[go: up one dir, main page]

EP0077031B1 - Rotary piston compressor - Google Patents

Rotary piston compressor Download PDF

Info

Publication number
EP0077031B1
EP0077031B1 EP82109274A EP82109274A EP0077031B1 EP 0077031 B1 EP0077031 B1 EP 0077031B1 EP 82109274 A EP82109274 A EP 82109274A EP 82109274 A EP82109274 A EP 82109274A EP 0077031 B1 EP0077031 B1 EP 0077031B1
Authority
EP
European Patent Office
Prior art keywords
rotor
main rotor
main
piston compressor
head
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP82109274A
Other languages
German (de)
French (fr)
Other versions
EP0077031A1 (en
Inventor
Beteiligungsgesellschaft Mbh Technika
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Priority to AT82109274T priority Critical patent/ATE14916T1/en
Publication of EP0077031A1 publication Critical patent/EP0077031A1/en
Application granted granted Critical
Publication of EP0077031B1 publication Critical patent/EP0077031B1/en
Expired legal-status Critical Current

Links

Images

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
    • 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
    • F04C18/082—Details specially related to intermeshing engagement type pumps
    • F04C18/084—Toothed wheels
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19949—Teeth
    • Y10T74/19953—Worm and helical

Definitions

  • the invention relates to a parallel and external axis rotary compressor with at least one helically toothed main rotor and in each case a secondary rotor meshing therewith.
  • Such a rotary compressor is e.g. B. known from DE-OS 2505113.
  • the published publication deals in particular with the formation of the tooth flanks of the secondary rotor, in order to avoid the blow hole of the compressor toothing present in rotary lobe compressors, which arises from the fact that the line of contact, along which the tooth flanks of one tooth of the main and secondary rotor of an engaged pair of teeth lie against one another down to the edge of the housing, which is the intersection of the two housing bores, (see also Rinder, Springer-Verlag Vienna, New York, 1979, p. 72 ff.).
  • US Pat. No. 2,622,787 is concerned with reducing the leakage caused by the blow hole.
  • the rotors of screw compressors - in order to keep leakages as small as possible - have to be manufactured with the greatest precision, which requires complex and expensive tools and machine tools. Due to the complicated design of the individual profiles, separate milling cutters are required, whereby the manufacture of a rotor usually requires several work steps (pre-milling with so-called roughing cutters and then finishing with finishing or fine milling cutters). A cutter set for a pair of rotors costs between DM 20,000 and 50,000, depending on the diameter. In addition, there is the effort for the necessary final checks.
  • Rotary lobe compressors with different delivery volumes are commercially available in order to meet the respective desired requirements. Accordingly, the manufacturers offer compressor series in which the distance between the stages is chosen to be relatively large because of the expensive production, so that too many expensive tools do not have to be manufactured and kept in stock. The consequence of this is that the individual rotary compressor types in a series are not operated directly in their optimum range or in the vicinity of the optimum range, but rather over a larger range.
  • 1 shows the specific power consumption in (kW / m 3 / min) over the delivery volume (m 3 / min).
  • the circumferential speed of a rotor or its speed could also be plotted on the abscissa; the qualitative statement would not change here.
  • the optimum operating point is - as can be seen from FIG.
  • the rotary lobe compressors currently on the market run in the BAC range, i.e. not exclusively in or close to the optimal range, which would be around B 'AC', in order to allow the flow rate of one type to be connected as seamlessly as possible to that of the next larger type.
  • the expansion of the flow rate range for each type must be achieved by changing the speed by means of a transmission gear (belt or gear drives or by speed control of the drive motor). If you wanted to operate the rotary lobe compressors in area B 'AC', the delivery volume would have to be reduced. However, as indicated above, this would again require a larger number of rotary lobe compressor types and thus a larger number of expensive tools.
  • the object of the invention is to provide a rotary compressor of the type mentioned, which is simple to manufacture and which requires relatively inexpensive tools for producing the profiles. Furthermore, the dimensional control should be able to be carried out precisely, inexpensively and simply.
  • tooth flanks of the main rotor are layered circle screw surfaces which are generated by screwing a circle whose plane is perpendicular to the screw axis.
  • a further advantageous embodiment of the invention can be such that the tooth flanks of the secondary rotor are generated and determined by the relative path of a point lying on a head line (main rotor head point) during the rolling of the main rotor and secondary rotor.
  • the main rotor advantageously has at least three teeth.
  • the tooth flanks of the main rotor are not composed of curve segments, but are formed by a constant, uniformly analytically definable curve shape from head point to head point, in this case circular arcs, because of the generating circles.
  • the tooth flanks here are stratified circle screw surfaces, the generating circles of which are (see also Wunderlich, Representative Geometry, Vol. 2 of the B.I. series, University Pocket Books, Vol. 133, 1967, p. 188 ff.).
  • the flanks of the teeth are produced by a hobbing process using a profile milling cutter. Such a profile cutter is one with a curved one. Surface line, which can be designed according to the shape of the forehead.
  • the tooth flanks of the secondary rotor are formed by a wheel curve, which can be produced with a profile cutter with an arc-like shape.
  • a rotary lobe compressor series can be offered with a significantly more sophisticated gradation compared to known compressor series. It is possible to optimize the efficiency of the individual rotary lobe compressors in the series by choosing the optimum circumferential speeds in the absence of gears (gears and pinions or belts, adapted to the standard electrical speed of the drive, which is designed as an electric motor, for example).
  • the individual rotary compressor can be operated in direct drive in the area B 'AC' (Fig. 1), so that the optimum working area can be used.
  • the geometry of the manufactured rotor is also much easier to measure, which, as mentioned above, makes the final inspection less expensive.
  • the individual rotary compressor of such a series can be driven directly without the interposition of an intermediate gear, so that an improvement in efficiency can be achieved in this way alone.
