US20120301288A1 - Charging device - Google Patents
Charging device Download PDFInfo
- Publication number
- US20120301288A1 US20120301288A1 US13/511,334 US201013511334A US2012301288A1 US 20120301288 A1 US20120301288 A1 US 20120301288A1 US 201013511334 A US201013511334 A US 201013511334A US 2012301288 A1 US2012301288 A1 US 2012301288A1
- Authority
- US
- United States
- Prior art keywords
- bearing
- recess
- shaft
- diameter
- exhaust gas
- 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.)
- Abandoned
Links
- 230000008859 change Effects 0.000 claims description 9
- 238000000034 method Methods 0.000 description 9
- 238000004519 manufacturing process Methods 0.000 description 8
- 238000002485 combustion reaction Methods 0.000 description 7
- 238000004512 die casting Methods 0.000 description 6
- 230000008901 benefit Effects 0.000 description 3
- 238000005266 casting Methods 0.000 description 2
- 230000003247 decreasing effect Effects 0.000 description 2
- 238000000227 grinding Methods 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 238000005553 drilling Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000005495 investment casting Methods 0.000 description 1
- 238000000465 moulding Methods 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 125000006850 spacer group Chemical group 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D17/00—Regulating or controlling by varying flow
- F01D17/10—Final actuators
- F01D17/12—Final actuators arranged in stator parts
- F01D17/14—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits
- F01D17/16—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of nozzle vanes
- F01D17/165—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of nozzle vanes for radial flow, i.e. the vanes turning around axes which are essentially parallel to the rotor centre line
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
- F02C6/04—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output
- F02C6/10—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output supplying working fluid to a user, e.g. a chemical process, which returns working fluid to a turbine of the plant
- F02C6/12—Turbochargers, i.e. plants for augmenting mechanical power output of internal-combustion piston engines by increase of charge pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2220/00—Application
- F05D2220/40—Application in turbochargers
Definitions
- the invention relates to a charging device, in particular turbocharger, of a vehicle, with a turbine having at least one flow guide vane for a medium, wherein the flow guide vane is pivotably mounted on a housing component of the charging device by means of a bearing shaft seated in a recess of the housing component.
- the charging device is for example an exhaust gas turbocharger having a variable or adjustable turbine geometry (BTG).
- BBG variable or adjustable turbine geometry
- Such a variable turbine geometry with rotatably mounted flow guide vanes is prior art in modern combustion engines for passenger cars and commercial vehicles—in particular with diesel combustion engines.
- By using the variable turbine geometry a clear improvement of the response behaviour of the combustion engine can be achieved.
- By means of the adjustable flow guide vane a flow cross section of the turbine can be changed.
- the flow cross section is adapted for example to the operating state of the combustion engine and/or of the charging device in order to achieve a reduction of the consumption and of the emissions.
- the change of the flow cross section serves for adapting the damming-up behaviour of the turbine.
- the flow guide vane is rotatably or pivotably fastened to the housing component—which can also be called bearing disc.
- the objective here is to mount the guide vane in such a manner that over a lifespan of the charging device, a jamming of the flow guide vane is prevented, so that easy-to-operate adjusting is ensured.
- the flow guide vane is to perform a defined movement within the exhaust gas flow flowing through the turbine.
- the flow guide vanes are actuated via an adjusting device, wherein a force required for the adjustment is introduced from outside a housing of the charging device.
- the flow guide vane is mounted by means of the bearing shaft, wherein the latter engages in the recess of the housing component. It is known from the prior art to embody the diameter of the bearing shaft constant over the entire length of the bearing shaft or to provide the bearing shaft with a constriction, so that it is not in contact with an inner wall of the recess at this location. The ease of operation of the bearing shaft can be improved in this manner. Such a design however renders the production of the flow guide vane or of the bearing shaft in a casting method, in particular die casting method, difficult.
- the charging device with the features mentioned in Claim 1 has the advantage that a similar and more cost effective production is possible and in particular die casting methods can be employed without slide tools being necessary for demoulding the bearing shaft.
- this is achieved in that the bearing shaft and the recess form at least two bearing locations with different diameters that are spaced from each other in axial direction.
