EP2300711B1 - Compressor system for supplying compressed air to a utility vehicle, and method for the operation of a compressor system - Google Patents
Compressor system for supplying compressed air to a utility vehicle, and method for the operation of a compressor system Download PDFInfo
- Publication number
- EP2300711B1 EP2300711B1 EP09757291.1A EP09757291A EP2300711B1 EP 2300711 B1 EP2300711 B1 EP 2300711B1 EP 09757291 A EP09757291 A EP 09757291A EP 2300711 B1 EP2300711 B1 EP 2300711B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- compressor
- drive
- compressor system
- hydraulic pump
- gear drive
- 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
Links
- 238000000034 method Methods 0.000 title claims description 8
- 230000005540 biological transmission Effects 0.000 description 13
- 230000008878 coupling Effects 0.000 description 9
- 238000010168 coupling process Methods 0.000 description 9
- 238000005859 coupling reaction Methods 0.000 description 9
- 244000027321 Lychnis chalcedonica Species 0.000 description 2
- 238000010276 construction Methods 0.000 description 2
- 239000002826 coolant Substances 0.000 description 2
- 238000001816 cooling Methods 0.000 description 2
- 238000005457 optimization Methods 0.000 description 2
- 230000001419 dependent effect Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 239000000725 suspension Substances 0.000 description 1
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
- F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
- F04B17/05—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by internal-combustion engines
-
- 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
- F04B23/00—Pumping installations or systems
- F04B23/04—Combinations of two or more pumps
-
- 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
- F04B23/00—Pumping installations or systems
- F04B23/04—Combinations of two or more pumps
- F04B23/08—Combinations of two or more pumps the pumps being of different types
- F04B23/10—Combinations of two or more pumps the pumps being of different types at least one pump being of the reciprocating positive-displacement type
-
- 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
- F04B35/002—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 driven by internal combustion engines
-
- 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
- F04B41/00—Pumping installations or systems specially adapted for elastic fluids
- F04B41/06—Combinations of two or more pumps
Definitions
- the invention relates to a compressor system for compressed air supply of a commercial vehicle with a compressor, a clutch and a hydraulic pump, wherein the compressor system is drivable via a drive train and the compressor is completely decoupled by the clutch of a drive motor.
- the invention further relates to a method for operating a compressor system for supplying compressed air to a commercial vehicle with a compressor, a clutch and a hydraulic pump, wherein the compressor system is driven by a drive train and the compressor is completely decoupled from the drive motor by the clutch.
- Modern commercial vehicles have many subsystems that are operated with compressed air. These include, for example, a compressed air operated service brake or air suspension.
- a compressed air supply device is normally provided in the commercial vehicle, which comprises a compressor.
- This compressor is mechanically driven by a drive motor of the commercial vehicle.
- the coupling of the compressor is normally via a toothing at one end of the crankshaft of the drive motor.
- the compressor itself has a further crankshaft, on whose side facing away from the drive side toothing often a hydraulic pump, for example a power steering pump, is arranged.
- connection of the hydraulic pump to the shaft of the compressor is carried out with the help of a radial play balance bearing, for example a Maltese cross, or a multi-tooth bearing, which can handle a higher torque, but tolerates a lesser clearance compared to the Maltese cross.
- a radial play balance bearing for example a Maltese cross, or a multi-tooth bearing, which can handle a higher torque, but tolerates a lesser clearance compared to the Maltese cross.
- a clutch is often provided in modern commercial vehicles, which is able to save energy to completely decouple the compressor from the drive motor.
- this is not tolerable for safety reasons.
- Another option is to operate the steering assistance purely electrically. It is then no longer mechanically powered by the drive motor power steering pump and the pump requires its own electric motor. This is in principle feasible, but the electric motor must provide a large power of about 50 KW, which is why he also claimed appropriate space and weight. Furthermore, the energy consumption is less favorable.
- the compressor system builds on the generic state of the art in that the drive train comprises a gear drive, via which the hydraulic pump is drivable and that the coupling between the gear drive and the compressor is arranged.
- Arranging the coupling between the gear drive and the compressor does not mean the spatial position of the coupling between the gear drive and the compressor.
- the term "between” rather describes the path of the transmitted force.
- the power is transmitted from the gear drive via the clutch to the compressor.
- the coupling is also arranged in space between the gear drive and the compressor.
- the arrangement of the clutch between the gear drive and the compressor, a decoupling of the compressor of the drive motor is possible without affecting the drive of the hydraulic pump.
- As an additional mechanical component only the gear drive in the drive train is necessary, via which a power take-off for the hydraulic pump is provided.
- the mechanical connection of the compressor system to the drive motor can remain unchanged compared to a conventional compressor system.
- the compressor and the hydraulic pump are integrated in a common housing.
- the placement of compressor and hydraulic pump in a common housing facilitates the cooling of both components, as a common cooling system can be used.
- the common housing can be cooled as a whole.
- the gear drive has a ratio equal to one.
- the compressor and the hydraulic pump can be operated at different speeds. This allows separate optimization of the compressor and hydraulic pump for the vehicle.
- a further advantage is that the compressor system comprises a further drive on the side facing away from the wheel drive side of the compressor.
- the further drive can be designed, for example, as a further wheel drive, as a belt drive or as a chain drive.
- a connection option for the hydraulic pump which is not limited by the compressor in terms of the available space.
- a second connection possibility can arise, which can be used to connect a further auxiliary unit, for example a coolant pump.
- the gear drive is partially mounted with a bushing and that the socket at the same time supports a crankshaft of the compressor.
- the gears used in the gear drive are usually rotatably mounted, wherein the simultaneous use of a bearing point of a gear of the gear drive for supporting the crankshaft simplifies the mechanical construction of the compressor system.
- the gear drive and the crankshaft are freely rotatably coupled to each other via the socket.
- the freely rotating coupling between the gear drive and the crankshaft allows only the switching off of the compressor via the clutch.
- the generic method for operating a compressor system is further developed in that the hydraulic pump is driven by a drive train of the drive train and that the drive train between the gear drive and the compressor is disconnected to decouple the compressor from the drive motor.
- the advantages and particularities of the compressor system according to the invention are also implemented in the context of a method. This also applies to the following particularly preferred embodiments of the method according to the invention.