  • a further advantage of the configuration according to the invention also consists in the following: in known rotors, the tooth depth, ie the groove depth between two adjacent head lines, is large. As a result, the ratio of core diameter to outer diameter is also large. In known rotors, this value is - tween 0.4 to 0.5. In the rotor according to the invention, however, which is defined by the features of the characterizing part of claim 1, the ratio of core diameter to outer diameter is approximately 0.95.
  • the deflections to be expected in the main rotor according to the invention are therefore practically zero in comparison with the known main rotors. As a result, the tolerances can be kept very small and the individual main rotor is also very robust. Due to these tolerances, the efficiency can be further improved.
  • the rotary piston compressor which is generally designated 10, has a compression chamber 14 in a housing 12, in which a main rotor 16 and a secondary rotor 18 meshing therewith are arranged.
  • the main rotor 16 has at one end an extension 24 divided into two areas 20 and 22 with different diameters, of which one area 20 with a larger diameter of the bearing by means of roller bearings 26 and the other area 22 with a smaller diameter for connecting a drive, not shown serves.
  • the bearing 26 is located in a bearing recess 28 in a bearing disk 30 which is fixedly connected to the housing 12 together with an end cover 32 via a screw connection 34.
  • a sealing ring 36 is provided to seal the bearing 26 to the outside.
  • the main rotor 16 has a further journal 38 which is mounted in a roller bearing 40 and in a ball bearing 42 in a first bearing opening 44 of the housing 12.
  • the bearings 40 and 42 are held on the inside by means of a nut 46 screwed onto the bearing pin 38 and on the outside by means of a compression spring 48 which is supported on a second end cover 50, which is firmly connected to the housing by means of screw bolts 52, with the interposition of a fixing sleeve 53 .
  • the secondary rotor 18 has a bearing journal 54 and 56 on the end face, of which the bearing journal 54 is supported in a roller bearing 58 in the bearing washer 30 and the bearing journal 56 in a roller bearing 60 and a ball bearing 62 in a second bearing opening 64 in the housing 12 .
  • the bearings 60 and 62 are held or axially fixed on the inner diameter or on the inner ring of the bearings by means of a nut 66 screwed onto the bearing journal 56 and on the outside of the bearing outer ring via a compression spring 68 with the interposition of a fixing sleeve 70.
  • the reference number 72 denotes the fillet line of the main rotor and the reference number 74 the dashed line of the secondary rotor.
  • the reference numbers 76 and 78 denote the top lines of the main and secondary rotors.
  • FIG. 3 shows a cross section along line AB of FIG. 2.
  • the main rotor 16 has a total of four teeth, the head points of which are represented by the reference numbers 80, 82, 84 and 86 in the section according to FIG. 3.
  • the teeth of the main rotor are formed by screwing a circle with the radius of the projection of the fillet screw line onto a plane perpendicular to the screw axis; the " screw deflection" is selected according to the radius of the head line.
  • the main rotor is manufactured using a hobbing process with a profiled milling cutter.
  • the secondary rotor 18 has nine teeth (which are not numbered in detail), wherein, as can be seen from FIGS. 4 to 7, the tooth flanks between the teeth are determined by the relative path of the head points 80 to 84 of the main rotor 16.
  • the secondary rotor tooth flanks in the case of pointed secondary rotor teeth are not circles, but intertwined epitrochoids, which, however, can be approximately replaced by their circles of curvature during manufacture, that is, by arcs.
  • FIG. 4 shows a first position of the main rotor and the secondary rotor relative to one another, in which the head point 82 of the main rotor 16 in the position shown, ie. H. the center point of the head point lies exactly on the connecting line V-V of the central axes of the rotors.
  • the head point 82 is also aligned with the throat point 82 'of the secondary rotor 18, which is also on the connecting line between the center points of the two rotors.
  • the center line of the head and the center of the throat coincide.
  • the head points 88 and 90 of the secondary rotor 18 lie exactly on the tooth flank of the tooth which has the head point 82.
  • the head point center line with the head point 82 moves clockwise, the head point 82 running exactly on the tooth flank of the secondary rotor in such a way that the tooth flank of the secondary rotor passes through the Path of the head point 82 is determined.
  • the head point 90 of the secondary rotor 18 is still on the other tooth flank.
  • the throat center line of the secondary rotor 18 has migrated counterclockwise by a smaller amount in accordance with the speed ratio between the main rotor and the secondary rotor from the connecting line of the center points of the two rotors.
  • the head point 82 of the main rotor is located in the region of the head point 88 of the secondary rotor, the head point 90 still lying on the tooth flank of the main rotor.
  • FIG. 7 it can be seen that the head point 82 has come free from the secondary rotor, but the head point 90 still remains on the tooth flank.
  • the head point 84 comes into engagement with the secondary rotor, and the sequence or the geometry is the same as in FIGS. 4 to 7: the tooth flanks of the secondary rotor are formed by the respective head point of the main rotor, when if a head point of the main rotor is located between two head points of the secondary rotor, the two mentioned head points rest on the tooth flank or the tooth flanks of the main rotor.
  • tooth flanks of the secondary rotor are formed by the head point of the main rotor in the case of pointed secondary rotor teeth, an explicit calculation of the tooth flanks of the secondary rotor, which can be regarded as a convoluted wheel line, is possible by calculation with electronic data processing.
  • blow hole is practically zero due to the profile shape of the main and secondary rotor.
  • profile shape is also particularly advantageously suitable for small delivery volumes, where even the smallest leakage can lead to a significant reduction in efficiency.

Landscapes

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

Abstract

A parallel and outer axial rotating piston compressor comprises at least one driven helical main rotor and one auxiliary rotor meshing therewith. The main rotor includes tooth surfaces comprising layered circular helicoids defined by the helical generation of a circle whose plane is perpendicular to the rotor axis.

Description

Die Erfindung betrifft einen parallel- und aussenachsigen Drehkolbenverdichter mit mindestens einem schräg verzahnten Hauptrotor und jeweils einem damit kämmenden Nebenrotor.The invention relates to a parallel and external axis rotary compressor with at least one helically toothed main rotor and in each case a secondary rotor meshing therewith.

