (12a).
- the drive-side mounting of the rotor (12) is denoted by (6,7,8,9,10), that of the rotor (12a) is denoted by (19,20,21,22).
- the bearing on the pressure side on the pins (14) of the bearing housing (15) is carried out by radial bearings (16, 17).
- the compressor drive is on the suction side of the rotor (12). This rotor is driven by a torsion shaft (4).
- the compressor-side coupling flange (1) can be seen at one end of the torsion shaft (4).
- sealing disks (5) Between the end faces of the rotors (12, 12a) arranged in the compressor housing (11) and the suction and pressure-side housing parts (3, 15) are the sealing disks (5), which are screwed to these housing parts (3, 15) in recesses, glued or inserted positively.
- These sealing washers consist of a reduced PTFE-mica mixture or of a material with similar properties.
- FIG. 4 shows in a further variant a rib rotor (12) on the drive side arranged in the compressor housing (11), which has a magnetic coupling.
- Radial (6) and axial bearings (9) are also used for the rotor bearings.
- a torsion shaft (4) is guided through a bore in the bearing housing (3) and in the pin (14) and is supported in the bearing housing (3) by means of a support bearing (28).
- the inner end of the torsion shaft (4a) is positively connected to the rotor (12).
- the compressor-side magnetic coupling half (29) On the torsion shaft (4) is the compressor-side magnetic coupling half (29), which is equipped with internal magnets (30).
- the motor-side magnetic coupling half (31) engages around the first-mentioned coupling half. It contains the external magnets (32).
- a bellows (29) is arranged between the compressor-side magnetic coupling half (29) and the motor-side magnetic coupling half (31). This can be made of a metallic material.
Description
Die Erfindung betrifft einen Rotorverdichter mit Kämmeingriff zwischen einem schraubverzahnten Rippenrotor und einem schraubverzahnten Nutenrotor.The invention relates to a rotor compressor with meshing engagement between a screw-toothed rib rotor and a screw-toothed slot rotor.
Die Entwicklung von Schraubenrotorverdichtern, d. h. zweiwelligen Drehkolbenmaschinen mit ausgeprägter Schrägverzahnung der Profile und diagonaler Durchströmung ihres Arbeitsraumes gehen bereits auf das Ende des letzten Jahrhunderts zurück. Das Grundpatent stammt von Lysholm, der erkannt hatte, daß sich mit der Schrägverzahnung eine innere Verdichtung erreichen läßt.The development of screw rotor compressors, i. H. twin-shaft rotary lobe machines with pronounced helical gearing of the profiles and diagonal flow through their working area go back to the end of the last century. The basic patent comes from Lysholm, who had recognized that an internal compression can be achieved with the helical teeth.
Der Schraubenrotorverdichter als zwangsläufig fördernde Verdrängermaschine transportiert dementsprechend das Fördermedium nicht nur von der Saug- zur Druckseite, sondern verdichtet es auch auf diesem Wege durch Verkleinerung der Zahnlückenräume. Drehen sich die Läufer bzw. Rotoren im Gehäuse, kommen sie an der saugseitigen Steuerkante außer Eingriff, so daß sich ein Querschnitt und ein Volumen zum Ansaugen öffnet. Bei weiterer Drehung kommen die Rotoren an ihren Steuerkanten wieder zum Eingriff. Der Querschnitt des in axialer Richtung sich bewegenden Arbeitsraumes verkleinert sich bis zur Steuerkante auf der Druckseite des Gehäuses, an der das komprimierte Medium ausgeschoben wird.Accordingly, the screw rotor compressor as a positive displacement machine not only transports the pumped medium from the suction to the pressure side, but also compresses it in this way by reducing the tooth space. If the rotors or rotors rotate in the housing, they disengage at the control edge on the suction side, so that a cross section and a volume open for suction. With further rotation, the rotors come back into engagement on their control edges. The cross section of the work space moving in the axial direction is reduced to the control edge on the pressure side of the housing, at which the compressed medium is pushed out.
Schraubenrotorverdichter lassen sich direkt mit der Motordrehzahl oder über ein eingebautes Getriebe antreiben.Screw rotor compressors can be driven directly at the engine speed or via a built-in gear.
Verdichter mit hohen Kompressionsverhältnissen (Enddruck/Saugdruck) über etwa 4,0 werden auf der Saugseite mit einer Öleinspritzung in den Arbeitsraum versehen, um die entstehende Kompressionstemperatur auf maximal 100 °C zu begrenzen. Bei diesen Maschinen befindet sich zwischen den Rotoren ein Ölfilm. Im Gegensatz zu Verdichtern ohne Öleinspritzung ist hier kein Ausgleichsgetriebe erforderlich, welches die Rotoren vor Berührung schützt.Compressors with high compression ratios (final pressure / suction pressure) above about 4.0 are oil-injected into the working area on the suction side in order to increase the compression temperature limit a maximum of 100 ° C. In these machines, there is an oil film between the rotors. In contrast to compressors without oil injection, there is no need for a differential gear that protects the rotors from contact.