- the hydraulic pump is driven via the gear drive with a ratio not equal to one.
- the compressor is driven by a further drive, which is arranged behind the gear drive seen from the drive train.
- FIG. 1 shows a schematic representation of a commercial vehicle with a compressor system according to the invention.
- the illustrated commercial vehicle 20 includes a drive motor 18 and is driven by the drive motor 18 via a drive train 28. From the drive train 28, a drive train 16 for a compressor system 10 is branched off via a drive 32, which comprises a compressor 12 and a hydraulic pump 14. The compressor system 10 is driven as a whole by the drive train 16, wherein via a gear drive 30, a power take-off 24 is provided for driving the hydraulic pump 14. Between the Rädertrieb 30 and the compressor 12, a clutch 22 is arranged, which can be opened or closed, without affecting the operation of the hydraulic pump 14. The switching of the clutch 22 can be taken over by a control unit, not shown, which, for example, part a compressed air treatment plant of the commercial vehicle 20 may be. The ratio of the gear drive 30 can be freely selected to allow a separate optimization of hydraulic pump 14 and compressor 12.
- FIG. 2 shows an exterior view of a compressor system according to the invention.
- the illustrated compressor system 10 is integrated in a common housing 26, wherein in the upper region of the compressor and in the lower region, the hydraulic pump is arranged.
- FIG. 3 shows a cross section through a compressor system according to the invention.
- the illustrated compressor system 10 is a cross-section through a section of FIG FIG. 2 illustrated outside view.
- the compressor 12 is arranged in the upper region and the power steering pump 14 in the lower region.
- the drive train 16 enters behind a standard connection port 34 in the common housing 26 of the compressor system 10, wherein subsequently via a gear drive 30, a power take-off 24 is provided for driving a hydraulic pump 14.
- a clutch 22 is further arranged.
- FIG. 4 shows an external view of a compressor system according to the invention without attached hydraulic pump. Shown is the arranged in the housing 26 compressor 12, which is separable via a clutch control port 36 of the drive train not visible in this illustration. In the foreground are still visible a connection flange 38 and a further connection flange 38 'to which the hydraulic pump can be connected. Depending on requirements, it is conceivable that two hydraulic pumps on the connecting flanges 38, 38 'simultaneously to operate, or supply other ancillaries with drive energy.
- FIG. 5 shows a cross section through a compressor system according to the invention without attached hydraulic pump. This is shown from the FIG. 4 already known compressor system in a sectional view.
- the wheel drive 30 and a further wheel drive 44 which are arranged on two different sides of the compressor 12, are visible.
- the clutch 22 is disposed between the further gear train 44 and the compressor 12 and is operable via the clutch control port 36.
- the transmission ratio of the further gear drive 44 can be chosen freely analogous to the transmission ratio of the gear drive 30.
- the transmitted from the drive train, not shown on the gear drive 30 force is transmitted via a shaft 42 to the other gear drive 44. From there it can be tapped at the connecting flanges 38, 38 ', or is transmitted via the coupling 22 to the compressor 12.
- crankshaft 46 assigned to the compressor 12 and the wheel drive 30 takes place via a bush 40 which supports both a gear of the gear drive 30 and the crankshaft 46.
- the use of two separate sockets, which can then be positioned arbitrarily, is also possible.
- the storage takes place freely rotating, so that the gear of the gear drive 30 can rotate independently of the crankshaft 46.
- FIG. 6 shows a schematic structure of a power transmission path in a compressor system according to the invention.
- Power is transmitted in the form of a torque to the gear drive 30 via the drive train 16.
- the illustrated gear drive 30 comprises three gears, which are shown without their teeth for the sake of simplicity.
- the force introduced into the wheel drive 30 is transmitted via the shaft 42 to the further wheel drive 44, which has two connecting flanges 38, 38 ', to which auxiliary units, not shown, for example the hydraulic pump, can be connected.
- the crankshaft 46 of the compressor is driven via the clutch 22, which is mounted on the wheel drive 30 side facing by means of a sleeve 40.
- the sleeve 40 stores at the same time a gear wheel of the gear drive 30, wherein the crankshaft 46 and the gear wheel of the gear drive 30 are independently rotatable.
- the sleeve 40 thus supports the crankshaft 46 in the compressor housing 26 and the gear of the gear drive 30 on the crankshaft 46 freely rotating.
- FIG. 7 shows a schematic representation of a commercial vehicle with a second embodiment of a compressor system according to the invention.
- the driving force for the in FIG. 7 shown compressor system 10 is transmitted directly from the drive 32 to the gear drive 30.
- a drive train for example in the form of a wave, can be omitted.
- a gear of the drive 32 directly engage in a gear of the gear drive 30 and thus supply the compressor system 10 with drive energy.
- FIG. 8 shows a schematic representation of a commercial vehicle with a third embodiment of a compressor system according to the invention.
- illustrated embodiment of the compressor system 10 is based on the already in FIG. 6 described power transmission path.
- drive energy is introduced into a gear drive 30, wherein a not explicitly illustrated gear of the gear drive 30 is supported by a bushing 40.
- the force introduced into the gear drive 30 is transmitted via a shaft 42 to a further gear drive 44 and supplied from there via a coupling 22 to a compressor 12.
- the crankshaft of the compressor 12 is mounted on the side facing away from the coupling 22 by a sleeve 40 '.
- FIG. 8 shows a schematic representation of a commercial vehicle with a third embodiment of a compressor system according to the invention.
- illustrated embodiment of the compressor system 10 is based on the already in FIG. 6 described power transmission path.
- a drive 30 and a drive train 16 drive energy is introduced into a gear drive 30, wherein a not explicitly illustrated gear of the gear drive 30 is supported by a bush
- the sleeve 40 ' is provided, which is arranged spatially spaced from the sleeve 40.
- a connecting flange 38 and a further connecting flange 38 ' are furthermore provided, to which a hydraulic pump 14 and a pump 14' can be connected.
- the pump 14 ' stands symbolically for any of the Drive motor 18 to be driven auxiliary unit, for example, a coolant pump.
- FIG. 9 shows a schematic representation of a commercial vehicle with a fourth embodiment of a compressor system according to the invention.
- the FIG. 9 illustrated embodiment differs from the in FIG. 8 illustrated embodiment in the way how torque is introduced into the compressor system 10. Analogous to the in FIG. 7 torque is transferred directly from the drive 32 to the gear drive 30, wherein an intermediate shaft is omitted.
