EP3221584B1 - Compressor with adjustable gear ratio to the driving means - Google Patents

Compressor with adjustable gear ratio to the driving means Download PDF

Info

Publication number
EP3221584B1
EP3221584B1 EP15794204.6A EP15794204A EP3221584B1 EP 3221584 B1 EP3221584 B1 EP 3221584B1 EP 15794204 A EP15794204 A EP 15794204A EP 3221584 B1 EP3221584 B1 EP 3221584B1
Authority
EP
European Patent Office
Prior art keywords
crankshaft
compressor
gear
driving means
connecting rod
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.)
Active
Application number
EP15794204.6A
Other languages
German (de)
French (fr)
Other versions
EP3221584A1 (en
Inventor
Gilles Hebrard
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.)
Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH
Original Assignee
Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH
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 Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH filed Critical Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH
Publication of EP3221584A1 publication Critical patent/EP3221584A1/en
Application granted granted Critical
Publication of EP3221584B1 publication Critical patent/EP3221584B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B67/00—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for
    • F02B67/04—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for of mechanically-driven auxiliary apparatus
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/01—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being mechanical
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0094—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 crankshaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F7/00—Casings, e.g. crankcases or frames
    • F02F7/0002—Cylinder arrangements
    • F02F7/0019—Cylinders and crankshaft not in one plane (deaxation)

Definitions

  • the invention relates to a compressor which is connected to a drive source by a gear transmission.
  • Air compressors for commercial vehicles generally convert a rotary movement provided by the drive source (engine) of at least one piston, which moves up and down in a cylinder and compresses the air during this movement. This conversion takes place by means of a connecting rod which is rotatably mounted on the piston with a connecting rod eye and which is rotatably mounted eccentrically on a crankshaft with another connecting rod eye.
  • the crankshaft is rotated by the drive source through a gear ratio.
  • the gear ratio is constant so that the working speed of the compressor changes with the engine speed.
  • the compressor is generally designed so that it can still supply the required compressed air requirement of the vehicle at its system pressure even when the vehicle engine is idling.
  • the compressor must fit into an installation volume specified by the vehicle design, and the crankshaft must have a gearwheel for the power transmission that fits into a gearwheel present on the drive source.
  • the operating parameters of the compressor are more or less fixed and must be accepted by the user, even if they are not optimal in terms of noise or energy consumption.
  • a compressor In the context of the invention, a compressor was developed. This has a crankcase in which a crankshaft is rotatably mounted in a crankcase.
  • the crankcase contains at least one cylinder space in which a piston, which is mounted eccentrically on the crankshaft by a connecting rod, can be excited to reciprocate.
  • the crankshaft is connected to a drive source by a gear transmission that has a modulus m, in that the gearwheel arranged on the crankshaft engages in the gearwheel on the drive source.
  • the axis of rotation of the crankshaft is offset from the central axis of the cylinder space by an amount d1, which is an integral multiple of m / 2.
  • the central axis of the cylinder space is understood to mean the axis extending from the center of the base area of the cylinder space perpendicular to this base area, along which the piston moves.
  • the transmission ratio of the transmission can be changed to an advantageous range without having to make changes to the external dimensions of the compressor or to the drive source.
  • the gear of the drive source does not have to be changed. If the gear of the drive source has a number Z 1 of teeth and the meshing gear of the crankshaft has a number Z 2 of teeth, then the distance between the axes of rotation of the gears is given by m ⁇ (Z 1 + Z 2 ) / 2, where m is the modulus of the transmission. This modulus is a measure of the size of the teeth.
  • the claimed offset between the axis of rotation of the crankshaft and the central axis of the cylinder space is introduced, the number of teeth Z 2 of the gear on the crankshaft and thus also the transmission ratio of the transmission can be changed without having to make changes to the drive source.
  • the number of teeth remains an integral number, particularly in the case of the claimed offset, so that complex adaptation measures on the gear wheels are not required.
  • the claimed feature of the integer multiple of m / 2 is not to be interpreted purely mathematically, but expressly also includes distances dl that deviate from an integer multiple of m / 2 only to such an extent that the gearwheel of the crankshaft within the mechanical tolerances can still mesh with the gear of the drive source without changes in the size of the teeth for the purpose of power transmission.
  • the transmission advantageously has a transmission ratio between 1 to 0.9 and 1 to 1.1 from the drive source to the crankshaft.
  • the typical motors for heavy commercial vehicles provide a gearwheel with a modulus value between 1.5 and 3.5 mm for driving a compressor.
  • the gear ratio by which the number of teeth Z 2 of the gear on the crankshaft is changed can thus be changed by 2 to 3%.
  • the transmission ratio is therefore advantageously greater than 1, ie Z 2 is less than Z 1 .
  • the piston of the compressor moves faster. Given the specifications for the air output per unit of time (for example 200 liters per minute at 12 bar system pressure and 700 revolutions per minute of the engine), less piston stroke in the cylinder is then required to achieve this output.
  • the compressor can be made more compact. Because of the limited space in the engine compartment, the piston displacement is a constant bottleneck. Typically only 360 to 400 cm 3 are available per cylinder.
  • the connecting rod eye of the connecting rod which is rotatably mounted against the crankshaft, is advantageously freely movable in a circle around the axis of the crankshaft. Wear caused by bearing forces is particularly low. Furthermore, this configuration takes up particularly little space in the crankcase of the crankcase.
  • the axis of rotation of the crankshaft is advantageously offset from the central axis of the cylinder space by an amount dl between 1 and 5 mm, preferably between 2 and 3 mm. Then the effect can additionally be exploited that the deflection of the connecting rod from the central axis of the cylinder is reduced when the crankshaft rotates about its axis. This deflection applies a force component to the piston, which presses against the wall of the cylinder and thus increases the wear due to friction between the cylinder and the piston.
  • the invention offers the advantage that compressors of a limited range of performance classes with a high proportion of identical parts can be manufactured inexpensively.
  • To adjust the power only the offset dl between the axis of rotation of the crankshaft and the central axis of the cylinder has to be adjusted.
  • FIG 1 shows a schematic diagram of a compressor according to the invention.
  • a cylinder bore 1a in the crankcase 1.5 Their central axis is labeled X.
  • a piston 2 moves in the cylinder bore. It is connected to the crankshaft 4 via a connecting rod 3.
  • the connecting rod has two connecting rod eyes 3a and 3b.
  • the upper connecting rod eye 3a is rotatably supported against the piston 2.
  • the lower connecting rod eye 3b is rotatably supported against a crank pin 4a which rotates with the crankshaft 4 about its central axis Y. If the crankshaft 4 rotates, the lower connecting rod eye 3b of the connecting rod 3 describes a circle around the central axis Y of the crankshaft 4.
  • the axes X and Y run perpendicular to one another; the X axis runs in the drawing plane, the Y axis perpendicular to the drawing plane. However, both axes are shifted parallel to each other by an amount dl.
  • the crankshaft 4 is rotatably supported against the part 5 of the crankcase 1.5.
  • the effect of the parallel displacement dl is shown in the integration of the compressor into an engine compartment Figure 2 ,
  • the motor block 9 with fixed dimensions is located at a predetermined location and provides a predetermined gear wheel 8 for driving the compressor.
  • the gearwheel rotates about an axis Z which is perpendicular to the plane of the drawing and is at a distance A from the central axis X of the cylinder space which runs in the plane of the drawing.
  • the crankshaft 4 is from driven a gear 7 that engages in the gear 8 on the engine block 9. This gear 7 rotates about the axis Y, which is the axis of symmetry of the crankshaft 4 and is perpendicular to the plane of the drawing.
  • the axes Y and Z are at a distance B from one another which is smaller than the distance A.
  • the gear 7 therefore has a number Z 2 of teeth which is smaller than the number Z 1 of the gear 8 on the engine block 9.
  • the gear 7 thus rotates faster than the gear 8.
  • the flange 6, with which it is mounted in the engine compartment, is also located at the same location as in a compressor according to the prior art, the gear 7 of which was the same size as the gear 8.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Compressor (AREA)