An den Stirnseiten der Rotoren von Schraubenrotorverdichtern soll der Spalt zum Gehäuse möglichst klein gehalten werden, um Leckagen des komprimierten Mediums zu vermindern. Die dazu erforderlichen engen Dichtspalte werden durch ein genaues Einstellen der Rotorenstellung zum Gehäuse unter Berücksichtigung der zu erwartenden Betriebsbedingungen erreicht. Aus Sicherheitsgründen wird dabei ein etwas größerer Spalt gewählt als theoretisch notwendig ist. Diese Sicherheitsspaltdifferenz erhöht aber zwangsläufig den Grad der Leckage und setzt den Verdichterwirkungsgrad herab.At the end faces of the rotors of screw rotor compressors, the gap to the housing should be kept as small as possible in order to reduce leakages of the compressed medium. The narrow sealing gaps required for this are achieved by precisely adjusting the rotor position to the housing, taking into account the expected operating conditions. For safety reasons, a slightly larger gap is chosen than is theoretically necessary. This safety gap difference inevitably increases the degree of leakage and reduces the compressor efficiency.
Durch Einbau einer Spaltdichtung zwischen Rotorzapfen und Gehäuse, d. h. direkt im Anschluß an den Wirkraum der Rotoren, läßt sich die Leckagemenge zwar weiter verringern, jedoch bringt diese Maßnahme den Nachteil mit sich, daß sich die Lagerabstände weiter vergrößern.By installing a gap seal between the rotor pin and housing, i. H. directly after the effective space of the rotors, the amount of leakage can be further reduced, but this measure has the disadvantage that the bearing distances increase further.
Das Austreten von Leckmengen umweltunverträglicher Medien an der Verdichter-Antriebsseite versucht man zudem mit Hilfe anspruchsvoller Dichtungskonstruktionen gering zu halten.The leakage of environmentally unacceptable media on the compressor drive side is also tried to be kept low with the help of sophisticated seal designs.
Die Rotoren der bekannten Schraubenrotorverdichter besitzen beidseitig angeordnete Zapfen, die in Axial- und Radiallagern im Gehäuse gelagert sind.The rotors of the known screw rotor compressors have pins arranged on both sides, which are mounted in axial and radial bearings in the housing.
Nachteilig ist bei dieser Ausführung die hohe Durchbiegung der Rotoren und das gleichzeitige Auftreten von hohen Torsions- und Biegespannungen an dem angetriebenen Rotorzapfen. Um den Rotoren eine möglichst hohe Steifigkeit zu verleihen bzw. um die erforderlichen Drehmomente übertragen zu können, führt man die Lagerzapfen möglichst groß aus. Dies hat zur Folge, daß der Lagerdurchmesser und der Lagerabstand auch entsprechend groß gewählt werden muß.A disadvantage of this design is the high deflection of the rotors and the simultaneous occurrence of high torsional and bending stresses on the driven rotor journal. To the rotors one To give the highest possible rigidity or to be able to transmit the required torques, the bearing pins are made as large as possible. The consequence of this is that the bearing diameter and the bearing spacing must also be chosen to be correspondingly large.
Aus der EP-A-O 101 345 ist ein Rotorverdichter mit Kämmeingriff zwischen einem schraubverzahnten Rippenrotor und einem schraubverzahnten Nutenrotor bekannt, bei dem die saug- und druckseitigen Zapfen nicht Bestandteil der Gehäusewand der Lagergehäuse sind und aus mehreren verschraubten Teilen bestehen. In den Bereichen, in welchen große Torsions- und Biegekräfte auftreten, sind die Zapfen Bestandteil der Rotoren. Diese Zapfenteile können nicht als Torsionswelle bezeichnet werden, da sie eben diese Torsions- und Biegekräfte aufnehmen müssen.From EP-A-O 101 345 a rotor compressor with meshing engagement between a screw-toothed rib rotor and a screw-toothed slot rotor is known, in which the suction and pressure-side pins are not part of the housing wall of the bearing housing and consist of several screwed parts. In the areas where large torsional and bending forces occur, the pins are part of the rotors. These pin parts cannot be called a torsion shaft because they have to absorb these torsional and bending forces.