- FIG. 10 shows a second embodiment of a power transmission path in a compressor system according to the invention.
- the illustrated power transmission path differs from that FIG. 3 mentioned embodiment in particular in that the gear drive 30 comprises three gears and the drive train 16 and the crankshaft 46 are not coupled together to a single gear of the gear drive 30. In this way, the speed of the compressor and the power take-off 24 in the design of the gear drive 30 can be varied within wide ranges.
- FIG. 11 shows a second external view of a compressor system according to the invention.
- the illustrated compressor system 10 is different from that FIG. 2 known compressor system 10 in particular by the mounting position of a in FIG. 11 ancillaries, not shown, for example, a hydraulic pump.
- the accessory is mounted on the port flange 38 so as to occupy a position between a cylinder head 48 of the compressor and the port flange 38 on the gear train inside the housing 26.
- FIG. 12 shows a third embodiment of a power transmission path in a compressor system according to the invention.
- the illustrated Kraftauertragungsweg differs from the embodiment known from Figure by the use of a belt drive 50 with a belt 52 and an additional tensioning wheel, the function of the FIG. 6 known further wheel drive takes over.
- On the representation of connecting flanges for the connection of ancillary units was omitted for better clarity. Analogous to FIG. 6 However, appropriate connection options are foreseeable.
- FIG. 13 shows a fourth embodiment of a power transmission path in a compressor system according to the invention.
- a chain drive 54 is used with a chain 56 and an additional tensioning wheel.
- Analogous to FIG. 12 are also possible connections for ancillaries.
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)
- Applications Or Details Of Rotary Compressors (AREA)
- Electromagnetic Pumps, Or The Like (AREA)
- Details Of Reciprocating Pumps (AREA)
- Auxiliary Drives, Propulsion Controls, And Safety Devices (AREA)
Description
Die Erfindung betrifft ein Kompressorsystem zur Druckluftversorgung eines Nutzfahrzeugs mit einem Kompressor, einer Kupplung und einer Hydraulikpumpe, wobei das Kompressorsystem über einen Antriebsstrang antreibbar ist und der Kompressor durch die Kupplung vollständig von einem Antriebsmotor entkoppelbar ist.The invention relates to a compressor system for compressed air supply of a commercial vehicle with a compressor, a clutch and a hydraulic pump, wherein the compressor system is drivable via a drive train and the compressor is completely decoupled by the clutch of a drive motor.
Die Erfindung betrifft weiterhin ein Verfahren zum Betreiben eines Kompressorsystems zur Druckluftversorgung eines Nutzfahrzeugs mit einem Kompressor, einer Kupplung und einer Hydraulikpumpe, wobei das Kompressorsystem über einen Antriebsstrang angetrieben wird und der Kompressor durch die Kupplung vollständig von dem Antriebsmotor entkoppelt wird.The invention further relates to a method for operating a compressor system for supplying compressed air to a commercial vehicle with a compressor, a clutch and a hydraulic pump, wherein the compressor system is driven by a drive train and the compressor is completely decoupled from the drive motor by the clutch.
Moderne Nutzfahrzeuge weisen viele Teilsysteme auf, die mit Druckluft betrieben werden. Dazu gehört beispielsweise eine druckluftbetriebene Betriebsbremse beziehungsweise eine Luftfederung. Um die Versorgung dieser Teilsysteme mit Druckluft sicherzustellen, ist normalerweise eine Druckluftversorgungseinrichtung in dem Nutzfahrzeug vorgesehen, die einen Kompressor umfasst. Dieser Kompressor wird mechanisch von einem Antriebsmotor des Nutzfahrzeugs angetrieben. Die Kopplung des Kompressors erfolgt normalerweise über eine Verzahnung an einem Ende der Kurbelwelle des Antriebsmotors. Der Kompressor selbst besitzt eine weitere Kurbelwelle, an deren der antriebsseitigen Verzahnung abgewandten Seite häufig eine Hydraulikpumpe, zum Beispiel eine Lenkhilfepumpe, angeordnet ist. Der Anschluss der Hydraulikpumpe an die Welle des Kompressors erfolgt mit Hilfe eines Radialspielausgleichlagers, zum Beispiel einem Malteser Kreuz, oder einem Vielzahnlager, welches ein höheres Drehmoment verkraftet, jedoch im Vergleich mit dem Malteser Kreuz ein geringeres Spiel toleriert.Modern commercial vehicles have many subsystems that are operated with compressed air. These include, for example, a compressed air operated service brake or air suspension. In order to ensure the supply of compressed air to these subsystems, a compressed air supply device is normally provided in the commercial vehicle, which comprises a compressor. This compressor is mechanically driven by a drive motor of the commercial vehicle. The coupling of the compressor is normally via a toothing at one end of the crankshaft of the drive motor. The compressor itself has a further crankshaft, on whose side facing away from the drive side toothing often a hydraulic pump, for example a power steering pump, is arranged. The connection of the hydraulic pump to the shaft of the compressor is carried out with the help of a radial play balance bearing, for example a Maltese cross, or a multi-tooth bearing, which can handle a higher torque, but tolerates a lesser clearance compared to the Maltese cross.
Zusätzlich wird in modernen Nutzfahrzeugen häufig eine Kupplung vorgesehen, die zur Energieeinsparung in der Lage ist, den Kompressor vollständig vom Antriebsmotor zu entkoppeln. Bei der herkömmlichen Anordnung der Hydraulikpumpe auf der Abtriebsseite der Kurbelwelle des Kompressors bedeutet dies, dass gleichzeitig mit dem Kompressor auch die Hydraulikpumpe vom Antrieb abgekoppelt wird. Dies führt jedoch dazu, dass beispielsweise keine Lenkunterstützung in Form einer Servolenkung für das Nutzfahrzeug mehr verfügbar wäre. Dies ist aus Sicherheitsgründen jedoch nicht tolerierbar.In addition, a clutch is often provided in modern commercial vehicles, which is able to save energy to completely decouple the compressor from the drive motor. In the conventional arrangement of the hydraulic pump on the output side of the crankshaft of the compressor, this means that simultaneously with the compressor and the hydraulic pump is disconnected from the drive. However, this means that, for example, no steering assistance in the form of a power steering for the commercial vehicle would be more available. However, this is not tolerable for safety reasons.
