EP2300711A1 - Kompressorsystem zur druckluftversorgung eines nutzfahrzeugs und verfahren zum betreiben eines kompressorsystems - Google Patents
Kompressorsystem zur druckluftversorgung eines nutzfahrzeugs und verfahren zum betreiben eines kompressorsystemsInfo
- Publication number
- EP2300711A1 EP2300711A1 EP09757291A EP09757291A EP2300711A1 EP 2300711 A1 EP2300711 A1 EP 2300711A1 EP 09757291 A EP09757291 A EP 09757291A EP 09757291 A EP09757291 A EP 09757291A EP 2300711 A1 EP2300711 A1 EP 2300711A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- compressor
- drive
- compressor system
- hydraulic pump
- gear
- 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
Links
- 238000000034 method Methods 0.000 title claims abstract description 11
- 230000008878 coupling Effects 0.000 claims description 10
- 238000010168 coupling process Methods 0.000 claims description 10
- 238000005859 coupling reaction Methods 0.000 claims description 10
- 230000005540 biological transmission Effects 0.000 description 15
- 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
- 241000282376 Panthera tigris Species 0.000 description 1
- 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
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
- Compressor system for compressed air supply of a commercial vehicle and method for operating a compressor system
- 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 Kompressorsys- system for compressed air supply 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 by the clutch from the drive motor.
- 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 takes place with the aid of a radial clearance bearing, for example a Maltese cross, or a multi-tooth bearing, which can cope with 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 not 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. In this design, 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.
- This is usefully further developed in that the compressor and the hydraulic pump are integrated into a common housing.
- the hydraulic pump is driven via the gear drive with a ratio equal to one.
- the compressor is driven by a further drive, which is arranged behind the gear drive seen from the drive train.
- Figure 1 is a schematic representation of a commercial vehicle with a compressor system according to the invention
- Figure 2 is an external view of a compressor system according to the invention
- FIG. 3 shows a cross section through a compressor system according to the invention
- Figure 4 is an external view of a compressor system according to the invention without attached hydraulic pump
- Figure 5 shows a cross section through a compressor system according to the invention without attached hydraulic pump
- Figure 6 shows a schematic structure of a power transmission path in a compressor system according to the invention
- Figure 7 is a schematic representation of a commercial vehicle with a second
- Figure 8 is a schematic representation of a commercial vehicle with a third
- Figure 9 is a schematic representation of a commercial vehicle with a fourth embodiment of a compressor system according to the invention.
- Figure 10 shows a second embodiment of a power transmission path in a compressor system according to the invention.
- Figure 11 is a second external view of a compressor system according to the invention.
- Figure 12 shows a third embodiment of a power transmission path in a compressor system according to the invention.
- FIG. 13 shows a fourth embodiment of a power transmission path in a compressor system according to the invention.
- 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.
- 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.
- 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. The transmission ratio can therefore be both equal to and not equal to one in particular.
- FIG. 2 shows an external 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 the exterior view shown in FIG. Again, the compressor 12 is arranged in the upper region and the power steering pump 14 in the lower region.
- the drive train 16 enters into the common housing 26 of the compressor system 10 behind a standard connection connection 34, with a power take-off 24 then being provided for driving a hydraulic pump 14 via a gear drive 30. Between the gear drive 30 and a compressor 12, a clutch 22 is further arranged.
- a single drive train 16 with a standard connection port 34 for driving the compressor system 10 a standardized connection of the compressor system 10 to the drive motor 18 can take place.
- 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 also conceivable to use two hydraulic pumps at the connecting flanges 38, 38 'simultaneously. tiger to operate, or supply other ancillaries with drive energy.
- Figure 5 shows a cross section through a compressor system according to the invention without attached hydraulic pump. Shown is the already known from Figure 4 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 wheel drive 44 can be chosen freely analogous to the transmission ratio of the wheel drive 30 and, in particular, both equal and unequal to one.
- 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.
- 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.
- Figure 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 compressor system 10 shown in FIG. 7 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.
- the embodiment of the compressor system 10 shown in FIG. 8 is based on the power transmission path already described in FIG. Via 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 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 '.
- the sleeve 40 ' is provided in this embodiment, which is spaced from the socket 40 arranged spatially. Furthermore, a connecting flange 38 and a further connecting flange 38 ', to which a hydraulic pump 14 and a pump 14' can be connected, are provided on the further gear train 44.
- the pump 14 ' stands symbolically for any of the Drive motor 18 to be driven auxiliary unit, for example, a coolant pump.
- Figure 9 shows a schematic representation of a commercial vehicle with a fourth embodiment of a compressor system according to the invention.