Ein derartiger Drehkolbenverdichter ist z. B. aus der DE-OS 2505113 bekannt geworden. Die Offenlegungsschrift befasst sich insbesondere mit der Ausbildung der Zahnflanken des Nebenrotors, um das bei Drehkolbenverdichtern vorhandene Blasloch der Verdichterverzahnung, das dadurch entsteht, dass die Berührungslinie, längs derer die Zahnflanken jeweils eines Zahnes von Haupt- und Nebenrotor eines in Eingriff stehenden Zahnpaares aneinanderliegen, nicht bis zur Gehäusekante, die als Schnitt der beiden Gehäusebohrungen entsteht, reicht (siehe auch Rinder, Springer-Verlag Wien, New York, 1979, S. 72 ff.), möglichst klein zu halten.Such a rotary compressor is e.g. B. known from DE-OS 2505113. The published publication deals in particular with the formation of the tooth flanks of the secondary rotor, in order to avoid the blow hole of the compressor toothing present in rotary lobe compressors, which arises from the fact that the line of contact, along which the tooth flanks of one tooth of the main and secondary rotor of an engaged pair of teeth lie against one another down to the edge of the housing, which is the intersection of the two housing bores, (see also Rinder, Springer-Verlag Vienna, New York, 1979, p. 72 ff.).

In ähnlicher Weise befasst sich auch die US-PS 2622787 mit der Verminderung der aufgrund des Blasloches entstehenden Leckage.Similarly, US Pat. No. 2,622,787 is concerned with reducing the leakage caused by the blow hole.

Diese und andere bekannte Drehkolbenverdichter besitzen symmetrische oder asymmetrische Zahnprofile, die aus unterschiedlich bemessenen Kurvensegmenten zusammengesetzt und mathematisch häufig nicht einheitlich definierbar sind. Im allgemeinen sind die Zähne tief eingeschnitten, siehe auch Rinder, Schraubenverdichter, S. 28, Abb. 11, wo die Konstruktion und der Aufbau eines asymmetrischen Rotorprofiles näher beschrieben ist.These and other known rotary lobe compressors have symmetrical or asymmetrical tooth profiles, which are composed of differently dimensioned curve segments and often cannot be defined mathematically uniformly. In general, the teeth are deeply cut, see also Cattle, Screw Compressor, p. 28, Fig. 11, where the construction and construction of an asymmetrical rotor profile is described in more detail.

Die Rotoren von Schraubenverdichtern müssen - um die Leckagen möglichst klein zu halten - mit grösster Präzision hergestellt werden, wozu aufwendige und teure Werkzeuge und Werkmaschinen erforderlich sind. Aufgrund der komplizierten Gestaltung der einzelnen Profile sind eigene Fräser erforderlich, wobei die Herstellung eines Rotors meist mehrere Arbeitsgänge (Vorfräsen mit sogenannten Schruppfräsern und danach Finishing mit Schlicht- oder Feinfräsern) erfordert. So kostet ein Fräsersatz für ein Rotorpaar je nach Durchmesser zwischen DM 20000.- bis 50000.-. Hinzu kommtder Aufwand für die notwendigen Endkontrollen.The rotors of screw compressors - in order to keep leakages as small as possible - have to be manufactured with the greatest precision, which requires complex and expensive tools and machine tools. Due to the complicated design of the individual profiles, separate milling cutters are required, whereby the manufacture of a rotor usually requires several work steps (pre-milling with so-called roughing cutters and then finishing with finishing or fine milling cutters). A cutter set for a pair of rotors costs between DM 20,000 and 50,000, depending on the diameter. In addition, there is the effort for the necessary final checks.

Im Handel erhältlich sind Drehkolbenverdichter mit unterschiedlichem Fördervolumen, um den jeweiligen gewünschten Bedarf zu befriedigen. Dementsprechend bieten die Hersteller Verdichterreihen an, bei denen der Abstand zwischen den Stufen wegen der teuren Herstellung relativ gross gewählt wird, damit nicht zu viele teure Werkzeuge hergestellt und auf Lager gehalten werden müssen. Dies hat zur Folge, dass die einzelnen Drehkolbenverdichtertypen einer Reihe nicht unmittelbar in ihrem optimalen Bereich oder in der Nähe des optimalen Bereiches, sondern über einen grösseren Bereich hinweg betrieben werden. In der Fig. 1 ist die spezifische Leistungsaufnahme in (kW/m3/min) über dem Fördervolumen (m3/min) aufgetragen. Dabei könnte auf der Abzisse auch die Umfangsgeschwindigkeit eines Rotors oder dessen Drehzahl aufgetragen sein; an der qualitativen Aussage würde sich hierbei nichts ändern. Der optimale Betriebspunkt liegt - wie aus der Fig. 1 ersichtlich ist - beim spezifischen Kraftbedarfsminimum, also beim Punkt A der eingezeichneten Kurve. Die derzeit auf dem Markt befindlichen Drehkolbenverdichter laufen im Bereich BAC, also nicht ausschliesslich im oder nahe am optimalen Bereich, der etwa bei B' AC' liegen würde, um den Fördervolumenstrom einer Type möglichst lückenlos an den der nächstgrösseren Type anschliessen zu lassen. Die Ausweitung des Fördermengenbereiches je einer Type muss durch Drehzahländerung mittels Übersetzungsgetriebes (Riemen- oder Zahnradgetrieben oder mittels Drehzahlregelung des Antriebsmotores) erzielt werden. Wollte man die Drehkolbenverdichter im Bereich B' AC' betreiben, müsste die Fördervolumenstufung verringert werden. Hierdurch müsste aber-wie oben angedeutet-wiederum eine grössere Anzahl von Drehkolbenverdichtertypen und damit wieder eine grössere Anzahl von teuren Werkzeugen erforderlich werden.Rotary lobe compressors with different delivery volumes are commercially available in order to meet the respective desired requirements. Accordingly, the manufacturers offer compressor series in which the distance between the stages is chosen to be relatively large because of the expensive production, so that too many expensive tools do not have to be manufactured and kept in stock. The consequence of this is that the individual rotary compressor types in a series are not operated directly in their optimum range or in the vicinity of the optimum range, but rather over a larger range. 1 shows the specific power consumption in (kW / m 3 / min) over the delivery volume (m 3 / min). The circumferential speed of a rotor or its speed could also be plotted on the abscissa; the qualitative statement would not change here. The optimum operating point is - as can be seen from FIG. 1 - at the specific power requirement minimum, that is at point A of the curve shown. The rotary lobe compressors currently on the market run in the BAC range, i.e. not exclusively in or close to the optimal range, which would be around B 'AC', in order to allow the flow rate of one type to be connected as seamlessly as possible to that of the next larger type. The expansion of the flow rate range for each type must be achieved by changing the speed by means of a transmission gear (belt or gear drives or by speed control of the drive motor). If you wanted to operate the rotary lobe compressors in area B 'AC', the delivery volume would have to be reduced. However, as indicated above, this would again require a larger number of rotary lobe compressor types and thus a larger number of expensive tools.

