EP3221584A1 - Compressor with adaptable transmission with respect to the motive source - Google Patents

Compressor with adaptable transmission with respect to the motive source

Info

Publication number
EP3221584A1
EP3221584A1 EP15794204.6A EP15794204A EP3221584A1 EP 3221584 A1 EP3221584 A1 EP 3221584A1 EP 15794204 A EP15794204 A EP 15794204A EP 3221584 A1 EP3221584 A1 EP 3221584A1
Authority
EP
European Patent Office
Prior art keywords
crankshaft
compressor
axis
gear
cylinder space
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.)
Granted
Application number
EP15794204.6A
Other languages
German (de)
French (fr)
Other versions
EP3221584B1 (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

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
    • 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
    • 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
    • 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 by a gear ratio with a drive source.
  • Commercial vehicle air compressors typically convert rotational motion provided by the drive source (motor) of at least one piston that moves up and down in a cylinder and compresses the air as it travels. This conversion is done by a connecting rod which is rotatably mounted with a connecting rod eye on the piston and which is mounted eccentrically rotatable with another connecting rod on a crankshaft.
  • the crankshaft is rotated by a gear ratio of the drive source in rotation. 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 deliver the required compressed air demand of the vehicle at its system pressure even when the vehicle engine is idling.
  • the compressor must fit into a specified by the vehicle design installation volume, and the crankshaft must have a gear for the transmission of power, which fits into an existing on the drive source gear.
  • the operating parameters of the compressor are thus more or less fixed and accepted by the user, even if they should not be optimal in terms of noise or energy consumption.
  • a compressor has been developed.
  • This has a crankcase, in which a crankshaft is rotatably mounted in a crank chamber.
  • the crankcase includes at least one cylinder space in which a by a connecting rod eccentrically mounted on the crankshaft piston to a reciprocation can be excited.
  • the crankshaft is connected to a drive source by a gear transmission having a modulus m by the gear arranged on the crankshaft engages the gear on the drive source.
  • the axis of rotation of the crankshaft is offset against the central axis of the cylinder space by an amount dl which is an integer multiple of m / 2.
  • the central axis of the cylinder space is understood to be the axis from which the center of the base area of the cylinder space extends perpendicular to this base area, along which the piston moves.
  • the gear ratio of the transmission can be changed to a favorable 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 need to be changed. If the gear of the drive source has a number Zi of teeth and the crankshaft meshing therewith has a number Z 2 of teeth, then the pitch of the axes of rotation of the gears is given by m * (Zi + Z 2 ) / 2, where m is the Modulus of the transmission is. 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 the transmission ratio of the transmission can be changed without changes to the drive source must be made.
  • the number of teeth remains integer, so that consuming adjustment measures account for the gears.
  • the claimed feature of the integer multiple of m / 2 is not interpreted purely mathematically, but also explicitly includes even distances dl, which differ from an integer multiple of m / 2 only so far that the gear of the crankshaft within the mechanical tolerances can intervene without changes to the size of the teeth for the purpose of transmitting power in the gear of the drive source.