Der Erfindung liegt daher die Aufgabe zugrunde, bei einem Schraubenrotorverdichter die Belastung der angetriebenen Zapfen zu verkleinern und den Rotoren insgesamt eine höhere Steifigkeit zu geben, die Dichtspalte zwischen den Stirnflächen der Rotoren und den Gehäuseteilen auf ein Minimum zu reduzieren, den Wirkungsgrad des Verdichters dadurch zu erhöhen und einen Antrieb so zu gestalten, daß die Dichtigkeit des Verdichters verbessert wird.The invention is therefore based on the object of reducing the load on the driven journals in a screw rotor compressor and giving the rotors a higher overall rigidity, reducing the sealing gaps between the end faces of the rotors and the housing parts to a minimum, thereby increasing the efficiency of the compressor increase and design a drive so that the tightness of the compressor is improved.
Diese Aufgabe wird nach der Erfindung in der Weise gelöst wie es in den Patentansprüchen 1 bis 3 angegeben ist.This object is achieved according to the invention in the manner as specified in
Nach der Erfindung weist der Schraubenrotorverdichter innenliegende Rotorenlagerungen auf. Die Lagerzapfen, nachstehend Zapfen genannt, für den Haupt- und Nebenrotor sind jeweils Teile des saugseitigen bzw. des druckseitigen Lagergehäuses, bestehen also aus dem gleichen Material, z. B. Stahlguß. Die einstückigen Zapfen ragen in Bohrungen der Rotoren hinein, die zur Lagerung der Zapfen mit Gleit- oder Wälzlagern ausgerüstet sind.According to the invention, the screw rotor compressor has internal rotor bearings. The bearing journals, hereinafter referred to as journals, for the main and secondary rotors are parts of the suction-side and pressure-side bearing housings, respectively, and therefore consist of the same material, e.g. B. Cast steel. The one-piece journals protrude into the bores of the rotors, which are equipped with plain or roller bearings to support the journals.
Ein besonderer wirtschaftlicher Vorteil dieser Lagerkonstruktion ist darin zu sehen, daß der so konstruierte Rotorverdichter eine gegenüber Verdichtern des Standes der Technik extrem kurze Bauform aufweist.A particular economic advantage of this bearing construction can be seen in the fact that the rotor compressor constructed in this way has an extremely short design compared to compressors of the prior art.
Es können für die Lagerung wahlweise saugseitig Axial- und Radiallager und druckseitig Radiallager oder aber saugseitig Radiallager und druckseitig Axial- und Radiallager verwendet werden.Either axial and radial bearings on the suction side and radial bearings on the pressure side or radial bearings on the suction side and axial and radial bearings on the pressure side can be used for the bearing.
Je nach Wunsch läßt sich der Antrieb des Schraubenrotorverdichter an einem der saug- oder druckseitigen Rotoren anordnen.Depending on your requirements, the drive of the screw rotor compressor can be arranged on one of the rotors on the suction or pressure side.
Erfindungsgemäß ist für den Antrieb eine Torsionswelle vorgesehen, die durch eine Bohrung im saug- oder druckseitigen Lagergehäuse und einen der vier Zapfen geführt ist. Über eine Kupplung am äußeren Ende der Torsionswelle erfolgt der Antrieb des Verdichters. Die Torsionswelle ist nicht durch Biegekräfte belastet, sondern ausschließlich durch Torsionskräfte.According to the invention, a torsion shaft is provided for the drive, which is guided through a bore in the suction or pressure-side bearing housing and one of the four pins. The compressor is driven by a coupling at the outer end of the torsion shaft. The torsion shaft is not loaded by bending forces, but only by torsional forces.
Die Verwendung der erfindungsgemäßen Dichtscheiben läßt sich sowohl bei Schraubenrotorverdichtern mit außenliegender Lagerung der Rotoren als auch bei den erfindungsgemäßen Maschinen anwenden, deren Rotoren auf innerhalb der Rotoren angeordneten Gehäusezapfen gelagert sind.The use of the sealing washers according to the invention can be used both in screw rotor compressors with the rotor mounted on the outside and in the machines according to the invention, the rotors of which are mounted on housing journals arranged inside the rotors.
Bei der Montage des Verdichters wird für den Abstand der Rotoren-Stirnflächen zum Gehäuse ein Spaltmaß von 0 mm eingestellt. Durch Längenänderung des Gehäuses und der Rotoren infolge von Wärmedehnungen während des Betriebes werden an den Rotoren die zuvor eingesetzten Dichtscheiben so weit abtragen, wie dies für einen berührungslosen Lauf zwischen Gehäuse und Rotor erforderlich ist. Dieser geringstmögliche Spalt stellt sich bei gleicher Belastung des Verdichters immer wieder ein.When installing the compressor, a gap of 0 mm is set for the distance between the rotor end faces and the housing. By changing the length of the housing and of the rotors as a result of thermal expansion during operation, the sealing disks previously used on the rotors will be removed as far as is necessary for contactless running between the housing and the rotor. This smallest possible gap occurs again and again with the same load on the compressor.