Aufgabe der Erfindung ist es, einen Drehkolbenverdichter der eingangs genannten Art zu schaffen, der in der Herstellung einfach ist und bei dem relativ preiswerte Werkzeuge zur Herstellung der Profile erforderlich sind. Ferner soll die Masskontrolle exakt, preiswert und einfach vorgenommen werden können.The object of the invention is to provide a rotary compressor of the type mentioned, which is simple to manufacture and which requires relatively inexpensive tools for producing the profiles. Furthermore, the dimensional control should be able to be carried out precisely, inexpensively and simply.

Diese Aufgabe wird erfindungsgemäss dadurch gelöst, dass die Zahnflanken des Hauptrotors Schichtenkreisschraubflächen sind, die durch die Verschraubung eines Kreises, dessen Ebene senkrecht zur Schraubachse steht, erzeugt sind.This object is achieved according to the invention in that the tooth flanks of the main rotor are layered circle screw surfaces which are generated by screwing a circle whose plane is perpendicular to the screw axis.

Eine weitere vorteilhafte Ausgestaltung der Erfindung kann dahin gehen, dass die Zahnflanken des Nebenrotors von der Relativbahn eines auf einer Kopflinie liegenden Punktes (Hauptrotorkopfpunkt) während des Abrollens von Hauptrotor und Nebenrotor erzeugt und bestimmt sind.A further advantageous embodiment of the invention can be such that the tooth flanks of the secondary rotor are generated and determined by the relative path of a point lying on a head line (main rotor head point) during the rolling of the main rotor and secondary rotor.

In vorteilhafter Weise besitzt der Hauptrotor mindestens drei Zähne.The main rotor advantageously has at least three teeth.

Bei dem gewählten erfindungsgemässen Profil sind die Zahnflanken des Hauptrotors nicht aus Kurvensegmenten zusammengesetzt, sondern wegen der erzeugenden Kreise durch eine stetige gleichmässige analytisch definierbare Kurvenform von Kopfpunkt zu Kopfpunkt gebildet, in diesem Falle Kreisbögen. Die Zahnflanken sind hierbei Schichtenkreisschraubflächen, deren Erzeugende Kreise sind (vgl. hierzu Wunderlich, darstellende Geometrie, Bd. 2 der Reihe B.I., Hochschultaschenbücher, Bd. 133,1967, S. 188 ff.). Die Flanken der Zähne werden durch einen Wälzfräsvorgang mit einem Profilfräser hergestellt. Ein derartiger Profilfräser ist ein solcher mit einer geschwungenen. Mantellinie, die entsprechend der Stirnschnittform ausgebildet sein kann.In the chosen profile according to the invention, the tooth flanks of the main rotor are not composed of curve segments, but are formed by a constant, uniformly analytically definable curve shape from head point to head point, in this case circular arcs, because of the generating circles. The tooth flanks here are stratified circle screw surfaces, the generating circles of which are (see also Wunderlich, Representative Geometry, Vol. 2 of the B.I. series, University Pocket Books, Vol. 133, 1967, p. 188 ff.). The flanks of the teeth are produced by a hobbing process using a profile milling cutter. Such a profile cutter is one with a curved one. Surface line, which can be designed according to the shape of the forehead.

Aufgrund der Wahl des Profiles des Hauptrotors werden die Zahnflanken des Nebenrotors durch eine Radkurve gebildet, die mit einem Profilfräser mit kreisbogenähnlicher Form hergestellt werden kann.Due to the choice of the profile of the main rotor, the tooth flanks of the secondary rotor are formed by a wheel curve, which can be produced with a profile cutter with an arc-like shape.

Die Vorteile der erfindungsgemässen Ausgestaltung bestehen somit insbesondere darin, dass die Herstellung sowohl des Hauptrotors als auch des Nebenrotors vereinfacht und damit insgesamt verbilligt wird. Auch die Masskontrolle bei der Endkontrolle wird vereinfacht, weil die Kurven der Profile des Haupt- und Nebenrotors viel einfacher zu beschreiben sind als die der bekannten Profile. Es wird ferner auch die Zerspanungsarbeit geringer.The advantages of the configuration according to the invention thus consist in particular in that the manufacture of both the main rotor and the secondary rotor is simplified and therefore cheaper overall. The dimensional control during the final inspection is also simplified because the curves of the profiles of the main and secondary rotors are much easier to describe than those of the known profiles. The cutting work is also reduced.