  • the transmission advantageously has a transmission ratio between 1 to 0.9 and 1 to 1.1 from the drive source to the crankshaft.
  • Typical heavy-duty engines provide a gear with a modulus between 1.5 and 3.5 mm for driving a compressor.
  • the gear ratio per tooth by which the tooth number Z 2 of the gear on the crankshaft is changed can be changed by 2 to 3%.
  • the transmission ratio is greater than 1, ie Z 2 is smaller than Zi. Then the piston of the compressor moves faster. Given specifications for airflow per unit time (eg, 200 liters per minute at 12 bar system pressure and 700 rpm engine), less piston stroke in the cylinder is required to achieve this performance.
  • the transmission ratio is greater than 1, ie Z 2 is smaller than Zi.
  • Compressor can be made more compact. Because of the cramped space in the engine compartment of Kolbenhubraum is a constant bottleneck. Typically are only 360 to 400 cm 3 per cylinder are available.
  • the pivotally mounted against the crankshaft connecting rod eye of the connecting rod is freely movable in a circle about the axis of the crankshaft. The wear due to bearing forces is then particularly low. Furthermore, this embodiment takes up very little space in the crankcase of the crankcase.
  • the axis of rotation of the crankshaft against the central axis of the cylinder space by an amount dl between 1 and 5 mm, preferably between 2 and 3 mm, offset.
  • the invention offers the advantage that compressors of a limited scope of power classes with a high common-mode component can be produced inexpensively. It is to adjust the power only the offset dl between the axis of rotation of the crankshaft and the center axis of the cylinder adapt.
  • Figure 1 schematic diagram of the compressor according to the invention with offset between the crankshaft and center axis of the cylinder chamber.
  • FIG. 2 shows the integration of a compressor according to the invention into a given engine compartment.
  • FIG. 1 shows a schematic diagram of a compressor according to the invention.
  • the crankcase 1.5 is a cylinder bore la. Its central axis is marked with 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 3 a is rotatably supported against the piston 2.
  • the lower connecting rod 3b is rotatably supported against a crank pin 4a which rotates with the crankshaft 4 about the central axis Y thereof. If the crankshaft 4 rotates, the lower connecting-rod eye 3b of the connecting rod 3 describes a circle about the central axis Y of the crankshaft 4.
  • the axes X and Y run perpendicular to one another; the axis X runs in the plane of the drawing, the axis Y perpendicular to the plane of the drawing. 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 in an engine compartment as shown in FIG 2.
  • the engine block 9 is of fixed dimensions, which provides a predetermined gear 8 for driving the compressor.
  • the gearwheel rotates about an axis Z, which is perpendicular to the plane of the drawing and has a distance A from the center plane X of the cylinder space running in the plane of the drawing.
  • the crankshaft 4 is of a gear 7 driven that engages 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 have a distance B from each other which is smaller than the distance A. Therefore, the gear 7 has a number Z 2 of teeth, which is smaller than the tooth number Zi of the gear 8 on the engine block 9. The gear 7 thus rotates faster than the gear 8.
  • the compressor ejects a larger volume of air per unit time. This change was made without having to change the size and shape of the compressor. Also, the flange 6, with which it is mounted in the engine compartment, is located in the same place as in a compressor according to the prior art, the gear 7 was the same size as the gear. 8