Als Werkstoff für die Dichtscheiben wird ein PTFE (Polytetrafluoräthylen)-Glimmer-Gemisch vorgeschlagen. Dichtscheiben aus diesem äußerst beständigen Kunststoff-Mineral-Gemisch, unter dem Namen Fluorsint bekannt, haben sich bereits bewährt. Selbstverständlich erstreckt sich der Erfindungsvorschlag auch auf etwaige andere Werkstoffe oder Werkstoffgemische mit gleichen oder ähnlichen Eigenschaften.A PTFE (polytetrafluoroethylene) mica mixture is proposed as the material for the sealing washers. Sealing washers made from this extremely durable plastic-mineral mixture, known under the name Fluorsint, have already proven themselves. Of course, the proposed invention extends to any other materials or material mixtures with the same or similar properties.
Die Dichtscheiben werden an die saug- und druckseitigen Gehäuseteile angeschraubt oder angeklebt. Sie können auch formschlüssig eingelegt sein.The sealing washers are screwed or glued to the suction and pressure side housing parts. They can also be inserted with a positive fit.
Es kann auch von Vorteil sein, bei Verwendung der beschriebenen Dichtscheiben zur Erzielung engster druckseitiger Stirnspalte und zugleich höchster Wirkungsgrade die Axiallagerung der Rotoren auf der Saugseite des Verdichters anzuordnen.It can also be advantageous to use the described sealing washers to achieve the narrowest pressure-side end gaps and at the same time the highest efficiency to arrange the axial bearing of the rotors on the suction side of the compressor.
Ausführungsbeispiele der Erfindung werden nachstehend anhand von schematischen Zeichnungen näher erläutert.Exemplary embodiments of the invention are explained in more detail below with the aid of schematic drawings.
Es zeigen:
- Fig. 1
- einen Längsschnitt durch einen Schraubenrotorverdichter mit Torsionswelle,
- Fig. 2
- als Einzelheit einen Getriebeantrieb im Längsschnitt,
- Fig. 3
- einen Längsschnitt durch einen Schraubenrotorverdichter mit Torsionswelle und Dichtscheiben,
- Fig. 4
- einen Ausschnitt des Antriebes eines Schraubenrotorverdichters mit innengelagerten Rotoren.
- Fig. 1
- a longitudinal section through a screw rotor compressor with torsion shaft,
- Fig. 2
- as a detail a gear drive in longitudinal section,
- Fig. 3
- a longitudinal section through a screw rotor compressor with torsion shaft and sealing washers,
- Fig. 4
- a section of the drive of a screw rotor compressor with internally mounted rotors.
Das in Fig. 1 dargestellte Lagergehäuse (3) der Antriebsseite ist an seiner Innenseite mit einem Zapfen (14) zum Eingriff in die Bohrung im Rotor (12) und mit einem weiteren Zapfen (14) zum Eingriff in den Rotor (12a) ausgestattet.The bearing housing (3) of the drive side shown in FIG. 1 is equipped on its inside with a pin (14) for engaging in the bore in the rotor (12) and with a further pin (14) for engaging in the rotor (12a).
Das druckseitige Lagergehäuse (15) besitzt an seiner Innenseite ebenfalls Zapfen (14). Einer dieser Zapfen greift in die Bohrung im Rotor (12) und der andere in die Bohrung im Rotor (12a) ein.The pressure-side bearing housing (15) also has pins (14) on its inside. One of these pins engages in the bore in the rotor (12) and the other in the bore in the rotor (12a).
Demnach bestehen die erfindungsgemäßen Rotoren (12, 12a) innerhalb des Verdichtergehäuses (11) nur noch aus dem schraubverzahnten Rippenrotor und dem schraubverzahnten Nutenrotor, in deren Enden zentrische Bohrungen zur Aufnahme der Zapfen (14) eingebracht sind.Accordingly, the rotors (12, 12a) according to the invention within the compressor housing (11) only consist of the screw-toothed rib rotor and the screw-toothed slot rotor, in the ends of which central bores for receiving the pins (14) are made.
Im Ausführungsbeispiel gemäß Fig. 1 befindet sich der Antrieb des Verdichters saugseitig am Rotor (12), dem schraubverzahnten Rippenrotor.In the exemplary embodiment according to FIG. 1, the drive of the compressor is located on the suction side on the rotor (12), the screw-toothed rib rotor.