Description

Die Erfindung betrifft einen Kompressor, der durch eine Getriebeübersetzung mit einer Antriebsquelle verbunden ist.The invention relates to a compressor which is connected to a drive source by a gear transmission.

Stand der TechnikState of the art

Luftkompressoren für Nutzfahrzeuge wandeln in der Regel eine von der Antriebsquelle (Motor) bereitgestellte Drehbewegung mindestens eines Kolbens um, der sich in einem Zylinder auf- und abbewegt und bei dieser Bewegung die Luft verdichtet. Diese Umwandlung geschieht durch eine Pleuelstange, die mit einem Pleuelauge am Kolben drehbar gelagert ist und die mit einem anderen Pleuelauge exzentrisch drehbar an einer Kurbelwelle gelagert ist. Die Kurbelwelle wird durch eine Getriebeübersetzung von der Antriebsquelle in Drehung versetzt. Das Übersetzungsverhältnis ist konstant, so dass die Arbeitsgeschwindigkeit des Kompressors sich mit der Motordrehzahl ändert.Air compressors for commercial vehicles generally convert a rotary movement provided by the drive source (engine) of at least one piston, which moves up and down in a cylinder and compresses the air during this movement. This conversion takes place by means of a connecting rod which is rotatably mounted on the piston with a connecting rod eye and which is rotatably mounted eccentrically on a crankshaft with another connecting rod eye. The crankshaft is rotated by the drive source through a gear ratio. The gear ratio is constant so that the working speed of the compressor changes with the engine speed.