- the embodiment illustrated in FIG. 9 differs from the embodiment shown in FIG. 8 in the way in which torque is introduced into the compressor system 10.
- torque is transmitted directly from the drive 32 to the gear drive 30, wherein an intermediate shaft is dispensed with.
- Figure 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 the embodiment mentioned in FIG. 3 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 differs from the compressor system 10 known from FIG. 2 in particular by the mounting position of an auxiliary unit (not shown in FIG. 11), 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.
- Figure 12 shows a third embodiment of a power transmission path in a compressor system according to the invention.
- the illustrated power transmission path differs from the embodiment known from FIG. 1 through the use of a belt drive 50 with a belt 52 and an additional tensioning wheel which performs the function of the further gear drive known from FIG takes over.
- On the representation of connecting flanges for the connection of ancillary units was omitted for better clarity. Analogous to Figure 6, however, corresponding connection options are providable.
- Figure 13 shows a fourth embodiment of a power transmission path in a compressor system according to the invention.
- a chain drive 54 with a chain 56 and an additional tensioning wheel is used in FIG. Analogous to FIG. 12, connection possibilities for auxiliary units can also be provided here.
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)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102008026684 | 2008-06-04 | ||
PCT/EP2009/003995 WO2009146908A1 (de) | 2008-06-04 | 2009-06-04 | Kompressorsystem zur druckluftversorgung eines nutzfahrzeugs und verfahren zum betreiben eines kompressorsystems |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2300711A1 true EP2300711A1 (de) | 2011-03-30 |
EP2300711B1 EP2300711B1 (de) | 2016-01-13 |
Family
ID=41037845
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP09757291.1A Active EP2300711B1 (de) | 2008-06-04 | 2009-06-04 | Kompressorsystem zur druckluftversorgung eines nutzfahrzeugs und verfahren zum betreiben eines kompressorsystems |
Country Status (8)
Country | Link |
---|---|
US (1) | US8496450B2 (de) |
EP (1) | EP2300711B1 (de) |
JP (1) | JP5523449B2 (de) |
CN (1) | CN101952589B (de) |
BR (1) | BRPI0912304B1 (de) |
CA (1) | CA2723203C (de) |
DE (1) | DE102009023869A1 (de) |
WO (1) | WO2009146908A1 (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102017120754A1 (de) | 2017-09-08 | 2019-03-14 | Voith Patent Gmbh | Kompressorsystem und Verfahren zum Betreiben eines Kompressorsystems |
Families Citing this family (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102008054164A1 (de) * | 2008-10-31 | 2010-05-12 | Knorr-Bremse Systeme für Nutzfahrzeuge GmbH | Kupplungskompressor- und Lenkhilfepumpenanordnung sowie Verfahren zu deren Steuerung |
US8435011B2 (en) * | 2009-05-08 | 2013-05-07 | Vanair Manufacturing Inc. | Integrated compressor and pump unit and vehicles equipped therewith |
ITFI20120194A1 (it) * | 2012-10-01 | 2014-04-02 | Nuovo Pignone Srl | "a turbine-driven reciprocating compressor and method" |
DE102013006861A1 (de) | 2013-04-19 | 2014-10-23 | Knorr-Bremse Systeme für Nutzfahrzeuge GmbH | Kompressorsystem mit Kupplung |
DE102013114303A1 (de) | 2013-12-18 | 2015-06-18 | Knorr-Bremse Systeme für Nutzfahrzeuge GmbH | Kompressorsystem mit einer Kolbenhubeinstellvorrichtung |
DE102013114304A1 (de) | 2013-12-18 | 2015-06-18 | Knorr-Bremse Systeme für Nutzfahrzeuge GmbH | Kompressorsystem mit einer Kolbenhubeinstellvorrichtung |
EP2998581B1 (de) * | 2014-09-22 | 2017-11-15 | KNORR-BREMSE Systeme für Nutzfahrzeuge GmbH | Verdichtersystem |
DE202014009106U1 (de) * | 2014-10-20 | 2016-01-25 | Liebherr-Components Biberach Gmbh | Hydraulikeinheit |