Es sind verschiedene Alternativen zur Lösung dieses Problems bekannt. Eine Möglichkeit besteht darin, die Lenkunterstützung zurückzufahren, wenn der Kompressor abgeschaltet ist. Bei dieser Variante wird davon ausgegangen, dass der Kompressor hauptsächlich auf Autobahnen ausgekuppelt werden kann. Auf diesen Strecken ist wegen der geringen Radien der Kurven auch die Lenkunterstützung nicht zwingend erforderlich. Falls jedoch ein Lenkmanöver, zum Beispiel zum Ausweichen, durchgeführt werden muss, fehlt die Lenkhilfe und der Kompressor müsste zugeschaltet werden.There are several alternatives known to solve this problem. One possibility is to reverse the steering assist when the compressor is off. In this variant, it is assumed that the compressor can be disengaged mainly on highways. On these routes, the steering assistance is not absolutely necessary because of the small radii of the curves. However, if a steering maneuver, for example, to avoid, must be performed, the power steering is missing and the compressor would have to be switched on.
Eine weitere Möglichkeit besteht darin, die Lenkunterstützung rein elektrisch zu betreiben. Es ist dann keine vom Antriebsmotor mechanisch angetriebene Lenkhilfepumpe mehr vorhanden und die Pumpe benötigt einen eigenen Elektromotor. Dies ist prinzipiell realisierbar, aber der Elektromotor muss eine große Leistung von etwa 50 KW erbringen, weshalb er auch entsprechenden Platz und Gewicht beansprucht. Weiterhin ist der Energieverbrauch ungünstiger.Another option is to operate the steering assistance purely electrically. It is then no longer mechanically powered by the drive motor power steering pump and the pump requires its own electric motor. This is in principle feasible, but the electric motor must provide a large power of about 50 KW, which is why he also claimed appropriate space and weight. Furthermore, the energy consumption is less favorable.
Es ist daher die Aufgabe der vorliegenden Erfindung das gattungsgemäße Kompressorsystem derart weiterzubilden, dass die vollständige Entkopplung des Kompressors von dem Antriebsmotor bei gleichzeitigem Betrieb der Hydraulikpumpe ohne großen mechanischen Mehraufwand möglich ist.It is therefore the object of the present invention to develop the generic compressor system such that the complete decoupling of the compressor from the drive motor with simultaneous operation of the hydraulic pump is possible without much additional mechanical effort.
Diese Aufgabe wird durch die Merkmale der unabhängigen Ansprüche gelöst.This object is solved by the features of the independent claims.
Vorteilhafte Ausgestaltungen und Weiterbildungen der Erfindungen ergeben sich aus den abhängigen Ansprüchen.Advantageous embodiments and further developments of the invention will become apparent from the dependent claims.
Das erfindungsgemäße Kompressorsystem baut auf dem gattungsgemäßen Stand der Technik dadurch auf, dass der Antriebsstrang einen Rädertrieb umfasst, über den die Hydraulikpumpe antreibbar ist und dass die Kupplung zwischen dem Rädertrieb und dem Kompressor angeordnet ist. Unter dem Anordnen der Kupplung zwischen dem Rädertrieb und dem Kompressor wird dabei nicht die räumliche Lage der Kupplung zwischen dem Rädertrieb und dem Kompressor verstanden. Der Begriff "zwischen" beschreibt vielmehr den Weg der übertragenen Kraft. Die Kraft wird von dem Rädertrieb über die Kupplung auf den Kompressor übertragen. Es ist jedoch denkbar, dass aufgrund baulicher Bedürfnisse die Kupplung auch in räumlicher Hinsicht zwischen dem Rädertrieb und dem Kompressor angeordnet ist. Durch die Anordnung der Kupplung zwischen dem Rädertrieb und dem Kompressor wird ein Entkoppeln des Kompressors von dem Antriebsmotor möglich, ohne den Antrieb der Hydraulikpumpe zu beeinträchtigen. Als zusätzliches mechanisches Bauteil ist dabei lediglich der Rädertrieb in dem Antriebsstrang notwendig, über den ein Nebenabtrieb für die Hydraulikpumpe bereitgestellt wird. Weiterhin kann der mechanische Anschluss des Kompressorsystems an den Antriebsmotor gegenüber einem herkömmlichen Kompressorsystem unverändert bleiben.The compressor system according to the invention builds on the generic state of the art in that the drive train comprises a gear drive, via which the hydraulic pump is drivable and that the coupling between the gear drive and the compressor is arranged. Arranging the coupling between the gear drive and the compressor does not mean the spatial position of the coupling between the gear drive and the compressor. The term "between" rather describes the path of the transmitted force. The power is transmitted from the gear drive via the clutch to the compressor. However, it is conceivable that due to structural needs, the coupling is also arranged in space between the gear drive and the compressor. The arrangement of the clutch between the gear drive and the compressor, a decoupling of the compressor of the drive motor is possible without affecting the drive of the hydraulic pump. As an additional mechanical component only the gear drive in the drive train is necessary, via which a power take-off for the hydraulic pump is provided. Furthermore, the mechanical connection of the compressor system to the drive motor can remain unchanged compared to a conventional compressor system.
Vorzugsweise ist dabei vorgesehen, dass der Kompressor und die Hydraulikpumpe in ein gemeinsames Gehäuse integriert sind. Die Unterbringung von Kompressor und Hydraulikpumpe in einem gemeinsamen Gehäuse erleichtert die Kühlung beider Komponenten, da ein gemeinsames Kühlsystem angewendet werden kann. Beispielsweise kann in einfacher Weise das gemeinsame Gehäuse insgesamt gekühlt werden.Preferably, it is provided that the compressor and the hydraulic pump are integrated in a common housing. The placement of compressor and hydraulic pump in a common housing facilitates the cooling of both components, as a common cooling system can be used. For example, in a simple manner, the common housing can be cooled as a whole.