Der Kompressor wird im Allgemeinen so ausgelegt, dass er den geforderten Druckluftbedarf des Fahrzeugs bei dessen Systemdruck auch im Leerlauf des Fahrzeugmotors noch liefern kann. Dabei muss der Kompressor in ein durch das Fahrzeugdesign vorgegebenes Einbauvolumen passen, und die Kurbelwelle muss für die Kraftübertragung ein Zahnrad aufweisen, das in ein an der Antriebsquelle vorhandenes Zahnrad passt. Die Betriebsparameter des Kompressors sind also mehr oder weniger fest vorgegeben und vom Benutzer hinzunehmen, auch wenn sie im Hinblick auf das Geräusch oder den Energieverbrauch nicht optimal sein sollten.The compressor is generally designed so that it can still supply the required compressed air requirement of the vehicle at its system pressure even when the vehicle engine is idling. The compressor must fit into an installation volume specified by the vehicle design, and the crankshaft must have a gearwheel for the power transmission that fits into a gearwheel present on the drive source. The operating parameters of the compressor are more or less fixed and must be accepted by the user, even if they are not optimal in terms of noise or energy consumption.

Aus der WO88/07620 A1 ist ein Kompressor mit den oberbegrifflichen Merkmalen bekannt. Auch aus der DE 38 04 574 A1 ist ein diesbezüglicher Kompressor bekannt.From the WO88 / 07620 A1 a compressor with the generic features is known. Also from the DE 38 04 574 A1 a compressor in this regard is known.

Aufgabe und LösungTask and solution

Es ist daher die Aufgabe der Erfindung, einen Kompressor zur Verfügung zu stellen, der bei Vorgabe eines konkreten Einbauraumes im Motorraum und eines konkreten Zahnrades an der Antriebsquelle für die Kraftübertragung auf vorteilhaftere Betriebsparameter konfigurierbar ist. Diese Aufgabe wird erfindungsgemäß gelöst durch einen Kompressor gemäß Hauptanspruch. Weitere vorteilhafte Ausgestaltungen ergeben sich aus den darauf rückbezogenen Unteransprüchen.It is therefore the object of the invention to provide a compressor which can be configured for more advantageous operating parameters for the power transmission when a specific installation space is specified in the engine compartment and a specific gearwheel on the drive source. This object is achieved by a compressor according to the main claim. Further advantageous configurations result from the subclaims which refer back to it.

Gegenstand der ErfindungSubject of the invention

Im Rahmen der Erfindung wurde ein Kompressor entwickelt. Dieser weist ein Kurbelgehäuse auf, in dem eine Kurbelwelle in einem Kurbelraum drehbar gelagert ist. Das Kurbelgehäuse enthält mindestens einen Zylinderraum, indem ein durch eine Pleuelstange exzentrisch an der Kurbelwelle gelagerter Kolben zu einer Hin- und Herbewebung anregbar ist. Die Kurbelwelle ist durch ein Zahnradgetriebe, dass einen Modulus m aufweist, mit einer Antriebsquelle verbunden, indem das an der Kurbelwelle angeordnete Zahnrad in das Zahnrad an der Antriebsquelle eingreift.In the context of the invention, a compressor was developed. This has a crankcase in which a crankshaft is rotatably mounted in a crankcase. The crankcase contains at least one cylinder space in which a piston, which is mounted eccentrically on the crankshaft by a connecting rod, can be excited to reciprocate. The crankshaft is connected to a drive source by a gear transmission that has a modulus m, in that the gearwheel arranged on the crankshaft engages in the gearwheel on the drive source.

Erfindungsgemäß ist die Drehachse der Kurbelwelle gegen die Mittelachse des Zylinderraums um einen Betrag dl versetzt, der ein ganzzahliges Vielfaches von m/2 ist. Unter der Mittelachse des Zylinderraums wird die vom Mittelpunkt der Grundfläche des Zylinderraums senkrecht zu dieser Grundfläche ausgehende Achse verstanden, entlang der der Kolben sich bewegt.According to the invention, the axis of rotation of the crankshaft is offset from the central axis of the cylinder space by an amount d1, which is an integral multiple of m / 2. The central axis of the cylinder space is understood to mean the axis extending from the center of the base area of the cylinder space perpendicular to this base area, along which the piston moves.