CN105673459B (zh) * | 2016-04-05 | 2019-04-02 | 徐州徐工环境技术有限公司 | 一种干式扫路车的双泵气源装置 |
CN106837532A (zh) * | 2017-03-27 | 2017-06-13 | 王超 | 发动机与动力输出系统 |
DE102017106702B4 (de) * | 2017-03-29 | 2022-02-03 | Voith Patent Gmbh | Systemgehäuse zur Koppelung eines Kompressorsystems mit einem Antriebsmotor |
US10563915B2 (en) * | 2017-04-03 | 2020-02-18 | John Paul Mackillop | Instrument air system and method |
DE202018104795U1 (de) | 2018-08-21 | 2019-11-26 | Saeta Gmbh & Co. Kg | Kraftfahrzeug |
DE102019126342B4 (de) * | 2019-09-30 | 2024-01-11 | Voith Patent Gmbh | Druckluftversorgungssystem für ein Kraftfahrzeug |
US20210388830A1 (en) * | 2020-06-12 | 2021-12-16 | Deere & Company | Demand based hydraulic pump control system |
DE102022211418A1 (de) * | 2022-10-27 | 2024-05-02 | Zf Friedrichshafen Ag | Versorgungseinheit für ein Fahrzeug und Fahrzeug |
Family Cites Families (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2002470C2 (de) * | 1970-01-21 | 1982-09-09 | Daimler-Benz Ag, 7000 Stuttgart | Anordnung eines Luftpressers an einer Brennkraftmaschine |
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 (ja) * | 1994-06-29 | 2001-09-25 | トヨタ自動車株式会社 | ハイブリッド車 |
FR2724881B1 (fr) | 1994-09-23 | 1997-01-03 | Renault | Dispositif d'entrainement des accessoires d'un moteur a combustion de vehicule automobile |
US5497742A (en) * | 1994-12-19 | 1996-03-12 | Midland Brake, Inc. | Drive through crankshaft |
DE10036504B4 (de) * | 1999-08-02 | 2011-05-19 | Schaeffler Technologies Gmbh & Co. Kg | Antriebsstrang |
US6981855B2 (en) * | 2002-09-30 | 2006-01-03 | Sandvik Ab | Drilling rig having a compact compressor/pump assembly |
DE102004062586A1 (de) * | 2004-10-18 | 2006-06-14 | Schaeffler Kg | Ausrückvorrichtung für eine Schalttrennkupplung an Kraftfahrzeugen |
DE102005013027A1 (de) * | 2005-03-22 | 2006-10-26 | Knorr-Bremse Systeme für Nutzfahrzeuge GmbH | Antriebsstrang für einen Kompressor und eine Hydraulikpumpe |
DE502006000716D1 (de) | 2006-03-03 | 2008-06-12 | Zahnradfabrik Friedrichshafen | Ausrückvorrichtung für eine Reibungskupplung eines Kraftfahrzeuges mit einer mehrteiligen Schiebehülse |
KR100783778B1 (ko) * | 2006-05-24 | 2007-12-10 | 유성기업 주식회사 | 에어콤프레서 |
DE102006033428A1 (de) * | 2006-07-19 | 2008-01-31 | Knorr-Bremse Systeme für Nutzfahrzeuge GmbH | System mit einem Verdichter und einem Verbraucher in einem Kraftfahrzeug |
-
2009
- 2009-06-04 CA CA2723203A patent/CA2723203C/en not_active Expired - Fee Related
- 2009-06-04 DE DE102009023869A patent/DE102009023869A1/de not_active Ceased
- 2009-06-04 JP JP2011512020A patent/JP5523449B2/ja not_active Expired - Fee Related
- 2009-06-04 BR BRPI0912304-0A patent/BRPI0912304B1/pt active IP Right Grant
- 2009-06-04 WO PCT/EP2009/003995 patent/WO2009146908A1/de active Application Filing
- 2009-06-04 EP EP09757291.1A patent/EP2300711B1/de active Active
- 2009-06-04 CN CN200980106212.5A patent/CN101952589B/zh active Active
-
2010
- 2010-12-03 US US12/959,444 patent/US8496450B2/en active Active
Non-Patent Citations (1)
Title |
---|
See references of WO2009146908A1 * |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102017120754A1 (de) | 2017-09-08 | 2019-03-14 | Voith Patent Gmbh | Kompressorsystem und Verfahren zum Betreiben eines Kompressorsystems |
Also Published As
Publication number | Publication date |
---|---|
US8496450B2 (en) | 2013-07-30 |
CA2723203C (en) | 2016-10-11 |
BRPI0912304A2 (pt) | 2015-10-13 |
JP2011522163A (ja) | 2011-07-28 |
US20110135510A1 (en) | 2011-06-09 |
DE102009023869A1 (de) | 2009-12-17 |
CN101952589A (zh) | 2011-01-19 |
CA2723203A1 (en) | 2009-12-10 |
JP5523449B2 (ja) | 2014-06-18 |
BRPI0912304B1 (pt) | 2019-11-19 |
WO2009146908A1 (de) | 2009-12-10 |
CN101952589B (zh) | 2016-01-20 |
EP2300711B1 (de) | 2016-01-13 |
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