Infolge der geringeren Werkzeugkosten und der einfachen Geometrie ist darüber hinaus eine grosse Typenvielfalt möglich, so dass eine Drehkolbenverdichterreihe mit im Vergleich zu bekannten Verdichterreihen deutlich verfeinerter Abstufung angeboten werden kann. Dabei ist eine Optimierung des Wirkungsgrades des einzelnen Drehkolbenverdichters der Reihe möglich, in dem optimale Umfangsgeschwindigkeiten bei Wegfall von Getrieben (Zahnrädern und Ritzeln oder Bändern, angepasst an die elektrische Normdrehzahl des beispielsweise als Elektromotor ausgebildeten Antriebes), gewählt werden können. Der einzelne Drehkolbenverdichter kann dabei im Direktantrieb im Bereich B' AC' (Fig. 1) betrieben werden, so dass dadurch der optimale Arbeitsbereich ausgenutzt werden kann.As a result of the lower tool costs and the simple geometry, a large variety of types is also possible, so that a rotary lobe compressor series can be offered with a significantly more sophisticated gradation compared to known compressor series. It is possible to optimize the efficiency of the individual rotary lobe compressors in the series by choosing the optimum circumferential speeds in the absence of gears (gears and pinions or belts, adapted to the standard electrical speed of the drive, which is designed as an electric motor, for example). The individual rotary compressor can be operated in direct drive in the area B 'AC' (Fig. 1), so that the optimum working area can be used.

Durch die Vereinfachung des Profiles ist auch die Geometrie des gefertigten Rotors wesentlich einfacher zu messen, wodurch-wie oben erwähnt - die Endkontrolle verbilligt werden kann. Wie oben erwähnt, kann der einzelne Drehkolbenverdichter einer solchen Reihe direkt ohne Zwischenfügung eines Zwischengetriebes angetrieben werden, so dass schon hierdurch eine Wirkungsgradverbesserung erzielt werden kann.By simplifying the profile, the geometry of the manufactured rotor is also much easier to measure, which, as mentioned above, makes the final inspection less expensive. As mentioned above, the individual rotary compressor of such a series can be driven directly without the interposition of an intermediate gear, so that an improvement in efficiency can be achieved in this way alone.

Ein weiterer Vorteil der erfindungsgemässen Ausgestaltung besteht auch im folgenden: bei bekannten Rotoren ist die Zahntiefe, d. h. die N uttiefe zwischen zwei benachbarten Kopflinien gross. Dies hat zur Folge, dass das Verhältnis Kerndurchmesser zu Aussendurchmesser ebenfalls gross ist. Bei bekannten Rotoren beträgt dieser Wert zwi- schen 0,4 bis 0,5. Bei dem erfindungsgemässen Rotor jedoch, der durch die Merkmale des kennzeichnenden Teiles des Anspruches 1 definiert ist, liegt das Verhältnis Kerndurchmesser zu Aussendurchmesser etwa bei 0,95. Damit sind die zu erwartenden Durchbiegungen bei dem erfindungsgemässen Hauptrotor im Vergleich zu den bekannten Hauptrotoren praktisch 0. Dadurch können die Toleranzen sehr klein gehalten werden und ferner ist der einzelne Hauptrotor sehr robust. Aufgrund dieser Toleranzen kann der Wirkungsgrad zusätzlich noch verbessert werden.A further advantage of the configuration according to the invention also consists in the following: in known rotors, the tooth depth, ie the groove depth between two adjacent head lines, is large. As a result, the ratio of core diameter to outer diameter is also large. In known rotors, this value is - tween 0.4 to 0.5. In the rotor according to the invention, however, which is defined by the features of the characterizing part of claim 1, the ratio of core diameter to outer diameter is approximately 0.95. The deflections to be expected in the main rotor according to the invention are therefore practically zero in comparison with the known main rotors. As a result, the tolerances can be kept very small and the individual main rotor is also very robust. Due to these tolerances, the efficiency can be further improved.

Anhand der Zeichnung, in der ein Ausführungsbeispiel der Erfindung dargestellt ist, sollen die Erfindung sowie weitere vorteilhafte Ausgestaltungen und Verbesserungen der Erfindung näher erläutert und beschrieben werden. Es zeigt:

  • Fig. 1 ein Diagramm, bei dem der spezifische Energiebedarf in kW/m3/min über der Fördermenge m3/min aufgetragen ist,
  • Fig. 2 einen Längsschnitt durch einen erfindungsgemässen Drehkolbenverdichter,
  • Fig. 3 eine Schnittansicht gemäss Linie 111-111 der Fig. 1,
  • Fig. 4 bis 7 je eine Darstellung der Zuordnung von Haupt- und Nebenrotor in unterschiedlichen Stellungen zueinander.
Based on the drawing, in which an embodiment of the invention is shown, the invention and further advantageous refinements and improvements of the invention are to be explained and described in more detail. It shows:
  • 1 is a diagram in which the specific energy requirement in kW / m 3 / min is plotted against the delivery rate m 3 / min,
  • 2 shows a longitudinal section through a rotary piston compressor according to the invention,
  • 3 shows a sectional view along line 111-111 of FIG. 1,
  • 4 to 7 each show the assignment of the main and secondary rotors to one another in different positions.

Es sei zunächst Bezug genommen auf die Fig. 2. Der Drehkolbenverdichter, der im allgemeinen mit 10 bezeichnet ist, besitzt in einem Gehäuse 12 einen Verdichtungsraum 14, in dem ein Hauptrotor 16 und ein damit kämmender Nebenrotor 18 angeordnet sind. Der Hauptrotor 16 besitzt an einem Ende einen in zwei Bereichen 20 und 22 mit unterschiedlichen Durchmessern unterteilten Fortsatz 24, von denen der eine Bereich 20 mit grösserem Durchmesser der Lagerung mittels Wälzlagern 26 und der andere Bereich 22 mit kleinerem Durchmesser zum Anschluss eines nicht weiter dargestellten Antriebes dient. Das Lager 26 befindet sich in einer Lagerausnehmung 28 in einer Lagerscheibe 30, die mit dem Gehäuse 12 zusammen mit einem Abschlussdeckel 32 über eine Schraubverbindung 34 fest verbunden ist. ZurAbdichtung des Lagers 26 nach aussen ist ein Dichtring 36 vorgesehen.Reference is first made to FIG. 2. The rotary piston compressor, which is generally designated 10, has a compression chamber 14 in a housing 12, in which a main rotor 16 and a secondary rotor 18 meshing therewith are arranged. The main rotor 16 has at one end an extension 24 divided into two areas 20 and 22 with different diameters, of which one area 20 with a larger diameter of the bearing by means of roller bearings 26 and the other area 22 with a smaller diameter for connecting a drive, not shown serves. The bearing 26 is located in a bearing recess 28 in a bearing disk 30 which is fixedly connected to the housing 12 together with an end cover 32 via a screw connection 34. A sealing ring 36 is provided to seal the bearing 26 to the outside.