Es wurde erkannt, dass auf diese Weise das Übersetzungsverhältnis des Getriebes in einen vorteilhaften Bereich geändert werden kann, ohne das an den Außenmaßen des Kompressors oder an der Antriebsquelle Veränderungen vorgenommen werden müssen. Insbesondere muss das Zahnrad der Antriebsquelle nicht geändert werden. Wenn das Zahnrad der Antriebsquelle eine Anzahl Z1 von Zähnen hat und das darin eingreifende Zahnrad der Kurbelwelle eine Anzahl Z2 von Zähnen hat, dann ist der Abstand der Drehachsen der Zahnräder gegeben durch m∗(Z1 + Z2)/2, worin m der Modulus des Getriebes ist. Dieser Modulus ist ein Maß für die Größe der Zähne. In dem der beanspruchte Versatz zwischen der Drehachse der Kurbelwelle und der Mittelachse des Zylinderraums eingeführt wird, kann die Zahnzahl Z2 des Zahnrads an der Kurbelwelle und damit auch das Übersetzungsverhältnis des Getriebes geändert werden, ohne das an der Antriebsquelle Veränderungen vorgenommen werden müssen. Gerade bei dem beanspruchten Versatz bleibt die Zahnanzahl ganzzahlig, so dass aufwendige Anpassungsmaßnahmen an den Zahnrädern entfallen. Somit ist das beanspruchte Merkmal des ganzzahligen Vielfachen von m/2 auch nicht rein mathematisch auszulegen, sondern umfasst ausdrücklich auch noch Abstände dl, die von einem ganzzahligen Vielfachen von m/2 nur so weit abweichen, dass das Zahnrad der Kurbelwelle im Rahmen der mechanischen Toleranzen noch ohne Änderungen an der Größe der Zähne zwecks Kraftübertragung in das Zahnrad der Antriebsquelle eingreifen kann.It was recognized that in this way the transmission ratio of the transmission can be changed to an advantageous range without having to make changes to the external dimensions of the compressor or to the drive source. In particular, the gear of the drive source does not have to be changed. If the gear of the drive source has a number Z 1 of teeth and the meshing gear of the crankshaft has a number Z 2 of teeth, then the distance between the axes of rotation of the gears is given by m ∗ (Z 1 + Z 2 ) / 2, where m is the modulus of the transmission. This modulus is a measure of the size of the teeth. In that the claimed offset between the axis of rotation of the crankshaft and the central axis of the cylinder space is introduced, the number of teeth Z 2 of the gear on the crankshaft and thus also the transmission ratio of the transmission can be changed without having to make changes to the drive source. The number of teeth remains an integral number, particularly in the case of the claimed offset, so that complex adaptation measures on the gear wheels are not required. Thus, the claimed feature of the integer multiple of m / 2 is not to be interpreted purely mathematically, but expressly also includes distances dl that deviate from an integer multiple of m / 2 only to such an extent that the gearwheel of the crankshaft within the mechanical tolerances can still mesh with the gear of the drive source without changes in the size of the teeth for the purpose of power transmission.

Dabei weist das Getriebe vorteilhaft ein Übersetzungsverhältnis zwischen 1 zu 0,9 und 1 zu 1,1 von der Antriebsquelle auf die Kurbelwelle auf. Die typischen Motoren für schwere Nutzfahrzeuge stellen für den Antrieb eines Kompressors ein Zahnrad mit einem Moduluswert zwischen 1,5 und 3,5 mm bereit. Damit kann das Übersetzungsverhältnis pro Zahn, um den die Zahnanzahl Z2 des Zahnrads an der Kurbelwelle geändert wird, um 2 bis 3 % geändert werden.The transmission advantageously has a transmission ratio between 1 to 0.9 and 1 to 1.1 from the drive source to the crankshaft. The typical motors for heavy commercial vehicles provide a gearwheel with a modulus value between 1.5 and 3.5 mm for driving a compressor. The gear ratio by which the number of teeth Z 2 of the gear on the crankshaft is changed can thus be changed by 2 to 3%.

Nach dem Stand der Technik waren die Zahnanzahlen beider Zahnräder identisch, also Z1 = Z2. Wird Z2 jetzt über Z1 hinaus gesteigert, bewegt sich der Kolben im Kompressor langsamer. Damit kann das Betriebsgeräusch des Kompressors vermindert werden um den Preis, dass auch die Luftleistung pro Zeiteinheit abnimmt. Vorteilhaft ist daher das Übersetzungsverhältnis größer als 1, d.h. Z2 ist kleiner als Z1. Dann bewegt sich der Kolben des Kompressors schneller. Bei gegebenen Spezifikationen für die Luftleistung pro Zeiteinheit (beispielsweise 200 Liter pro Minute bei 12 bar Systemdruck und 700 Umdrehungen pro Minute des Motors) ist dann weniger Kolbenhub im Zylinder erforderlich, um diese Leistung zu erbringen. Der Kompressor kann kompakter ausgestaltet werden. Wegen der beengten Platzverhältnisse im Motorraum ist der Kolbenhubraum ein ständiger Engpass. Typischerweise stehen nur 360 bis 400 cm3 pro Zylinder zur Verfügung.According to the prior art, the number of teeth of both gears were identical, that is Z 1 = Z 2 If Z 2 is now increased above Z 1 , the piston in the compressor moves more slowly. The operating noise of the compressor can thus be reduced at the price that the air output per unit of time also decreases. The transmission ratio is therefore advantageously greater than 1, ie Z 2 is less than Z 1 . Then the piston of the compressor moves faster. Given the specifications for the air output per unit of time (for example 200 liters per minute at 12 bar system pressure and 700 revolutions per minute of the engine), less piston stroke in the cylinder is then required to achieve this output. The compressor can be made more compact. Because of the limited space in the engine compartment, the piston displacement is a constant bottleneck. Typically only 360 to 400 cm 3 are available per cylinder.