Die Lagerung der Rotoren (12, 12a) auf den druckseitigen Zapfen erfolgt durch Radiallager (16, 17). Saugseitig sind die Rotoren (12, 12a) in Radiallagern (6, 22) und Axiallagern (9, 21) auf den Zapfen (14) gelagert.The rotors (12, 12a) are supported on the pressure-side pins by radial bearings (16, 17). On the suction side, the rotors (12, 12a) are mounted on the pins (14) in radial bearings (6, 22) and axial bearings (9, 21).
Der Antrieb des Rotors (12) erfolgt auf der Saugseite mit Hilfe einer Torsionswelle (4). Diese Torsionswelle ist durch eine Bohrung im antriebsseitigen Lagergehäuse (3) und den Zapfen (14) geführt und weist am innenseitigen Ende eine Verdickung (4a) auf, die sich in einer Ausnehmung der Bohrung befindet. Das verdickte Ende (4a) der Torsionswelle (4) kann bei der Montage des Verdichters in die Ausnehmung der Bohrung eingesetzt werden. Anschließend wird das antriebsseitige Lagergehäuse (3) über die Torsionswelle (4) geschoben und der Zapfen (14) mit den Lagern (6, 9) in den Rotor (12) geschoben.The rotor (12) is driven on the suction side by means of a torsion shaft (4). This torsion shaft is guided through a bore in the drive-side bearing housing (3) and the pin (14) and points on the inside End a thickening (4a), which is located in a recess in the bore. The thickened end (4a) of the torsion shaft (4) can be inserted into the recess in the bore when mounting the compressor. The drive-side bearing housing (3) is then pushed over the torsion shaft (4) and the pin (14) with the bearings (6, 9) is pushed into the rotor (12).
Zwischen der Torsionswelle (4) und dem Rotor (12) wird dadurch eine formschlüssige Verbindung hergestellt. Innerhalb des antriebsseitigen Lagergehäuses (3) ist eine Wellendichtung (2) für die Torsionswelle (4) angeordnet.A positive connection is thereby established between the torsion shaft (4) and the rotor (12). A shaft seal (2) for the torsion shaft (4) is arranged inside the drive-side bearing housing (3).
Auf das äußere Ende der Torsionswelle (4) ist der zum Verdichter gehörige Kupplungsflansch (1) gesetzt, der durch eine Mutter (23) gehalten wird.The coupling flange (1) belonging to the compressor is placed on the outer end of the torsion shaft (4) and is held by a nut (23).
Als Antriebs-Alternative ist in Fig. 2 dargestellt, daß der Rotor (12) saugseitig über ein Zahnradgetriebe angetrieben wird. Ein Getriebeabtriebsrad (25) ist an der Seite des Rotors (12) erkennbar, das in ein Getriebeantriebsrad (27) mit Antriebswelle (26) eingreift. Die Antriebswelle ist in Radiallagern (13, 18) an der Getriebeinnenseite des Verdichtergehäuses (11) und der Getriebeaußenseite des antriebsseitigen Lagergehäuses (3) gelagert.2 shows that the rotor (12) is driven on the suction side via a gear transmission. A gear output gear (25) can be seen on the side of the rotor (12), which engages in a gear input gear (27) with a drive shaft (26). The drive shaft is mounted in radial bearings (13, 18) on the inside of the gearbox of the compressor housing (11) and on the outside of the gearbox of the bearing housing (3) on the drive side.
In der Mitte, unten, von Fig. 2 ist die Lagerung des Zapfens (14) in der Bohrung des Getriebeabtriebsrades (25) erkennbar, nämlich das Radiallager (6) und das Axiallager (9). Des weiteren sind Vorspannfeder (7) und Distanzring (8) dargestellt.In the middle, below, of Fig. 2, the bearing of the pin (14) in the bore of the gear driven gear (25) can be seen, namely the radial bearing (6) and the axial bearing (9). Preload spring (7) and spacer ring (8) are also shown.
Ein Ausführungsbeispiel der erfindungsgemäßen Abdichtung wird nachstehend anhand der Fig. 3 näher erläutert.An embodiment of the seal according to the invention is explained below with reference to FIG. 3.
Das antriebsseitige Lagergehäuse (3) ist an seiner Innenseite mit einem Zapfen (14) zum Eingriff in die Bohrung im Rotor (12) und mit einem weiteren Zapfen (14) zum Eingriff in den Rotor (12a) ausgestattet.The inside of the drive-side bearing housing (3) is equipped with a pin (14) for engaging in the bore in the rotor (12) and with a further pin (14) for engaging in the rotor (12a).