Am gegenüberliegenden Ende besitzt der Hauptrotor 16 einen weiteren Lagerzapfen 38, der in einem Wälzlager 40 und in einem Kugellager 42 in einer ersten Lageröffnung 44 des Gehäuses 12 gelagert ist. Die Halterung der Lager 40 und 42 erfolgt innen über eine auf dem Lagerzapfen 38 aufgeschraubte Mutter 46 und aussen über eine Druckfeder 48, die sich an einem zweiten Abschlussdeckel 50, der mit dem Gehäuse über Schraubenbolzen 52 fest verbunden ist, unter Zwischenfügung einer Fixierhülse 53 abstützt.At the opposite end, the main rotor 16 has a further journal 38 which is mounted in a roller bearing 40 and in a ball bearing 42 in a first bearing opening 44 of the housing 12. The bearings 40 and 42 are held on the inside by means of a nut 46 screwed onto the bearing pin 38 and on the outside by means of a compression spring 48 which is supported on a second end cover 50, which is firmly connected to the housing by means of screw bolts 52, with the interposition of a fixing sleeve 53 .

In ähnlicher Weise besitzt der Nebenrotor 18 stirnseitig je einen Lagerzapfen 54 und 56, von denen der Lagerzapfen 54 in einem Wälzlager 58 in der Lagerscheibe 30 und der Lagerzapfen 56 in einem Wälzlager 60 und einem Kugellager 62 in einer zweiten Lageröffnung 64 im Gehäuse 12 aufgelagert ist. Die Halterung bzw. axiale Fixierung der Lager 60 und 62 erfolgt am Innendurchmesser bzw. am Innenring der Lager mittels einer auf den Lagerzapfen 56 aufgeschraubten Mutter 66 und aussen am Lageraussenring über eine Druckfeder 68 unter Zwischenfügung einer Fixierhülse 70.In a similar manner, the secondary rotor 18 has a bearing journal 54 and 56 on the end face, of which the bearing journal 54 is supported in a roller bearing 58 in the bearing washer 30 and the bearing journal 56 in a roller bearing 60 and a ball bearing 62 in a second bearing opening 64 in the housing 12 . The bearings 60 and 62 are held or axially fixed on the inner diameter or on the inner ring of the bearings by means of a nut 66 screwed onto the bearing journal 56 and on the outside of the bearing outer ring via a compression spring 68 with the interposition of a fixing sleeve 70.

Mit der Bezugsziffer 72 ist die -...-dargestellte Kehllinie des Hauptrotors und mit der Bezugsziffer 74 die strichliert dargestellte Linie des Nebenrotors bezeichnet. Die Bezugsziffern 76 und 78 bezeichnen die Kopflinien des Haupt- bzw. Nebenrotors.The reference number 72 denotes the fillet line of the main rotor and the reference number 74 the dashed line of the secondary rotor. The reference numbers 76 and 78 denote the top lines of the main and secondary rotors.

In der Fig. 3 ist ein Querschnitt gemäss der Linie A-B der Fig. 2 dargestellt. Der Hauptrotor 16 besitzt insgesamt vier Zähne, deren Kopfpunkte in dem Schnitt gemäss Fig. 3 durch die Bezugsziffern 80, 82, 84 und 86 dargestellt sind. Die Zähne des Hauptrotors sind durch eine Verschraubung eines Kreises mit dem Radius der Projektion der Kehlschraublinie auf eine Ebene senkrecht zur Schraubachse gebildet; dabei ist der "Schraub- ausschlag" entsprechend dem Radius der Kopflinie gewählt.3 shows a cross section along line AB of FIG. 2. The main rotor 16 has a total of four teeth, the head points of which are represented by the reference numbers 80, 82, 84 and 86 in the section according to FIG. 3. The teeth of the main rotor are formed by screwing a circle with the radius of the projection of the fillet screw line onto a plane perpendicular to the screw axis; the " screw deflection" is selected according to the radius of the head line.

Die Herstellung des Hauptrotors erfolgt mittels eines Wälzfräsvorganges mit einem profilierten Fräser.The main rotor is manufactured using a hobbing process with a profiled milling cutter.

Der Nebenrotor 18 besitzt neun Zähne (die nicht im einzelnen beziffert sind), wobei, wie aus den Fig. 4 bis 7 ersichtlich ist, die Zahnflanken zwischen den Zähnen durch die Relativbahn der Kopfpunkte 80 bis 84 des Hauptrotors 16 bestimmt sind. Genau genommen sind die Nebenrotorzahnflanken bei spitzen Nebenrotorzähnen keine Kreise, sondern verschlungene Epitrochoiden, die allerdings näherungsweise bei der Herstellung durch ihre Krümmungskreise, also durch Kreisbögen ersetzt werden können.The secondary rotor 18 has nine teeth (which are not numbered in detail), wherein, as can be seen from FIGS. 4 to 7, the tooth flanks between the teeth are determined by the relative path of the head points 80 to 84 of the main rotor 16. Strictly speaking, the secondary rotor tooth flanks in the case of pointed secondary rotor teeth are not circles, but intertwined epitrochoids, which, however, can be approximately replaced by their circles of curvature during manufacture, that is, by arcs.