Vorteilhaft ist das gegen die Kurbelwelle drehbar gelagerte Pleuelauge der Pleuelstange frei in einem Kreis um die Achse der Kurbelwelle beweglich. Der Verschleiß durch Lagerkräfte ist dann besonders gering. Weiterhin beansprucht diese Ausgestaltung besonders wenig Platz im Kurbelraum des Kurbelgehäuses.The connecting rod eye of the connecting rod, which is rotatably mounted against the crankshaft, is advantageously freely movable in a circle around the axis of the crankshaft. Wear caused by bearing forces is particularly low. Furthermore, this configuration takes up particularly little space in the crankcase of the crankcase.

Vorteilhaft ist die Drehachse der Kurbelwelle gegen die Mittelachse des Zylinderraums um einen Betrag dl zwischen 1 und 5 mm, bevorzugt zwischen 2 und 3 mm, versetzt. Dann kann zusätzlich der Effekt ausgenutzt werden, dass bei der Drehung der Kurbelwelle um ihre Achse die Auslenkung der Pleuelstange aus der Mittelachse des Zylinders vermindert wird. Diese Auslenkung beaufschlagt den Kolben mit einer Kraftkomponente, die gegen die Wand des Zylinders drückt und somit den Verschleiß durch Reibung zwischen Zylinder und Kolben erhöht.The axis of rotation of the crankshaft is advantageously offset from the central axis of the cylinder space by an amount dl between 1 and 5 mm, preferably between 2 and 3 mm. Then the effect can additionally be exploited that the deflection of the connecting rod from the central axis of the cylinder is reduced when the crankshaft rotates about its axis. This deflection applies a force component to the piston, which presses against the wall of the cylinder and thus increases the wear due to friction between the cylinder and the piston.

Allgemein bietet die Erfindung den Vorteil, dass Kompressoren eines begrenzten Umfangs an Leistungsklassen mit einem hohen Gleichteilanteil kostengünstig gefertigt werden könne. Es ist zur Einstellung der Leistung lediglich der Versatz dl zwischen der Drehachse der Kurbelwelle und der Mittelachse des Zylinders anzupassen.In general, the invention offers the advantage that compressors of a limited range of performance classes with a high proportion of identical parts can be manufactured inexpensively. To adjust the power, only the offset dl between the axis of rotation of the crankshaft and the central axis of the cylinder has to be adjusted.

Spezieller BeschreibungsteilSpecial description part

Nachfolgend wird der Gegenstand der Erfindung anhand von Figuren erläutert, ohne dass der Gegenstand der Erfindung hierdurch beschränkt wird. Es ist gezeigt:

Figur 1
Prinzipskizze des erfindungsgemäßen Kompressors mit Versatz zwischen Kurbelwelle und Mittelachse des Zylinderraums.
Figur 2
Integration eines erfindungsgemäßen Kompressors in einen vorgegebenen Motorraum.
The subject matter of the invention is explained below with reference to figures, without the subject matter of the invention being restricted thereby. It is shown:
Figure 1
Schematic diagram of the compressor according to the invention with an offset between the crankshaft and the central axis of the cylinder space.
Figure 2
Integration of a compressor according to the invention in a given engine compartment.

Figur 1 zeigt eine Prinzipskizze eines erfindungsgemäßen Kompressors. In dem Kurbelgehäuse 1,5 befindet sich eine Zylinderbohrung 1a. Ihre Mittelachse ist mit X bezeichnet. In der Zylinderbohrung bewegt sich ein Kolben 2. Er ist über eine Pleuelstange 3 mit der Kurbelwelle 4 verbunden. Die Pleuelstange hat zwei Pleuelaugen 3a und 3b. Das obere Pleuelauge 3a ist drehbar gegen den Kolben 2 gelagert. Das untere Pleuelauge 3b ist drehbar gegen einen Kurbelzapfen 4a gelagert, der sich mit der Kurbelwelle 4 um deren Mittelachse Y dreht. Dreht sich die Kurbelwelle 4, beschreibt das untere Pleuelauge 3b der Pleuelstange 3 einen Kreis um die Mittelachse Y der Kurbelwelle 4. Die Achsen X und Y verlaufen senkrecht zueinander; die Achse X verläuft in der Zeichenebene, die Achse Y senkrecht zur Zeichenebene. Beide Achsen sind jedoch parallel um einen Betrag dl zueinander verschoben. Die Kurbelwelle 4 ist gegen das Teil 5 des Kurbelgehäuses 1,5 drehbar gelagert. Figure 1 shows a schematic diagram of a compressor according to the invention. There is a cylinder bore 1a in the crankcase 1.5. Their central axis is labeled X. A piston 2 moves in the cylinder bore. It is connected to the crankshaft 4 via a connecting rod 3. The connecting rod has two connecting rod eyes 3a and 3b. The upper connecting rod eye 3a is rotatably supported against the piston 2. The lower connecting rod eye 3b is rotatably supported against a crank pin 4a which rotates with the crankshaft 4 about its central axis Y. If the crankshaft 4 rotates, the lower connecting rod eye 3b of the connecting rod 3 describes a circle around the central axis Y of the crankshaft 4. The axes X and Y run perpendicular to one another; the X axis runs in the drawing plane, the Y axis perpendicular to the drawing plane. However, both axes are shifted parallel to each other by an amount dl. The crankshaft 4 is rotatably supported against the part 5 of the crankcase 1.5.