Das druckseitige Lagergehäuse (15) weist an seiner Innenseite ebenfalls Zapfen (14) auf. Einer dieser Zapfen (14) greift in die Bohrung im Rotor (12) und der andere in die Bohrung im Rotor (12a) ein.The pressure-side bearing housing (15) also has pins (14) on its inside. One of these pins (14) engages in the bore in the rotor (12) and the other in the bore in the rotor (12a).
Die antriebsseitige Lagerung des Rotors (12) ist mit (6,7,8,9,10), die des Rotors (12a) ist mit (19,20,21,22) bezeichnet.The drive-side mounting of the rotor (12) is denoted by (6,7,8,9,10), that of the rotor (12a) is denoted by (19,20,21,22).
Die druckseitige Lagerung an den Zapfen (14) des Lagergehäuses (15) erfolgt durch Radiallager (16, 17). Der Antrieb des Verdichters befindet sich saugseitig am Rotor (12). Dieser Rotor wird mit einer Torsionswelle (4) angetrieben. An einem Ende der Torsionswelle (4) ist der verdichterseitige Kupplungsflansch (1) erkennbar.The bearing on the pressure side on the pins (14) of the bearing housing (15) is carried out by radial bearings (16, 17). The compressor drive is on the suction side of the rotor (12). This rotor is driven by a torsion shaft (4). The compressor-side coupling flange (1) can be seen at one end of the torsion shaft (4).
Zwischen den Stirnflächen der im Verdichtergehäuse (11) angeordneten Rotoren (12, 12a) und den saug- und druckseitigen Gehäuseteilen (3, 15) befinden sich die Dichtscheiben (5), die an diese Gehäuseteile (3, 15) in Aussparungen angeschraubt, angeklebt oder formschlüssig eingelegt sind. Diese Dichtscheiben bestehen aus einem gesinderten PTFE-Glimmer-Gemisch oder aus einem Werkstoff mit ähnlichen Eigenschaften.Between the end faces of the rotors (12, 12a) arranged in the compressor housing (11) and the suction and pressure-side housing parts (3, 15) are the sealing disks (5), which are screwed to these housing parts (3, 15) in recesses, glued or inserted positively. These sealing washers consist of a reduced PTFE-mica mixture or of a material with similar properties.
Fig. 4 zeigt in einer weiteren Variante einen im Verdichtergehäuse (11) angeordneten antriebsseitigen Rippenrotor (12), der über eine Magnetkupplung verfügt. Ein Zapfen (14) am Lagergehäuse (3) greift in den Rotor (12) ein. Für die Rotorlagerung werden auch hier Radial- (6) und Axiallager (9) verwendet.4 shows in a further variant a rib rotor (12) on the drive side arranged in the compressor housing (11), which has a magnetic coupling. A pin (14) on the bearing housing (3) engages in the rotor (12). Radial (6) and axial bearings (9) are also used for the rotor bearings.
Durch eine Bohrung im Lagergehäuse (3) und im Zapfen (14) ist eine Torsionswelle (4) geführt, die im Lagergehäuse (3) mittels eines Stützlagers (28) gelagert ist. Das innere Ende der Torsionswelle (4a) ist formschlüssig mit dem Rotor (12) verbunden.A torsion shaft (4) is guided through a bore in the bearing housing (3) and in the pin (14) and is supported in the bearing housing (3) by means of a support bearing (28). The inner end of the torsion shaft (4a) is positively connected to the rotor (12).
Auf die Torsionswelle (4) ist die verdichterseitige Magnetkupplungshälfte (29), die mit Innenmagneten (30) ausgestattet ist. Die motorseitige Magnetkupplungshälfte (31) umgreift die erstgenannte Kupplungshälfte. Sie enthält die Außenmagnete (32).On the torsion shaft (4) is the compressor-side magnetic coupling half (29), which is equipped with internal magnets (30). The motor-side magnetic coupling half (31) engages around the first-mentioned coupling half. It contains the external magnets (32).
Zwischen der verdichterseitigen Magnetkupplungshälfte (29) und der motorseitigen Magnetkupplungshälfte (31) ist ein Faltenbalg (29) angeordnet. Dieser kann aus einem metallischen Werkstoff hergestellt sein.A bellows (29) is arranged between the compressor-side magnetic coupling half (29) and the motor-side magnetic coupling half (31). This can be made of a metallic material.