- Both the recess of the housing part as well as the bearing shaft preferentially have a round cross section. Jointly they form the at least two bearing locations.
- the bearing location and the inner wall of the recess are in tactile contact with each other in the region of the bearing location at the most.
- the bearing shaft is not in tactile contact with the inner wall of the recess over its entire longitudinal extension, but only in certain parts or sections, by means of which a torque (rotational resistance) counteracting an adjusting torque is reduced.
- the diameter of the bearing shaft is called shaft diameter and the diameter of the recess, recess diameter. It is now immaterial if shaft diameter and/or recess diameter of the bearing locations differ from each other. It can be provided, both, that the shaft diameter remains constant over the entire length of the bearing shaft while the recess diameter changes in order to achieve the different diameters of the bearing locations, and also that the shaft diameter changes, while the recess diameter remains constant.
- the bearing shaft at the bearing locations has different shaft diameters and/or the recess at the bearing locations has different recess diameters.
- the flow guide vane or the bearing shaft can be produced with moulding production processes, without a reworking such as for example grinding being necessary.
- a MIM or a similar process is preferred.
- the bearing locations with the different diameters are formed at least through a change of the shaft diameter. In this manner, a slide tool can be omitted, which is otherwise necessary for demoulding the bearing shaft from a casting mould used for the production.
- a further development of the invention provides that the bearing location having the larger diameter is arranged on the side facing the flow guide vane. Starting out from the flow guide vane, the diameter of the bearing location therefore diminishes. In particular when the different diameters of the bearing locations are formed through different shaft diameters, the demoulding of the flow guide vane or of the bearing shaft can be facilitated in this manner.
- a further development of the invention provides that between the bearing locations a continuous change of the shaft diameter and/or of the recess diameter is provided.
- a sudden change of the shaft diameter or of the recess diameter is avoided, in order to keep the notch effect as small as possible.
- a local stress concentration could occur at the location concerned, by means of which the load on the material at this location would be significantly increased.
- the continuous diameter change is preferably provided.
- a further development of the invention provides that in the region of at least one of the bearing locations the recess diameter substantially corresponds to the shaft diameter.
- the bearing shaft in this region is directly mounted on the housing component, i.e. is in tactile contact with the latter. It is thus not necessary to provide an additional intermediate element between bearing shaft and the inner wall of the recess in order to form the bearing location.
- the shaft diameter is slightly smaller than the recess diameter in order to make possible an easily operated adjustment of the flow guide vanes by means of the bearing shaft.
- the recess is present as stepped recess and/or as recess with constant diameter.
- the recess can be achieved for example by means of bores having at least two different diameters.
- a stepped bore is present.
- the recess has a constant diameter, while the different diameters of the bearing locations are realised with different shaft diameters.
- the bearing shaft is assigned at least one bearing element.
- the bearing element is arranged in the region of the bearing location or assigned to the latter, so that the bearing element can at least co-form the bearing location.
- the bearing element can be present as ring element, which is fastened on the bearing shaft or in the recess. With such a ring element it is achieved that the recess diameter can be kept constant over the length of the recess, while the different diameters of the bearing locations are realised with different shaft diameters.
- bearing element is non-positively, positively and/or materially connected to the bearing shaft.
- bearing element can be likewise introduced into the recess of the housing where it is non-positively, positively and/or materially fastened.
- the bearing element is part of an adjusting device for the bearing shaft, so that the adjusting device at least in certain regions interacts with the bearing shaft and the recess in order to form the bearing location.
- the bearing element is part of an adjusting lever of the adjusting device. This adjusting lever is used in order to apply a torque onto the bearing shaft and thus adjust the flow guide vane.
- the bearing element engages about the bearing shaft at least in certain regions and simultaneously engages in the recess. In this manner, the recess diameter in turn can remain constant and different shaft diameters can be present in order to form the different diameters of the bearing locations.
- a further development of the invention provides that the bearing shaft and the guide vane are produced as a common component, in particular by means of a die casting method. Such a procedure is particularly preferred when the bearing shaft, starting out from the flow guide vane, has a decreasing shaft diameter.