Die Fig. 4 zeigt eine erste Stellung von Haupt-und Nebenrotor zueinander, in der der Kopfpunkt 82 des Hauptrotors 16 in der gezeichneten Stellung , d. h. die Kopfpunktmittellinie exakt auf der Verbindungslinie V-V der Mittelachsen der Rotoren liegt. Der Kopfpunkt 82 fluchtet dabei auch mit dem Kehlpunkt 82' des Nebenrotors 18, der ebenfalls auf der Verbindungslinie zwischen den Mittelpunkten der beiden Rotoren liegt. Die Kopfpunktmittellinie und die Kehlpunktmittellinie fallen dabei zusammen. Die Kopfpunkte 88 und 90 des Nebenrotors 18 liegen genau auf der Zahnflanke des Zahnes auf, der den Kopfpunkt 82 besitzt. Verdreht man den Hauptrotor gemäss Pfeilrichtung C, dann bewegt sich die Kopfpunktmittellinie mit dem Kopfpunkt 82 (in der Fig. 5 nach unten) im Uhrzeigersinn, wobei der Kopfpunkt 82 genau auf der Zahnflanke des Nebenrotors läuft, dergestalt, dass die Zahnflanke des Nebenrotors durch die Bahn des Kopfpunktes 82 bestimmt wird. Der Kopfpunkt 90 des Nebenrotors 18 liegt an der anderen Zahnflanke immer noch an. Die Kehlpunktmittellinie des Nebenrotors 18 ist dabei entsprechend des Drehzahlverhältnisses zwischen Haupt- und Nebenrotor um einen geringeren Betrag entgegen dem Uhrzeigersinn aus der Verbindungslinie der Mittelpunkte der beiden Rotoren ausgewandert.FIG. 4 shows a first position of the main rotor and the secondary rotor relative to one another, in which the head point 82 of the main rotor 16 in the position shown, ie. H. the center point of the head point lies exactly on the connecting line V-V of the central axes of the rotors. The head point 82 is also aligned with the throat point 82 'of the secondary rotor 18, which is also on the connecting line between the center points of the two rotors. The center line of the head and the center of the throat coincide. The head points 88 and 90 of the secondary rotor 18 lie exactly on the tooth flank of the tooth which has the head point 82. If you turn the main rotor in the direction of arrow C, the head point center line with the head point 82 (downwards in FIG. 5) moves clockwise, the head point 82 running exactly on the tooth flank of the secondary rotor in such a way that the tooth flank of the secondary rotor passes through the Path of the head point 82 is determined. The head point 90 of the secondary rotor 18 is still on the other tooth flank. The throat center line of the secondary rotor 18 has migrated counterclockwise by a smaller amount in accordance with the speed ratio between the main rotor and the secondary rotor from the connecting line of the center points of the two rotors.

In der Fig. 6 befindet sich der Kopfpunkt 82 des Hauptrotors in dem Bereich des Kopfpunktes 88 des Nebenrotors, wobei der Kopfpunkt 90 nach wie vor auf der Zahnflanke des Hauptrotores liegt. In der Fig. 7 erkennt man, dass der Kopfpunkt 82 vom Nebenrotor freigekommen ist, dabei jedoch bleibt der Kopfpunkt 90 immer noch auf der Zahnflanke liegen. Bei weiterer Verdrehung gelangt der Kopfpunkt 84 in Eingriff mit dem Nebenrotor, und der Ablauf bzw. die Geometrie ist die gleiche wie in den Fig. 4 bis 7: die Zahnflanken des Nebenrotors werden durch den jeweiligen Kopfpunkt des Hauptrotors gebildet, wobei dann, wenn sich ein Kopfpunkt des Hauptrotors zwischen zwei Kopfpunkten des Nebenrotors befindet, die beiden genannten Kopfpunkte auf der Zahnflanke bzw. den Zahnflanken des Hauptrotors aufliegen.6, the head point 82 of the main rotor is located in the region of the head point 88 of the secondary rotor, the head point 90 still lying on the tooth flank of the main rotor. In FIG. 7 it can be seen that the head point 82 has come free from the secondary rotor, but the head point 90 still remains on the tooth flank. With further rotation, the head point 84 comes into engagement with the secondary rotor, and the sequence or the geometry is the same as in FIGS. 4 to 7: the tooth flanks of the secondary rotor are formed by the respective head point of the main rotor, when if a head point of the main rotor is located between two head points of the secondary rotor, the two mentioned head points rest on the tooth flank or the tooth flanks of the main rotor.

Da bei spitzen Nebenrotorzähnen die Zahnflanken des Nebenrotors durch den Kopfpunkt des Hauptrotors gebildet werden, ist eine explizite Berechnung der Zahnflanken des Nebenrotors, die als verschlungene Aufradlinie anzusehen ist, durch Berechnung mit elektronischer Datenverarbeitung möglich.Since the tooth flanks of the secondary rotor are formed by the head point of the main rotor in the case of pointed secondary rotor teeth, an explicit calculation of the tooth flanks of the secondary rotor, which can be regarded as a convoluted wheel line, is possible by calculation with electronic data processing.

Es ist noch festzuhalten, dass aufgrund der Profilform von Haupt- und Nebenrotor das Blasloch praktisch Null ist. Dies ist ein weiterer, besonderer Vorteil der erfindungsgemässen Ausgestaltung und die Profilform ist aus diesem Grunde auch besonders günstig geeignet für kleine Fördervolumina, wo schon kleinste Leckagen zu einer deutlichen Verringerung des Wirkungsgrades führen können.It should be noted that the blow hole is practically zero due to the profile shape of the main and secondary rotor. This is a further, particular advantage of the configuration according to the invention and for this reason the profile shape is also particularly advantageously suitable for small delivery volumes, where even the smallest leakage can lead to a significant reduction in efficiency.