Abstract

In the context of the invention, a compressor has been developed. This compressor has a crankcase in which a crankshaft is rotatably mounted in a crankspace. The crankcase contains at least one cylinder space in which a piston, mounted eccentrically on the crankshaft by means of a connecting rod, can be driven in reciprocating motion. The crankshaft is connected, via a gearing having a modulus m, to a motive source, wherein the gear wheel arranged on the crankshaft engages with the gear wheel on the motive source. According to the invention, the axis of rotation of the crankshaft is offset with respect to the center axis of the cylinder space by an amount dl which is a whole multiple of m/2. The center axis of the cylinder space is understood as the axis which proceeds from the center point of the base area of the cylinder space, perpendicular to this base area, and along which the piston moves. It has been recognized that it is thus possible to change the transmission ratio of the gearing within an advantageous range, without it being necessary to undertake modifications to the external dimensions of the compressor or to the motive source. In particular, the gear wheel of the motive source need not be altered. Depending on the transmission ratio, it is possible to reduce the operating noise of the compressor or to increase the air capacity.

Description

Kompressor mit anpassbarer Übersetzung zur Antriebsquelle  Compressor with adjustable translation to the drive source
Die Erfindung betrifft einen Kompressor, der durch eine Getriebeübersetzung mit einer Antriebsquelle verbunden ist. Stand der Technik The invention relates to a compressor which is connected by a gear ratio with a drive source. State 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 Motor- drehzahl ändert. Commercial vehicle air compressors typically convert rotational motion provided by the drive source (motor) of at least one piston that moves up and down in a cylinder and compresses the air as it travels. This conversion is done by a connecting rod which is rotatably mounted with a connecting rod eye on the piston and which is mounted eccentrically rotatable with another connecting rod on a crankshaft. The crankshaft is rotated by a gear ratio of the drive source in rotation. 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. Aufgabe und Lösung The compressor is generally designed so that it can still deliver the required compressed air demand of the vehicle at its system pressure even when the vehicle engine is idling. In this case, the compressor must fit into a specified by the vehicle design installation volume, and the crankshaft must have a gear for the transmission of power, which fits into an existing on the drive source gear. The operating parameters of the compressor are thus more or less fixed and accepted by the user, even if they should not be optimal in terms of noise or energy consumption. Task 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 Betrieb sparameter 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 an object of the invention to provide a compressor that is configurable sparameter when specifying a specific installation space in the engine compartment and a concrete gear on the drive source for power transmission to more advantageous operation. This object is achieved by a compressor according to the main claim. Further advantageous embodiments will be apparent from the dependent claims.
Gegenstand der Erfindung Subject 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 has been developed. This has a crankcase, in which a crankshaft is rotatably mounted in a crank chamber. The crankcase includes at least one cylinder space in which a by a connecting rod eccentrically mounted on the crankshaft piston to a reciprocation can be excited. The crankshaft is connected to a drive source by a gear transmission having a modulus m by the gear arranged on the crankshaft engages the gear 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 against the central axis of the cylinder space by an amount dl which is an integer multiple of m / 2. The central axis of the cylinder space is understood to be the axis from which the center of the base area of the cylinder space extends 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 müs- sen. Insbesondere muss das Zahnrad der Antriebsquelle nicht geändert werden. Wenn das Zahnrad der Antriebsquelle eine Anzahl Zi 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*(Zi + 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 has been found that in this way the gear ratio of the transmission can be changed to a favorable 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 need to be changed. If the gear of the drive source has a number Zi of teeth and the crankshaft meshing therewith has a number Z 2 of teeth, then the pitch of the axes of rotation of the gears is given by m * (Zi + Z 2 ) / 2, where m is the Modulus of the transmission is. 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 the transmission ratio of the transmission can be changed without changes to the drive source must be made. Especially with the claimed offset, the number of teeth remains integer, so that consuming adjustment measures account for the gears. Thus, the claimed feature of the integer multiple of m / 2 is not interpreted purely mathematically, but also explicitly includes even distances dl, which differ from an integer multiple of m / 2 only so far that the gear of the crankshaft within the mechanical tolerances can intervene without changes to the size of the teeth for the purpose of transmitting power in the gear of the drive source.