- 11
- Kupplungsflansch VerdichterCoupling flange compressor
- 22nd
- WellendichtungShaft seal
- 33rd
- Lagergehäuse AntriebsseiteBearing housing drive side
- 44th
- TorsionswelleTorsion shaft
- 4a4a
- Torsionswelle (Verdickung)Torsion shaft (thickening)
- 55
- DichtscheibeSealing washer
- 66
-
Radiallager Rotor 12
Radial bearing rotor 12 - 77
- VorspannfederPreload spring
- 88th
- DistanzringSpacer ring
- 99
-
Axiallager Rotor 12
Thrust bearing rotor 12 - 1010th
- WellenmutterShaft nut
- 1111
- VerdichtergehäuseCompressor housing
- 1212th
- RotorenRotors
- 12a12a
- RotorenRotors
- 1313
- Radiallager (im Lagergehäuse 3)Radial bearing (in bearing housing 3)
- 1414
- ZapfenCones
- 1515
- Lagergehäuse DruckseiteBearing housing pressure side
- 1616
-
Radiallager Rotor 12
Radial bearing rotor 12 - 1717th
-
Radiallager Rotor 12a
Radial bearing rotor 12a - 1818th
- Radiallager (im Verdichtergehäuse 11)Radial bearing (in compressor housing 11)
- 1919th
- WellenmutterShaft nut
- 2020th
- VorspannfederPreload spring
- 2121
-
Axiallager Rotor 12a
Thrust bearing rotor 12a - 2222
-
Radiallager Rotor 12
Radial bearing rotor 12 - 2323
- Muttermother
- 2424th
- SicherungsringCirclip
- 2525th
- GetriebeabtriebsradGear output gear
- 2626
- Antriebswelledrive shaft
- 2727
- GetriebeantriebsradGear drive wheel
- 2828
- StützlagerSupport bearing
- 2929
- erste Magnetkupplungshälftefirst magnetic coupling half
- 3030th
- Innenmagneten in 29Internal magnets in 29
- 3131
- zweite Magnetkupplungshälftesecond magnetic coupling half
- 3232
- Außenmagneten in 31External magnets in 31
- 3333
- FaltenbalgBellows
Claims (3)
- Rotor compressor with a comb engagement between a screw-toothed ribbed rotor (12) and a screw-toothed grooved rotor (12a), characterised in that the suction side (3) and pressure side (15) bearing casings have integral pins (14) which are a component of the wall of the bearing case (3, 15) and which project into the bores inside the rotors (12, 12a), which are provided with radial and axial bearings (6, 9, 16, 17, 21, 22) and in that a torsion bar (4) which is subjected exclusively to torsion forces, and not to bending forces, is conducted through a bore in the suction-side or pressure-side bearing casing (3, 15) and one of the four pins (14), and has a coupling flange (1) for the compressor drive; in that a shaft sealing (2) is disposed on the bearing casing side and, at the end of the bore for the torsion shaft (4) a recess is provided for the form-locking connection between the thickening (4a) of the torsion shaft (4) and the rotor (12).
- Rotor compressor according to Claim 1, characterised in that the bores in the rotors (12, 12a), have, for the pins (14), selectively, either axial bearings (9) and radial bearings (6) on the suction side and radial bearings (16,17) on the pressure side or radial bearings (16,17) on the suction side and axial bearings (9) and radial bearings (6) on the pressure side.
- Rotor compressor according to Claims 1 and 2, characterised in that between the end faces of the rotors (12, 12a) on the drive side (3) and the pressure-side casing parts (15), there are located sealing discs (5) which are screwed onto these casing parts (3,15), adhered thereto or inserted in a form-locking manner; and in that the sealing discs (5) are produced from a sintered PTFE-mica compound or from a material with similar properties.