Erfindungsgemäß weist der Rädertrieb eine Übersetzung ungleich Eins auf. Durch das Vorsehen einer Übersetzung ungleich Eins in dem Rädertrieb können der Kompressor und die Hydraulikpumpe mit verschiedenen Drehzahlen betrieben werden. Dadurch wird eine separate Optimierung von Kompressor und Hydraulikpumpe für das Fahrzeug ermöglicht.According to the invention, the gear drive has a ratio equal to one. By providing a gear ratio equal to one in the gear drive, the compressor and the hydraulic pump can be operated at different speeds. This allows separate optimization of the compressor and hydraulic pump for the vehicle.
Vorteilhaft ist weiterhin, dass das Kompressorsystem einen weiterer Trieb auf der dem Rädertrieb abgewandten Seite des Kompressors umfasst. Durch das Vorsehen eines weiteren Triebs auf der dem Rädertrieb abgewandten Seite des Kompressors wird eine mechanisch stabilere Konstruktion ermöglicht. Der weitere Trieb kann beispielsweise als weiterer Rädertrieb, als Riementrieb oder als Kettentrieb ausgeführt sein. Weiterhin ergibt sich auf der dem Rädertrieb abgewandten Seite des Kompressors eine Anschlussmöglichkeit für die Hydraulikpumpe, die hinsichtlich des verfügbaren Bauraums nicht durch den Kompressor beschränkt ist. Bei dieser Bauform kann auch eine zweite Anschlussmöglichkeit entstehen, die zum Anschluss eines weiteren Nebenaggregates, zum Beispiel einer Kühlmittelpumpe, verwendet werden kann.A further advantage is that the compressor system comprises a further drive on the side facing away from the wheel drive side of the compressor. By providing a further drive on the side facing away from the wheel drive side of the compressor, a mechanically more stable construction is made possible. The further drive can be designed, for example, as a further wheel drive, as a belt drive or as a chain drive. Furthermore, results on the side facing away from the wheel drive side of the compressor, a connection option for the hydraulic pump, which is not limited by the compressor in terms of the available space. In this design, a second connection possibility can arise, which can be used to connect a further auxiliary unit, for example a coolant pump.
Es kann vorgesehen sein, dass der Rädertrieb teilweise mit einer Buchse gelagert ist und dass die Buchse zugleich eine Kurbelwelle des Kompressors lagert. Die in dem Rädertrieb verwendeten Zahnräder werden üblicherweise drehbar gelagert, wobei die gleichzeitige Verwendung eines Lagerpunkts eines Zahnrads des Rädertriebs zur Lagerung der Kurbelwelle den mechanischen Aufbau des Kompressorssystems vereinfacht.It can be provided that the gear drive is partially mounted with a bushing and that the socket at the same time supports a crankshaft of the compressor. The gears used in the gear drive are usually rotatably mounted, wherein the simultaneous use of a bearing point of a gear of the gear drive for supporting the crankshaft simplifies the mechanical construction of the compressor system.
Insbesondere ist dabei vorgesehen, dass der Rädertrieb und die Kurbelwelle über die Buchse frei drehend miteinander gekoppelt sind. Die frei drehende Kopplung zwischen dem Rädertrieb und der Kurbelwelle erlaubt erst das Abschalten des Kompressors über die Kupplung.In particular, it is provided that the gear drive and the crankshaft are freely rotatably coupled to each other via the socket. The freely rotating coupling between the gear drive and the crankshaft allows only the switching off of the compressor via the clutch.
Das gattungsgemäße Verfahren zum Betreiben eines Kompressorsystems wird dadurch weiterentwickelt, dass die Hydraulikpumpe über einen Rädertrieb von dem Antriebsstrang angetrieben wird und dass der Antriebsstrang zwischen dem Rädertrieb und dem Kompressor getrennt wird, um den Kompressor von dem Antriebsmotor zu entkoppeln. Auf diese Weise werden die Vorteile und Besonderheiten des erfindungsgemäßen Kompressorsystems auch im Rahmen eines Verfahrens umgesetzt. Dies gilt auch für die nachfolgend angegebenen besonders bevorzugten Ausführungsformen des erfindungsgemäßen Verfahrens.The generic method for operating a compressor system is further developed in that the hydraulic pump is driven by a drive train of the drive train and that the drive train between the gear drive and the compressor is disconnected to decouple the compressor from the drive motor. In this way, the advantages and particularities of the compressor system according to the invention are also implemented in the context of a method. This also applies to the following particularly preferred embodiments of the method according to the invention.
Dieses ist in nützlicher Weise dadurch weitergebildet, dass der Kompressor und die Hydraulikpumpe in ein gemeinsames Gehäuse integriert werden.This is usefully further developed in that the compressor and the hydraulic pump are integrated into a common housing.
Erfindungsgemäß ist vorgesehen, dass die Hydraulikpumpe über den Rädertrieb mit einer Übersetzung ungleich Eins angetrieben wird.According to the invention, it is provided that the hydraulic pump is driven via the gear drive with a ratio not equal to one.
Besonders bevorzugt ist, dass der Kompressor über einen weiteren Trieb angetrieben wird, der von dem Antriebsstrang aus gesehen hinter dem Rädertrieb angeordnet ist.It is particularly preferred that the compressor is driven by a further drive, which is arranged behind the gear drive seen from the drive train.
Die Erfindung wird nun mit Bezug auf die begleitenden Zeichnungen anhand besonders bevorzugter Ausführungsformen beispielhaft erläutert.The invention will now be described by way of example with reference to the accompanying drawings by way of particularly preferred embodiments.
Es zeigen:
- Figur 1
- eine schematische Darstellung eines Nutzfahrzeugs mit einem erfindungsgemäßen Kompressorsystem;
- Figur 2
- eine Außenansicht eines erfindungsgemäßen Kompressorsystems;
- Figur 3
- einen Querschnitt durch ein erfindungsgemäßes Kompressorsystem;
- Figur 4
- eine Außenansicht eines erfindungsgemäßen Kompressorsystems ohne angebaute Hydraulikpumpe;
- Figur 5
- einen Querschnitt durch ein erfindungsgemäßes Kompressorsystem ohne angebaute Hydraulikpumpe;
- Figur 6
- einen schematischen Aufbau eines Kraftübertragungsweges in einem erfindungsgemäßen Kompressorsystem;
- Figur 7
- eine schematische Darstellung eines Nutzfahrzeugs mit einer zweiten Ausführungsform eines erfindungsgemäßen Kompressorsystems;
- Figur 8
- eine schematische Darstellung eines Nutzfahrzeugs mit einer dritten Ausführungsform eines erfindungsgemäßen Kompressorsystems;
- Figur 9
- eine schematische Darstellung eines Nutzfahrzeugs mit einer vierten Ausführungsform eines erfindungsgemäßen Kompressorsystems;
Figur 10- eine zweite Ausführungsform eines Kraftübertragungsweges in einem erfindungsgemäßen Kompressorsystem;
- Figur 11
- eine zweite Außenansicht eines erfindungsgemäßen Kompressorsystems;
Figur 12- eine dritte Ausführungsform eines Kraftübertragungsweges in einem erfindungsgemäßen Kompressorsystem und
- Figur 13
- eine vierte Ausführungsform eines Kraftübertragungsweges in einem erfindungsgemäßen Kompressorsystem.