Die Wirkung der Parallelverschiebung dl zeigt sich bei der Integration des Kompressors in einen Motorraum gemäß Figur 2. An einem vorgegebenen Ort befindet sich der Motorblock 9 mit festen Abmessungen, der ein vorgegebenes Zahnrad 8 für den Antrieb des Kompressors bereitstellt. Das Zahnrad dreht sich um eine Achse Z, die senkrecht auf der Zeichenebene steht und von der in der Zeichenebene verlaufenden Mittelachse X des Zylinderraums einen Abstand A hat. Die Kurbelwelle 4 wird von einem Zahnrad 7 angetrieben, dass in das Zahnrad 8 am Motorblock 9 eingreift. Dieses Zahnrad 7 dreht sich um die Achse Y, die die Symmetrieachse der Kurbelwelle 4 ist und senkrecht auf der Zeichenebene steht. Die Achsen Y und Z haben einen Abstand B voneinander, der kleiner als der Abstand A ist. Daher hat das Zahnrad 7 eine Anzahl Z2 von Zähnen, die kleiner ist als die Zahnanzahl Z1 des Zahnrads 8 am Motorblock 9. Das Zahnrad 7 dreht also schneller als das Zahnrad 8. Dadurch stößt der Kompressor pro Zeiteinheit ein größeres Luftvolumen aus. Diese Veränderung wurde bewirkt, ohne das an den Abmessungen und am Formfaktor des Kompressors eine Veränderung vorgenommen werden musste. Auch der Flansch 6, mit dem er im Motorraum montiert ist, befindet sich an der gleichen Stelle wie bei einem Kompressor gemäß Stand der Technik, dessen Zahnrad 7 genauso groß war wie das Zahnrad 8.The effect of the parallel displacement dl is shown in the integration of the compressor into an engine compartment Figure 2 , The motor block 9 with fixed dimensions is located at a predetermined location and provides a predetermined gear wheel 8 for driving the compressor. The gearwheel rotates about an axis Z which is perpendicular to the plane of the drawing and is at a distance A from the central axis X of the cylinder space which runs in the plane of the drawing. The crankshaft 4 is from driven a gear 7 that engages in the gear 8 on the engine block 9. This gear 7 rotates about the axis Y, which is the axis of symmetry of the crankshaft 4 and is perpendicular to the plane of the drawing. The axes Y and Z are at a distance B from one another which is smaller than the distance A. The gear 7 therefore has a number Z 2 of teeth which is smaller than the number Z 1 of the gear 8 on the engine block 9. The gear 7 thus rotates faster than the gear 8. As a result, the compressor discharges a larger volume of air per unit of time. This change was accomplished without having to change the dimensions and shape factor of the compressor. The flange 6, with which it is mounted in the engine compartment, is also located at the same location as in a compressor according to the prior art, the gear 7 of which was the same size as the gear 8.

Claims (5)

  1. Compressor with a crankcase (1, 5) in which a crankshaft (4) is mounted and able to rotate in a crank space, wherein the crank case (1, 5) contains at least one cylinder space (1a) in which a piston (2) fitted eccentrically onto the crankshaft (4) by a connecting rod (3) can be made to move to and fro and wherein the crankshaft (4) is connected to a driving means (9) by a gearset (7, 8) having a modulus m, in which gearset the gearwheel (7) arranged on the crankshaft (4) engages with the gearwheel (8) of the driving means (9), the rotation axis (Y) of the crankshaft (4) being offset relative to the central axis (X) of the cylinder space (1a) by an amount dl,
    characterised in that the amount dl is an integral multiple of m/2 and dl is between 1 and 5 mm.
  2. Compressor according to Claim 1,
    characterised in that the gearset (7, 8) has a gear ratio between 1:0.9 and 1:1.1 from the driving means (9) to the crankshaft (4).
  3. Compressor according to either of Claims 1 or 2,
    characterised in that the gear ratio is greater than 1.
  4. Compressor according to any of Claims 1 to 3,
    characterised in that the connecting-rod eye (3b) of the connecting rod (3) mounted so that it can rotate relative to the crankshaft (4) can move freely in a circle about the axis (Y) of the crankshaft (4).
  5. Compressor according to any of Claims 1 to 4,
    characterised in that the rotation axis (Y) of the crankshaft (4) is offset relative to the central axis (X) of the cylinder space (1a) by an amount dl of between 2 and 3 mm.
EP15794204.6A 2014-11-17 2015-11-16 Compressor with adjustable gear ratio to the driving means Active EP3221584B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014116805.4A DE102014116805A1 (en) 2014-11-17 2014-11-17 Compressor with adjustable translation to the drive source
PCT/EP2015/076636 WO2016079031A1 (en) 2014-11-17 2015-11-16 Compressor with adaptable transmission with respect to the motive source