Applications Claiming Priority (6)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE4403648 | 1994-02-05 | ||
| DE19944403649 DE4403649C2 (en) | 1994-02-05 | 1994-02-05 | Bearing and drive of the rotors of a screw compressor |
| DE4403647 | 1994-02-05 | ||
| DE19944403648 DE4403648A1 (en) | 1994-02-05 | 1994-02-05 | Screw compressor |
| DE4403649 | 1994-02-05 | ||
| DE19944403647 DE4403647A1 (en) | 1994-02-05 | 1994-02-05 | Screw compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP0666422A1 EP0666422A1 (en) | 1995-08-09 |
| EP0666422B1 true EP0666422B1 (en) | 1997-10-22 |
Family
ID=27206052
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP95101024A Expired - Lifetime EP0666422B1 (en) | 1994-02-05 | 1995-01-26 | Bearings and drive connection for the rotors of a screw compressor |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US5599176A (en) |
| EP (1) | EP0666422B1 (en) |
| JP (1) | JPH07279868A (en) |
| AU (1) | AU689829B2 (en) |
| DE (1) | DE59500818D1 (en) |
| FI (1) | FI950482A (en) |
Families Citing this family (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2376505B (en) * | 2001-06-11 | 2003-12-17 | Compair Uk Ltd | Improvements in screw compressors |
| JP4784484B2 (en) * | 2006-11-02 | 2011-10-05 | 株式会社豊田自動織機 | Electric pump |
| EP2602428B1 (en) * | 2011-12-08 | 2018-04-25 | Alfa Laval Corporate AB | Rotary positive displacement pump with fixed shafts and rotating sleeves |
| CN103277309A (en) * | 2013-06-17 | 2013-09-04 | 上海大隆机器厂有限公司 | Synchronous gear device of double-screw-rod compressor |
| CN106574539A (en) * | 2014-08-08 | 2017-04-19 | 伊顿公司 | Energy recovery device with heat dissipation mechanisms |
| WO2016157445A1 (en) * | 2015-03-31 | 2016-10-06 | 株式会社日立産機システム | Screw compressor |
| BE1022922B1 (en) * | 2015-04-17 | 2016-10-19 | Atlas Copco Airpower Naamloze Vennootschap | Compressor element for a screw compressor and screw compressor in which such compressor element is applied |
| JP6747572B2 (en) | 2017-02-20 | 2020-08-26 | ダイキン工業株式会社 | Screw compressor |
| GB2560375A (en) * | 2017-03-10 | 2018-09-12 | Edwards Ltd | Rotating machine and rotors for use therein |
| CN108757450B (en) * | 2018-05-14 | 2020-04-28 | 西安交通大学 | Screw compressor adopting sliding bearing |
| DE202018107141U1 (en) | 2018-12-13 | 2020-03-18 | Vogelsang Gmbh & Co. Kg | Rotary lobe pump with internal bearing |
| CA3186636A1 (en) * | 2020-06-10 | 2021-12-16 | Mehmet Bora KUZUCAN | Compressor |
| WO2021253060A1 (en) * | 2020-06-10 | 2021-12-16 | CILLIE, Willem, Isaac | Rotor assembly |
Family Cites Families (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1834976A (en) * | 1928-03-09 | 1931-12-08 | Patiag Patentverwertungs Und I | Rotary compressor, pump or the like |
| US3417915A (en) * | 1966-10-10 | 1968-12-24 | Albert J. Granberg | Rotary blower and timing adjustment mechanism |
| DE2115058A1 (en) * | 1970-05-13 | 1971-12-16 | VEB Kühlautomat, χ 1197 Berlin | Bearing of the rotors of screw compressors |
| DE2520667C2 (en) * | 1975-05-09 | 1984-11-29 | Allweiler Ag, 7760 Radolfzell | Screw pump |
| US4293290A (en) * | 1979-05-04 | 1981-10-06 | Crepaco, Inc. | Positive displacement rotary pump with bearings in countersunk portions of the rotors |
| FR2530742B1 (en) * | 1982-07-22 | 1987-06-26 | Dba | VOLUMETRIC SCREW COMPRESSOR |
| US4674960A (en) * | 1985-06-25 | 1987-06-23 | Spectra-Physics, Inc. | Sealed rotary compressor |
| US4797078A (en) * | 1986-06-11 | 1989-01-10 | Wankel Gmbh | Bearing arrangement of an external-axial rotary piston blower |
| JP3074829B2 (en) * | 1991-09-05 | 2000-08-07 | 松下電器産業株式会社 | Fluid rotating device |
| US5374173A (en) * | 1992-09-04 | 1994-12-20 | Matsushita Electric Industrial Co., Ltd. | Fluid rotating apparatus with sealing arrangement |
| US5449278A (en) * | 1994-11-14 | 1995-09-12 | Lin; Chi-So | Double action piston having plural annular check valves |
-
1995
- 1995-01-26 EP EP95101024A patent/EP0666422B1/en not_active Expired - Lifetime
- 1995-01-26 DE DE59500818T patent/DE59500818D1/en not_active Expired - Fee Related
- 1995-01-31 AU AU11472/95A patent/AU689829B2/en not_active Ceased
- 1995-02-03 US US08/383,247 patent/US5599176A/en not_active Expired - Fee Related
- 1995-02-03 JP JP7051660A patent/JPH07279868A/en active Pending
- 1995-02-03 FI FI950482A patent/FI950482A/en unknown
Also Published As
| Publication number | Publication date |
|---|---|
| FI950482A0 (en) | 1995-02-03 |
| AU1147295A (en) | 1995-08-17 |
| DE59500818D1 (en) | 1997-11-27 |
| US5599176A (en) | 1997-02-04 |
| FI950482A (en) | 1995-08-06 |
| EP0666422A1 (en) | 1995-08-09 |
| JPH07279868A (en) | 1995-10-27 |
| AU689829B2 (en) | 1998-04-09 |
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