- FIG. 1
- a schematic representation of a commercial vehicle with a compressor system according to the invention;
- FIG. 2
- an external view of a compressor system according to the invention;
- FIG. 3
- a cross section through a compressor system according to the invention;
- FIG. 4
- an external view of a compressor system according to the invention without attached hydraulic pump;
- FIG. 5
- a cross section through a compressor system according to the invention without attached hydraulic pump;
- FIG. 6
- a schematic structure of a power transmission path in a compressor system according to the invention;
- FIG. 7
- a schematic representation of a commercial vehicle with a second embodiment of a compressor system according to the invention;
- FIG. 8
- a schematic representation of a commercial vehicle with a third embodiment of a compressor system according to the invention;
- FIG. 9
- a schematic representation of a commercial vehicle with a fourth embodiment of a compressor system according to the invention;
- FIG. 10
- a second embodiment of a power transmission path in a compressor system according to the invention;
- FIG. 11
- a second external view of a compressor system according to the invention;
- FIG. 12
- a third embodiment of a power transmission path in a compressor system according to the invention and
- FIG. 13
- A fourth embodiment of a power transmission path in a compressor system according to the invention.
In den folgenden Zeichnungen bezeichnen gleiche Bezugszeichen gleiche oder gleichartige Teile.In the following drawings, like reference characters designate like or similar parts.
Insbesondere sind keine weiteren Modifikationen im Bereich des Antriebsstrangs 16 erforderlich, wenn an Stelle eines gattungsgemäßen Kompressorsystems ein erfindungsgemäßes Kompressorsystem verwendet wird.In particular, no further modifications in the area of the
Die in der vorstehenden Beschreibung, in den Zeichnungen sowie in den Ansprüchen offenbarten Merkmale der Erfindung können sowohl einzeln als auch in beliebiger Kombination für die Verwirklichung der Erfindung wesentlich sein.The features of the invention disclosed in the foregoing description, in the drawings and in the claims may be essential to the realization of the invention both individually and in any combination.
- 1010
- Kompressorsystemcompressor system
- 1212
- Kompressorcompressor
- 1414
- Hydraulikpumpehydraulic pump
- 14'14 '
- Pumpepump
- 1616
- Antriebsstrangpowertrain
- 1818
- Antriebsmotordrive motor
- 2020
- Nutzfahrzeugcommercial vehicle
- 2222
- Kupplungclutch
- 2424
- NebenabtriebPTO
- 2626
- Gehäusecasing
- 2828
- Triebstrangdrive train
- 3030
- Rädertriebgear drive
- 3232
- Triebshoot
- 3434
- Verbindungsanschlussconnection port
- 3636
- KupplungssteueranschlussClutch control terminal
- 3838
- Anschlussflanschflange
- 38'38 '
- weiterer Anschlussflanschadditional connection flange
- 4040
- BuchseRifle
- 40'40 '
- weitere Buchseanother socket
- 4242
- Wellewave
- 4444
- weiterer Rädertriebanother wheel drive
- 4646
- Kurbelwellecrankshaft
- 4848
- Zylinderkopfcylinder head
- 5050
- Riementriebbelt drive
- 5252
- Riemenbelt
- 5454
- Kettentriebchain drive
- 5656
- KetteChain
Claims (8)
- Compressor system (10) for supplying a commercial vehicle (20) with compressed air, the system comprising a compressor (12), a clutch (22) and a hydraulic pump (14), wherein the compressor system (10) can be driven by the engine (18) of the commercial vehicle (20) via a drive train (16) and wherein the compressor (12) can be completely decoupled from the engine (18) by the clutch (22), wherein the drive train (16) comprises a gear drive (30) via which the hydraulic pump (14) can be driven and wherein the clutch (22) is arranged between the gear drive (30) and the compressor (12), characterised in that the gear drive (30) provides different speeds for driving the compressor (12) and the hydraulic pump (14) at two separate power takeoffs.
- Compressor system (10) according to claim 1, characterised in that the compressor (12) and the hydraulic pump (14) are integrated in a common housing (26).
- Compressor system (10) according to claim 1 or 2, characterised in that the compressor system (10) comprises a further drive (44, 50, 54) on that side of the compressor (12) which faces away from the gear drive (30).
- Compressor system (10) according to any of the preceding claims, characterised in that- the gear drive (30) is bearing-mounted partially by means of a bush (40), and- the bush (40) simultaneously serves to bearing-mount a crankshaft (46) of the compressor (12).
- Compressor system (10) according to any of the preceding claims, characterised in that the gear drive (30) and the crankshaft (46) are coupled to one another in a freely rotatable manner by means of the bush (40).
- Method for operating a compressor system (10) for supplying a commercial vehicle (20) with compressed air, the system comprising a compressor (12), a clutch (22) and a hydraulic pump (14), wherein the compressor system (10) is driven by the engine (18) of the commercial vehicle (20) via a drive train (16) and wherein the compressor (12) is completely decoupled from the engine (18) by the clutch (22), and wherein the hydraulic pump (14) is driven by the drive train (16) via a gear drive (30), and wherein the drive train (16) is separated between the gear drive (30) and the compressor (12) in order to decouple the compressor (12) from the engine (18), characterised in that different speeds for driving the compressor (12) and the hydraulic pump (14) are provided at two separate power takeoffs.
- Method according to claim 6, characterised in that the compressor (12) and the hydraulic pump (14) are integrated in a common housing (26).