Claims (3)

1. A parallel and outer axial rotating piston compressor comprising at least one driven helical main rotor and an auxiliary rotor meshing therewith, characterised in that the tooth surfaces of the main rotor are layered circular screw surfaces produced by screwing of a circle with a plane which is perpendicular to the screw axis.
2. A rotating piston compressor according to Claim 1, characterised in that the tooth surfaces of the auxiliary rotor are defined by the travel path of a point lying on the head line (the main rotor head point) during the relative rolling motion of the main rotor and auxiliary rotor.
3. A rotating piston compressor according to Claim 1, characterised in that the main rotor has at least three teeth.
EP82109274A 1981-10-09 1982-10-07 Rotary piston compressor Expired EP0077031B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT82109274T ATE14916T1 (en) 1981-10-09 1982-10-07 ROTARY COMPRESSOR.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19813140108 DE3140108A1 (en) 1981-10-09 1981-10-09 TURN PISTON COMPRESSORS
DE3140108 1981-10-09

Publications (2)

Publication Number Publication Date
EP0077031A1 EP0077031A1 (en) 1983-04-20
EP0077031B1 true EP0077031B1 (en) 1985-08-14

Family

ID=6143718

Family Applications (1)

Application Number Title Priority Date Filing Date
EP82109274A Expired EP0077031B1 (en) 1981-10-09 1982-10-07 Rotary piston compressor

Country Status (5)

Country Link
US (1) US4619596A (en)
EP (1) EP0077031B1 (en)
JP (1) JPS58135394A (en)
AT (1) ATE14916T1 (en)
DE (1) DE3140108A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2006483A2 (en) 2007-06-21 2008-12-24 Franz Kraler Venetian blind

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60116920A (en) * 1983-11-30 1985-06-24 Hitachi Ltd Thrust bearing holding in rotary fluid machine
DE8434596U1 (en) * 1983-12-14 1985-02-21 Boge Kompressoren Otto Boge Gmbh & Co Kg, 4800 Bielefeld TURNING PISTON COMPRESSORS
DD301062A7 (en) * 1989-01-17 1992-10-01 Kuehlautomat Berlin Gmbh Rotor pair for high pressure screw compressor
CN114635849B (en) * 2022-05-19 2022-08-12 冰轮环境技术股份有限公司 Four-rotor displacement pump and flow adjusting method

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB254986A (en) * 1925-10-06 1926-07-15 Alexander Johan Mollinger Improvements in or relating to screw pumps
AT169479B (en) * 1946-07-18 1951-11-26 Ljungstroems Angturbin Ab Rotary piston machine
US2486770A (en) * 1946-08-21 1949-11-01 Joseph E Whitfield Arc generated thread form for helical rotary members
CH384768A (en) * 1959-09-02 1965-02-26 Ingersoll Rand Co Fluid pump or motor
US3138110A (en) * 1962-06-05 1964-06-23 Joseph E Whitfield Helically threaded intermeshing rotors
US3282495A (en) * 1964-04-29 1966-11-01 Dresser Ind Sealing arrangement for screw-type compressors and similar devices
GB1197432A (en) * 1966-07-29 1970-07-01 Svenska Rotor Maskiner Ab Improvements in and relating to Rotary Positive Displacement Machines of the Intermeshing Screw Type and Rotors therefor
SE390751B (en) * 1973-07-20 1977-01-17 Atlas Copco Ab SCREWDRIVER
DE2360403A1 (en) * 1973-12-04 1975-06-05 H & H Licensing Corp SCREW COMPRESSOR SYSTEM FOR COMPRESSING GAS-FORM MEDIA, IN PARTICULAR FOR LOW SUCTION VOLUMES

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2006483A2 (en) 2007-06-21 2008-12-24 Franz Kraler Venetian blind

Also Published As

Publication number Publication date
DE3140108A1 (en) 1983-04-28
ATE14916T1 (en) 1985-08-15
JPS58135394A (en) 1983-08-11
US4619596A (en) 1986-10-28
EP0077031A1 (en) 1983-04-20

Similar Documents

Publication Publication Date Title
DE3780158T2 (en) CYCLLOIDED AQUIDISTANT CURVE TRANSMISSION MECHANISM AND ITS DEVICE.
DE3432915C2 (en) Internal axis rotary piston machine
DE69503385T2 (en) CROWN GEARBOX, CROWN WHEEL AND METHOD AND TOOL FOR PRODUCING THE CROWN WHEEL
DE2508435C3 (en) Parallel and external axis rotary piston machine with comb engagement
DE2818332C2 (en) Drive shaft with spherical external spline teeth and method for producing the same
AT400974B (en) SCREW ROTOR MACHINE
DE2512651A1 (en) LOW-NOISE GEAR TRANSMISSION
DE3034299C2 (en)
DE594691C (en) Screw compressor, consisting of right- and left-handed, mutually engaging screws coupled by cogwheels
DE202016005208U1 (en) Dry-compacting vacuum pump
DE2911415C2 (en) Parallel and external axis rotary piston machine with meshing engagement
EP3507497B1 (en) Vacuum pump screw rotor
EP0077031B1 (en) Rotary piston compressor
DE2108714A1 (en) Rotary piston machine
DE1231055B (en) Rotary piston internal combustion engine in trochoid design
EP3507495B1 (en) Screw-type vacuum pump
DE19620482C2 (en) Spiral compressor with an inclined surface on a spiral part
EP0080585B1 (en) Rotary piston compressor
EP0149446A2 (en) Rotary piston compressor
DE934605C (en) Rotary piston machine
DE3301140C2 (en)
DE102019212221A1 (en) Strain wave gear
DE2315503C2 (en) External rotary piston compression or expansion machine
DE102019212220A1 (en) Strain wave gear
CH109955A (en) Gears rotating machine.

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Designated state(s): AT BE CH FR GB IT LI NL SE

17P Request for examination filed

Effective date: 19830914

ITF It: translation for a ep patent filed
GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Designated state(s): AT BE CH FR GB IT LI NL SE

REF Corresponds to:

Ref document number: 14916

Country of ref document: AT

Date of ref document: 19850815

Kind code of ref document: T

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: AT

Payment date: 19861030

Year of fee payment: 5

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: NL

Payment date: 19861031

Year of fee payment: 5

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Effective date: 19871007

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Effective date: 19871008

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Effective date: 19871031

Ref country code: CH

Effective date: 19871031

Ref country code: BE

Effective date: 19871031

BERE Be: lapsed

Owner name: TECHNIKA BETEILIGUNGSG-M.B.H.

Effective date: 19871031

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Effective date: 19880501

NLV4 Nl: lapsed or anulled due to non-payment of the annual fee
GBPC Gb: european patent ceased through non-payment of renewal fee
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19880630

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Effective date: 19881121

EUG Se: european patent has lapsed

Ref document number: 82109274.9

Effective date: 19880712