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. Nach dem Stand der Technik waren die Zahnanzahlen beider Zahnräder identisch, also Zi = Z2. Wird Z2 jetzt über Zi 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 Zi. 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 we- niger Kolbenhub im Zylinder erforderlich, um diese Leistung zu erbringen. DerIn this case, the transmission advantageously has a transmission ratio between 1 to 0.9 and 1 to 1.1 from the drive source to the crankshaft. Typical heavy-duty engines provide a gear with a modulus between 1.5 and 3.5 mm for driving a compressor. Thus, the gear ratio per tooth by which the tooth number Z 2 of the gear on the crankshaft is changed can be changed by 2 to 3%. According to the prior art, the tooth numbers of both gears were identical, ie Zi = Z 2 . If Z 2 is now increased beyond Zi, the piston moves slower in the compressor. Thus, the operating noise of the compressor can be reduced by the price that the air flow per unit time decreases. Advantageously, therefore, the transmission ratio is greater than 1, ie Z 2 is smaller than Zi. Then the piston of the compressor moves faster. Given specifications for airflow per unit time (eg, 200 liters per minute at 12 bar system pressure and 700 rpm engine), less piston stroke in the cylinder is required to achieve this performance. Of the
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. 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. 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. Compressor can be made more compact. Because of the cramped space in the engine compartment of Kolbenhubraum is a constant bottleneck. Typically are only 360 to 400 cm 3 per cylinder are available. Advantageously, the pivotally mounted against the crankshaft connecting rod eye of the connecting rod is freely movable in a circle about the axis of the crankshaft. The wear due to bearing forces is then particularly low. Furthermore, this embodiment takes up very little space in the crankcase of the crankcase. Advantageously, the axis of rotation of the crankshaft against the central axis of the cylinder space by an amount dl between 1 and 5 mm, preferably between 2 and 3 mm, offset. Then, in addition, the effect can be exploited that upon rotation of the crankshaft about its axis, the deflection of the connecting rod from the central axis of the cylinder is reduced. This deflection acts on the piston with a force component which presses against the wall of the cylinder and thus increases wear due to friction between cylinder and piston.
Allgemein bietet die Erfindung den Vorteil, dass Kompressoren eines begrenzten Umfangs an Leistungsklassen mit einem hohen Gleichteilanteil kostengünstig gefer- tigt werden könne. Es ist zur Einstellung der Leistung lediglich der Versatz dl zwischen der Drehachse der Kurbelwelle und der Mittelachse des Zylinders anzupassen. Spezieller Beschreibungsteil In general, the invention offers the advantage that compressors of a limited scope of power classes with a high common-mode component can be produced inexpensively. It is to adjust the power only the offset dl between the axis of rotation of the crankshaft and the center axis of the cylinder adapt. Special description part
Nachfolgend wird der Gegenstand der Erfindung anhand von Figuren erläutert, ohne dass der Gegenstand der Erfindung hierdurch beschränkt wird. Es ist gezeigt: The subject matter of the invention will be explained below with reference to figures, without the subject matter of the invention being limited thereby. It is shown:
Figur 1 Prinzipskizze des erfindungsgemäßen Kompressors mit Versatz zwischen Kurbelwelle und Mittelachse des Zylinderraums. Figure 1 schematic diagram of the compressor according to the invention with offset between the crankshaft and center axis of the cylinder chamber.
Figur 2 Integration eines erfindungsgemäßen Kompressors in einen vorgege- b enen Motorraum . FIG. 2 shows the integration of a compressor according to the invention into a given engine compartment.
Figur 1 zeigt eine Prinzipskizze eines erfindungsgemäßen Kompressors. In dem Kurbelgehäuse 1,5 befindet sich eine Zylinderbohrung la. Ihre Mittelachse ist mit X bezeichnet. In der Zylinderbohrung bewegt sich ein Kolben 2. Er ist über eine Pleu- elstange 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. 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 Zi 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 Mo- torraum 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. FIG. 1 shows a schematic diagram of a compressor according to the invention. In the crankcase 1.5 is a cylinder bore la. Its central axis is marked with 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 3 a is rotatably supported against the piston 2. The lower connecting rod 3b is rotatably supported against a crank pin 4a which rotates with the crankshaft 4 about the central axis Y thereof. If the crankshaft 4 rotates, the lower connecting-rod eye 3b of the connecting rod 3 describes a circle about the central axis Y of the crankshaft 4. The axes X and Y run perpendicular to one another; the axis X runs in the plane of the drawing, the axis Y perpendicular to the plane of the drawing. 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 in an engine compartment as shown in FIG 2. At a predetermined location, the engine block 9 is of fixed dimensions, which provides a predetermined gear 8 for driving the compressor. The gearwheel rotates about an axis Z, which is perpendicular to the plane of the drawing and has a distance A from the center plane X of the cylinder space running in the plane of the drawing. The crankshaft 4 is of a gear 7 driven that engages 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 have a distance B from each other which is smaller than the distance A. Therefore, the gear 7 has a number Z 2 of teeth, which is smaller than the tooth number Zi of the gear 8 on the engine block 9. The gear 7 thus rotates faster than the gear 8. As a result, the compressor ejects a larger volume of air per unit time. This change was made without having to change the size and shape of the compressor. Also, the flange 6, with which it is mounted in the engine compartment, is located in the same place as in a compressor according to the prior art, the gear 7 was the same size as the gear. 8