Publications (2)

Publication Number Publication Date
EP3221584A1 EP3221584A1 (en) 2017-09-27
EP3221584B1 true EP3221584B1 (en) 2020-01-15

Family

ID=54541092

Family Applications (1)

Application Number Title Priority Date Filing Date
EP15794204.6A Active EP3221584B1 (en) 2014-11-17 2015-11-16 Compressor with adjustable gear ratio to the driving means

Country Status (7)

Country Link
US (1) US10753349B2 (en)
EP (1) EP3221584B1 (en)
JP (1) JP2017534802A (en)
CN (1) CN107110139B (en)
BR (1) BR112017009922A2 (en)
DE (1) DE102014116805A1 (en)
WO (1) WO2016079031A1 (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE1025648B1 (en) * 2017-10-19 2019-05-20 Paul Uyttersprot SLICED SETUP OF THE CYLINDER AGAINST THE CRANKSHAFT
DE102017011615A1 (en) 2017-12-15 2019-06-19 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Drive arrangement for a compressor of a commercial vehicle
CN112324634B (en) * 2020-10-28 2021-07-13 西安交通大学 Reciprocating compressor with automatic lateral force balance function

Family Cites Families (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2302800C2 (en) 1973-01-20 1982-12-16 Klöckner-Humboldt-Deutz AG, 5000 Köln Reciprocating internal combustion engine with air compressor
US3985475A (en) * 1974-02-20 1976-10-12 Tecumseh Products Company Expansible chamber device
JPS51109305U (en) * 1975-02-27 1976-09-03
JPS56120377U (en) * 1980-02-18 1981-09-12
WO1988007620A1 (en) * 1987-03-30 1988-10-06 Mueller Lothar Reciprocating piston engine
US4848213A (en) 1988-01-11 1989-07-18 The Devilbiss Company Reciprocating piston compressor with offset cylinder
DE3804574A1 (en) 1988-02-13 1989-08-24 Man Nutzfahrzeuge Gmbh PTO OF AN INTERNAL COMBUSTION ENGINE FOR AN AIR PRESSER
DE3815741C1 (en) 1988-05-07 1989-12-28 Man Nutzfahrzeuge Ag, 8000 Muenchen, De
US5378123A (en) * 1990-02-02 1995-01-03 Carmelo J. Scuderi Apparatus for recovering refrigerant with offset cam
US5215447A (en) * 1992-06-26 1993-06-01 Wen San Jou Mini-type air compressor
US20040129244A1 (en) * 2001-03-15 2004-07-08 Normand Beaudoin Poly inductive machines and differential turbines
EP1394413B1 (en) * 2002-08-31 2016-10-12 Continental Teves AG & Co. oHG Piston compressor with reduced size
JP4309326B2 (en) * 2004-10-06 2009-08-05 本田技研工業株式会社 Plant control device
JP4752241B2 (en) * 2004-11-01 2011-08-17 パナソニック株式会社 Reciprocating compressor
US20070264139A1 (en) * 2006-05-09 2007-11-15 Chou Wen S Air compressor having stabilized structure
DE102006026220B4 (en) * 2006-06-06 2008-05-08 Siemens Ag Fluid pump with crank mechanism
DE202007017339U1 (en) * 2007-12-12 2008-03-27 Neander Motors Ag piston engine
US8522833B2 (en) * 2008-11-04 2013-09-03 Wen San Chou Device for sealing and inflating inflatable object
DE102011015720A1 (en) * 2011-03-31 2012-10-04 Neander Motors Ag Lifting cylinder machine e.g. compressor has gear box that is provided with gear wheels which are surrounded by lubricant-free shaft gear box space so as to ensure lubricant-free connection of teeth portions in gear wheels
WO2014065208A1 (en) * 2012-10-26 2014-05-01 住友ゴム工業株式会社 Compressor and flat tire repair kit using same
JP6307617B2 (en) * 2013-12-19 2018-04-04 ボルボトラックコーポレーション Internal combustion engine
WO2016137587A1 (en) * 2015-02-24 2016-09-01 Illinois Tool Works Inc. Compressor for discharging a medium