- Method according to claim 6 or 7, characterised in that a further drive (44, 50, 54) is provided downstream of the gear drive (30) as viewed from the drive train (16).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102008026684 | 2008-06-04 | ||
PCT/EP2009/003995 WO2009146908A1 (en) | 2008-06-04 | 2009-06-04 | Compressor system for supplying compressed air to a utility vehicle, and method for the operation of a compressor system |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2300711A1 EP2300711A1 (en) | 2011-03-30 |
EP2300711B1 true EP2300711B1 (en) | 2016-01-13 |
Family
ID=41037845
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP09757291.1A Active EP2300711B1 (en) | 2008-06-04 | 2009-06-04 | Compressor system for supplying compressed air to a utility vehicle, and method for the operation of a compressor system |
Country Status (8)
Country | Link |
---|---|
US (1) | US8496450B2 (en) |
EP (1) | EP2300711B1 (en) |
JP (1) | JP5523449B2 (en) |
CN (1) | CN101952589B (en) |
BR (1) | BRPI0912304B1 (en) |
CA (1) | CA2723203C (en) |
DE (1) | DE102009023869A1 (en) |
WO (1) | WO2009146908A1 (en) |
Families Citing this family (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102008054164A1 (en) * | 2008-10-31 | 2010-05-12 | Knorr-Bremse Systeme für Nutzfahrzeuge GmbH | Kupplungskompressor- and power steering pump assembly and method for their control |
US8435011B2 (en) * | 2009-05-08 | 2013-05-07 | Vanair Manufacturing Inc. | Integrated compressor and pump unit and vehicles equipped therewith |
ITFI20120194A1 (en) * | 2012-10-01 | 2014-04-02 | Nuovo Pignone Srl | "A TURBINE-DRIVEN RECIPROCATING COMPRESSOR AND METHOD" |
DE102013006861A1 (en) | 2013-04-19 | 2014-10-23 | Knorr-Bremse Systeme für Nutzfahrzeuge GmbH | Compressor system with clutch |
DE102013114304A1 (en) | 2013-12-18 | 2015-06-18 | Knorr-Bremse Systeme für Nutzfahrzeuge GmbH | Compressor system with a Kolbenhubeinstellvorrichtung |
DE102013114303A1 (en) | 2013-12-18 | 2015-06-18 | Knorr-Bremse Systeme für Nutzfahrzeuge GmbH | Compressor system with a Kolbenhubeinstellvorrichtung |
EP2998581B1 (en) * | 2014-09-22 | 2017-11-15 | KNORR-BREMSE Systeme für Nutzfahrzeuge GmbH | Compressor system |
DE202014009106U1 (en) | 2014-10-20 | 2016-01-25 | Liebherr-Components Biberach Gmbh | hydraulic unit |
CN105673459B (en) * | 2016-04-05 | 2019-04-02 | 徐州徐工环境技术有限公司 | A kind of double pump compressed air source unit of dry-type road sweeper |
CN106837532A (en) * | 2017-03-27 | 2017-06-13 | 王超 | Engine and power output system |
DE102017106702B4 (en) * | 2017-03-29 | 2022-02-03 | Voith Patent Gmbh | System housing for coupling a compressor system to a drive motor |
US10563915B2 (en) * | 2017-04-03 | 2020-02-18 | John Paul Mackillop | Instrument air system and method |
DE102017120754A1 (en) | 2017-09-08 | 2019-03-14 | Voith Patent Gmbh | Compressor system and method of operating a compressor system |
DE202018104795U1 (en) | 2018-08-21 | 2019-11-26 | Saeta Gmbh & Co. Kg | motor vehicle |
DE102019126342B4 (en) * | 2019-09-30 | 2024-01-11 | Voith Patent Gmbh | Compressed air supply system for a motor vehicle |
US20210388830A1 (en) * | 2020-06-12 | 2021-12-16 | Deere & Company | Demand based hydraulic pump control system |
DE102022211418A1 (en) * | 2022-10-27 | 2024-05-02 | Zf Friedrichshafen Ag | Supply unit for a vehicle and vehicle |
Family Cites Families (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2002470C2 (en) * | 1970-01-21 | 1982-09-09 | Daimler-Benz Ag, 7000 Stuttgart | Arrangement of an air compressor on an internal combustion engine |
GB2073827B (en) * | 1980-04-10 | 1983-11-23 | Well Men Ind Co Ltd | Combined air compressor and vacuum device |
GB2136510B (en) * | 1983-03-12 | 1986-04-16 | Lucas Ind Plc | Air compressor |
JP3211626B2 (en) * | 1994-06-29 | 2001-09-25 | トヨタ自動車株式会社 | Hybrid car |
FR2724881B1 (en) | 1994-09-23 | 1997-01-03 | Renault | DEVICE FOR DRIVING ACCESSORIES OF A MOTOR VEHICLE COMBUSTION ENGINE |
US5497742A (en) * | 1994-12-19 | 1996-03-12 | Midland Brake, Inc. | Drive through crankshaft |
DE10036504B4 (en) | 1999-08-02 | 2011-05-19 | Schaeffler Technologies Gmbh & Co. Kg | powertrain |
US6981855B2 (en) * | 2002-09-30 | 2006-01-03 | Sandvik Ab | Drilling rig having a compact compressor/pump assembly |
DE102004062586A1 (en) | 2004-10-18 | 2006-06-14 | Schaeffler Kg | Release device for a shift disconnect clutch on motor vehicles |
DE102005013027A1 (en) | 2005-03-22 | 2006-10-26 | Knorr-Bremse Systeme für Nutzfahrzeuge GmbH | Drive train for a compressor and a hydraulic pump |
EP1830094B1 (en) | 2006-03-03 | 2008-04-30 | Zf Friedrichshafen Ag | Clutch release device for a friction clutch of a motor vehicule with a multi part push sleeve |
KR100783778B1 (en) * | 2006-05-24 | 2007-12-10 | 유성기업 주식회사 | An air compressor |
DE102006033428A1 (en) * | 2006-07-19 | 2008-01-31 | Knorr-Bremse Systeme für Nutzfahrzeuge GmbH | System with a compressor and a consumer in a motor vehicle |
-
2009
- 2009-06-04 WO PCT/EP2009/003995 patent/WO2009146908A1/en active Application Filing
- 2009-06-04 EP EP09757291.1A patent/EP2300711B1/en active Active
- 2009-06-04 JP JP2011512020A patent/JP5523449B2/en not_active Expired - Fee Related
- 2009-06-04 CN CN200980106212.5A patent/CN101952589B/en active Active
- 2009-06-04 BR BRPI0912304-0A patent/BRPI0912304B1/en active IP Right Grant
- 2009-06-04 DE DE102009023869A patent/DE102009023869A1/en not_active Ceased
- 2009-06-04 CA CA2723203A patent/CA2723203C/en not_active Expired - Fee Related
-
2010
- 2010-12-03 US US12/959,444 patent/US8496450B2/en active Active
Also Published As
Publication number | Publication date |
---|---|
JP5523449B2 (en) | 2014-06-18 |
WO2009146908A1 (en) | 2009-12-10 |
CN101952589B (en) | 2016-01-20 |
CN101952589A (en) | 2011-01-19 |
CA2723203C (en) | 2016-10-11 |
DE102009023869A1 (en) | 2009-12-17 |
BRPI0912304B1 (en) | 2019-11-19 |
US20110135510A1 (en) | 2011-06-09 |
US8496450B2 (en) | 2013-07-30 |
BRPI0912304A2 (en) | 2015-10-13 |
EP2300711A1 (en) | 2011-03-30 |
JP2011522163A (en) | 2011-07-28 |
CA2723203A1 (en) | 2009-12-10 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP2300711B1 (en) | Compressor system for supplying compressed air to a utility vehicle, and method for the operation of a compressor system | |
DE102009006523B4 (en) | Electric axle arrangement | |
EP2551234B1 (en) | Drive device for a crane | |
EP2176085B1 (en) | Drive train for a motor vehicle | |
WO2014033137A1 (en) | Mechanical and electric drive train of a motor vehicle and motor vehicle with mechanical and electric drive train | |
DE102011055192B4 (en) | generator unit | |
EP2256247A1 (en) | Road finisher | |
EP3246187A1 (en) | Hybrid drive for a motor vehicle, in particular for a commercial vehicle | |
DE102005003077B4 (en) | Drive unit for a motor vehicle | |
EP0282784B1 (en) | Gas turbine installation for helicopters | |
EP1556634A1 (en) | Motor vehicle drive device | |