Claims

Patentansprüche claims
Kompressor mit einem Kurbelgehäuse (1,5), in dem eine Kurbelwelle (4) in einem Kurbelraum drehbar gelagert ist, wobei das Kurbelgehäuse (1,5) mindestens einen Zylinderraum (la) enthält, in dem ein durch eine PleuelstangeCompressor with a crankcase (1,5), in which a crankshaft (4) is rotatably mounted in a crank chamber, wherein the crankcase (1,5) at least one cylinder chamber (la) contains, in which a through a connecting rod
(3) exzentrisch an der Kurbelwelle (4) gelagerter Kolben (2) zu einer Hin- und Herbewegung anregbar ist und wobei die Kurbelwelle (4) durch ein Zahnradgetriebe (7,8), das einen Modulus m aufweist, mit einer Antriebsquelle (9) verbunden ist, indem das an der Kurbelwelle (4) angeordnete Zahnrad (7) in das Zahnrad (8) der Antriebsquelle (9) eingreift, (3) eccentrically on the crankshaft (4) mounted piston (2) is excitable to a reciprocating motion and wherein the crankshaft (4) by a gear transmission (7,8) having a Modulus m, with a drive source (9 ) is connected by the arranged on the crankshaft (4) gear (7) engages the gear (8) of the drive source (9),
dadurch gekennzeichnet, dass characterized in that
die Drehachse (Y) der Kurbelwelle (4) gegen die Mittelachse (X) des Zylinderraums (la) um einen Betrag dl versetzt ist, der ein ganzzahliges Vielfaches von m/2 ist. the axis of rotation (Y) of the crankshaft (4) is offset from the central axis (X) of the cylinder space (1a) by an amount dl which is an integer multiple of m / 2.
Kompressor nach Anspruch 1, Compressor according to claim 1,
dadurch gekennzeichnet, dass das Getriebe (7,8) ein Übersetzungsverhältnis zwischen 1 :0,9 und 1 : 1,1 von der Antriebsquelle (9) auf die Kurbelwellecharacterized in that the transmission (7, 8) has a gear ratio between 1: 0.9 and 1: 1.1 from the drive source (9) to the crankshaft
(4) aufweist. (4).
Kompressor nach einem der Ansprüche 1 bis 2, Compressor according to one of claims 1 to 2,
dadurch gekennzeichnet, dass das Übersetzungsverhältnis größer als 1 ist. Kompressor nach einem der Ansprüche 1 bis 3, characterized in that the gear ratio is greater than 1. Compressor according to one of claims 1 to 3,
dadurch gekennzeichnet, dass das gegen die Kurbelwelle (4) drehbar gelagerte Pleuelauge (3b) der Pleuelstange (3) frei in einem Kreis um die Achse (Y) der Kurbelwelle (4) beweglich ist. characterized in that against the crankshaft (4) rotatably mounted connecting rod eye (3b) of the connecting rod (3) freely in a circle about the axis (Y) of the crankshaft (4) is movable.
5. Kompressor nach einem der Ansprüche 1 bis 4, 5. Compressor according to one of claims 1 to 4,
dadurch gekennzeichnet, dass die Drehachse (Y) der Kurbelwelle (4) gegen die Mittelachse (X) des Zylinderraums (la) um einen Betrag dl zwischen 1 und 5 mm, bevorzugt zwischen 2 und 3 mm, versetzt ist.  characterized in that the axis of rotation (Y) of the crankshaft (4) against the central axis (X) of the cylinder space (la) by an amount dl between 1 and 5 mm, preferably between 2 and 3 mm, is offset.
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 true EP3221584A1 (en) 2017-09-27
EP3221584B1 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
CN104755760B (en) * 2012-10-26 2017-05-31 住友橡胶工业株式会社 Compressor assembly and the puncture repair kit using the compressor assembly
CN105829678B (en) * 2013-12-19 2019-10-11 沃尔沃卡车集团 Internal combustion engine
US20170350476A1 (en) * 2015-02-24 2017-12-07 Illinois Tool Works Inc. Compressor for discharging a medium

Also Published As

Publication number Publication date
BR112017009922A2 (en) 2018-01-02
CN107110139A (en) 2017-08-29
EP3221584B1 (en) 2020-01-15
DE102014116805A1 (en) 2016-05-19
WO2016079031A1 (en) 2016-05-26
US20180291883A1 (en) 2018-10-11
US10753349B2 (en) 2020-08-25
JP2017534802A (en) 2017-11-24
CN107110139B (en) 2019-10-11

Similar Documents

Publication Publication Date Title
EP1736666B1 (en) Pump gear
DE102018010272B4 (en) generator
EP3221584B1 (en) Compressor with adjustable gear ratio to the driving means
EP2188496B1 (en) Compressed air motor
DE102005030725A1 (en) compressor unit
EP0148348A1 (en) Piston compressor
DE102017200918B4 (en) Crank mechanism for a reciprocating internal combustion engine
WO2015071204A1 (en) Oscillatorily driven machine tool
WO2004005712A1 (en) Reciprocating piston machine
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
DE10058924C2 (en) Low-vibration multi-stage piston compressor
DE112004000749B4 (en) fluid pump
DE102007007683A1 (en) Component e.g. oil pump, drive for internal-combustion engine of motor vehicle, has main drive shaft coupled with aggregate drive shaft by gear mechanism that is formed as hydraulic 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
DE102005026119B4 (en) Reibarmer reciprocating engine with adjustable compression end space
DE102011119447B4 (en) Double eccentric crank mechanism with conrod gear
DE102013015836B4 (en) Hot gas engine (Stirling engine) with weight-compensated displacer moved by two eccentrics
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"
DE102015220130B4 (en) Compressor device for an internal combustion engine, drive device, motor vehicle
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
DE102014203127A1 (en) compressor
DE202010011581U1 (en) Reciprocating engine with periodically changing piston stroke and crank lever crank mechanism
EP3019770A1 (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
DE202009010555U1 (en) reciprocating engine

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