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
BR112017009922A2 (en) 2018-01-02
JP2017534802A (en) 2017-11-24
CN107110139B (en) 2019-10-11
US10753349B2 (en) 2020-08-25
CN107110139A (en) 2017-08-29
US20180291883A1 (en) 2018-10-11
DE102014116805A1 (en) 2016-05-19
WO2016079031A1 (en) 2016-05-26
EP3221584A1 (en) 2017-09-27

Similar Documents

Publication Publication Date Title
EP1736666B1 (en) Pump gear
DE102018104546B3 (en) generator
EP3221584B1 (en) Compressor with adjustable gear ratio to the driving means
EP1902217A1 (en) Compressor unit comprising an eccentric gear
EP3207233A1 (en) Power unit
EP2556256B1 (en) Rotary piston pump and method for operating a rotary piston pump
DE102012014047B3 (en) Method for operating combustion engine, involves connecting piston of combustion engine with crankshaft, supporting eccentric cam at crank pin, and driving eccentric cam with large rotation speed to achieve alternate lifting of piston
EP3175112B1 (en) Process pump with a crank mechanism
EP1963677B1 (en) Compressor unit
WO2004005712A1 (en) Reciprocating piston machine
EP3019770B1 (en) Drive having a piston machine and a device provided for such a drive, and the use of such a device for compensating alternating torques
EP1612369B1 (en) A mechanism for the conversion of reciprocating motion into rotary and vice versa
WO2015091169A1 (en) Compressor system having a piston-stroke adjustment device
DE112004000749B4 (en) fluid pump
DE19927770A1 (en) Multiple cylinder IC engine
DE10242228A1 (en) Compact piston crank drive has a drive shaft with cranked drive with a pinion with gear teeth meshing with an outer ring attached to a piston
DE102016207247A1 (en) Cavity Pump
DE10140066A1 (en) Gear pump used for supplying lubricating oil to an internal combustion engine comprises a volume-changing shifting unit, drive gear meshing with first gear and further driven gear so that one of the gears is arranged between the others
DE875102C (en) Free-flight piston machine with counter-rotating masses
DE102005026119B4 (en) Reibarmer reciprocating engine with adjustable compression end space
DE10206144A1 (en) transmission
DE102013015836B4 (en) Hot gas engine (Stirling engine) with weight-compensated displacer moved by two eccentrics
DE102011119447B4 (en) Double eccentric crank mechanism with conrod gear
DE202009010555U1 (en) reciprocating engine
DE202012000781U1 (en) Mechanical assembly for the conversion of a translational into a rotational, as well as vice versa from a rotary to a translatory movement with the innovation that only the linear axes perform a translatory, oscillating motion and the transformation into a rotational movement only over rotational, with constant angular velocity Machine elements is realized. Selected designation of the mechanical unit: "ring gear drive"

Legal Events

Date Code Title Description
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE INTERNATIONAL PUBLICATION HAS BEEN MADE

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

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

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20170619

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

DAV Request for validation of the european patent (deleted)
DAX Request for extension of the european patent (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

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

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTG Intention to grant announced

Effective date: 20190830

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

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

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502015011551

Country of ref document: DE

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 1225369

Country of ref document: AT

Kind code of ref document: T

Effective date: 20200215

REG Reference to a national code

Ref country code: SE

Ref legal event code: TRGR

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20200115

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

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

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200415

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200115

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200115

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200115

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200607

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

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200515

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200416

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200415

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200115

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200115

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502015011551

Country of ref document: DE

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

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200115

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200115

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200115

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200115

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200115

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200115

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200115

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200115

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

Effective date: 20201016

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

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200115

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

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200115

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200115

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

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200115

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

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

Ref country code: LU

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

Effective date: 20201116

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20201130

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

Ref country code: LI

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

Effective date: 20201130

Ref country code: CH

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

Effective date: 20201130

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: 20201130

Ref country code: IE

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

Effective date: 20201116

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 1225369

Country of ref document: AT

Kind code of ref document: T

Effective date: 20201116

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

Ref country code: AT

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

Effective date: 20201116

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

Ref country code: GB

Payment date: 20211123

Year of fee payment: 7

Ref country code: SE

Payment date: 20211123

Year of fee payment: 7

Ref country code: DE

Payment date: 20211122

Year of fee payment: 7

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

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200115

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200115

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

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200115

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200115

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

Ref country code: BE

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

Effective date: 20201130

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502015011551

Country of ref document: DE

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20230508

REG Reference to a national code

Ref country code: SE

Ref legal event code: EUG

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20221116

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

Ref country code: SE

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

Effective date: 20221117

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

Ref country code: GB

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

Effective date: 20221116

Ref country code: DE

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

Effective date: 20230601