DE102007001841A1 (en) | Drive train retrofitting method for e.g. hybrid vehicle, involves demounting retarder from gear box assembly of motor vehicle, and mounting electric motor in place of retarder, where motor is mounted on or at gear of gear box assembly | |
EP3246188A1 (en) | Commercial vehicle with a parallel hybrid drive train | |
AT517965B1 (en) | Arrangement of ancillaries in an internal combustion engine | |
EP3829912A1 (en) | Hybrid drive device for a motor vehicle, and motor vehicle | |
EP3658397B1 (en) | Electric axle drive unit for a motor vehicle, and associated commercial vehicle | |
DE102015008835A1 (en) | Drive device for a motor vehicle, in particular a passenger car | |
AT518419A4 (en) | Secondary drive of an internal combustion engine | |
EP3590749A1 (en) | Electric drive system and method for operating same | |
DE102012007623B4 (en) | motor-gear unit | |
DE102020109781A1 (en) | Hybrid vehicle drive train with two-electric machine transmission for serial drive and hybrid vehicle | |
EP1770000B1 (en) | Motor vehicle comprising a power steering pump and an air compressor | |
EP2986850B1 (en) | Compressor system having a coupling | |
DE102019208378A1 (en) | Rail vehicle drive train and rail vehicle | |
DE102020006782A1 (en) | Drive device for a motor vehicle, in particular for a passenger car |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
17P | Request for examination filed |
Effective date: 20110104 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): 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 SE SI SK TR |
|
AX | Request for extension of the european patent |
Extension state: AL BA RS |
|
RIN1 | Information on inventor provided before grant (corrected) |
Inventor name: HEBRARD, GILLES Inventor name: MELLAR, JOERG |
|
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 |
|
RIN1 | Information on inventor provided before grant (corrected) |
Inventor name: MELLAR, JOERG Inventor name: HEBRARD, GILLES |
|
INTG | Intention to grant announced |
Effective date: 20150804 |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): 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 SE SI SK TR |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D Free format text: NOT ENGLISH |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: EP |
|
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: AT Ref legal event code: REF Ref document number: 770710 Country of ref document: AT Kind code of ref document: T Effective date: 20160215 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R096 Ref document number: 502009012044 Country of ref document: DE |
|
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: FP |
|
REG | Reference to a national code |
Ref country code: LT Ref legal event code: MG4D |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 8 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
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: 20160113 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: 20160414 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: 20160113 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: 20160413 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: 20160113 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
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: 20160513 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: 20160113 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: 20160113 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: 20160113 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: 20160513 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R097 Ref document number: 502009012044 Country of ref document: DE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
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: 20160113 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: 20160113 |
|
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 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
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: 20160113 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: 20160113 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: 20160113 |
|
26N | No opposition filed |
Effective date: 20161014 |
|
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: 20160630 |
|
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: 20160113 |
|
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: 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: 20160113 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: 20160413 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: MM4A |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20160630 Ref country code: LI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20160630 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20160604 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 9 |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: MM01 Ref document number: 770710 Country of ref document: AT Kind code of ref document: T Effective date: 20160604 |
|
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: 20160604 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
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: 20160113 Ref country code: HU Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO Effective date: 20090604 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 10 |
|
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: 20160113 Ref country code: TR 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: 20160113 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: 20160113 Ref country code: LU Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20160604 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: IT Payment date: 20210630 Year of fee payment: 13 Ref country code: NL Payment date: 20210621 Year of fee payment: 13 Ref country code: FR Payment date: 20210621 Year of fee payment: 13 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: GB Payment date: 20220623 Year of fee payment: 14 |
|
REG | Reference to a national code |
Ref country code: NL Ref legal event code: MM Effective date: 20220701 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: NL Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20220701 |
|
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: 20220630 |
|
P01 | Opt-out of the competence of the unified patent court (upc) registered |
Effective date: 20230508 |
|
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 NON-PAYMENT OF DUE FEES Effective date: 20220604 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20230620 Year of fee payment: 15 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: SE Payment date: 20230622 Year of fee payment: 15 |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20230604 |
|
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: 20230604 |