- a slide mould for demoulding can be omitted during the production of the component so that both the production of the common component as well as a provision of the die casting mould for producing the component is easier and more cost-effectively to accomplish.
- FIG. 1 a charging device in cross section
- FIG. 2 a flow guide vane known from the prior art with a bearing shaft in a first embodiment
- FIG. 3 the flow guide vane with a bearing shaft in a second embodiment known from the prior art
- FIG. 4 the flow guide vane with a bearing shaft in a first embodiment according to the invention
- FIG. 5 the flow guide vane with a bearing shaft in a second embodiment according to the invention.
- FIG. 1 shows a charging device 1 with a turbine 2 , in particular exhaust gas turbine, which comprises a turbine wheel 3 .
- the turbine wheel 3 is subject to a radial onflow via an adjustable vane system 4 , an outflow from the turbine wheel 3 takes place axially (in FIG. 1 to the right).
- the adjustable vane system 4 comprises at least one flow guide vane 5 , which is arranged in the flow path of the exhaust gas flowing onto the turbine wheel 3 .
- the flow guide vane 5 is pivotably mounted by means of a bearing shaft 6 .
- the bearing shaft 6 is seated in a recess 7 of a housing component 8 —which is part of a housing 9 of the turbine 2 .
- the housing component 8 is for example a bearing disc 10 of the charging device 1 .
- a cover disc 11 Opposite the bearing disc 10 , a cover disc 11 is provided. Between bearing disc 10 and cover disc 11 the flow guide vane 5 is arranged. For adjusting the flow guide vane an adequate spacing between bearing disc 10 and cover disc 11 is necessary. In order to ensure this, a spacer 12 is additionally provided between bearing disc 10 and cover disc 11 .
- the flow guide vane 5 preferentially has a minor spacing both from the bearing disc 10 as well as from the cover disc 11 , in order to make possible in this way a reliable and easy-to-operate adjusting of the flow guide vane 5 .
- an adjusting device 13 is provided and connected to the bearing shaft 6 in a rotationally fixed manner.
- a torque can be applied to the bearing shaft 6 and thus the flow guide vane 5 adjusted.
- an onflow angle of the turbine wheel 3 can be adjusted corresponding to a load state of a combustion engine (not shown), which is assigned to the charging device 1 .
- a combustion engine not shown
- the flow cross section in a flow channel 14 in which the flow guide vane 5 is arranged, can be reduced.
- the onflow speed of the turbine wheel 3 is sufficiently high despite the low exhaust gas mass flow through the charging device 1 or the turbine 2 in order to drive the turbine wheel 3 .
- the flow cross section of the flow channel 14 is increased with high loading of the combustion engine, which is synonymous with a large exhaust gas mass flow, so that the turbine 2 does not generate an unnecessarily high flow resistance or pressure loss and the energy contained in the exhaust gas is advantageously available for driving the turbine wheel 3 .
- the turbine wheel 3 driven by the exhaust gas in turn drives for example a compressor wheel (not shown) of the charging device 1 via a shaft 15 .
- FIG. 2 shows a first embodiment of the flow guide vane 5 know from the prior art with the bearing shaft 6 .
- the latter is rotatably mounted in the recess 7 of the housing component 8 or the bearing disc 10 .
- the recess 7 has a constant recess diameter d 1 and the bearing shaft 6 a constant bearing shaft diameter d 2 .
- the bearing shaft diameter substantially corresponds to the recess diameter or is slightly smaller, so that an easy-to-operate adjusting of the flow guide vane 5 by means of the bearing shaft 6 is ensured.
- FIG. 3 shows a second embodiment of the flow guide vane 5 and the bearing shaft 6 known from the prior art.
- the bearing shaft 6 is mounted in the recess 7 of the housing component 8 .
- the recess diameter d 1 is constant.
- the shaft diameter d 2 is also substantially constant.
- the bearing shaft 6 has a constriction 16 in a region, so that the diameter is reduced here (indicated in FIG. 3 by the interrupted lines).
- a first bearing location 17 and a second bearing location 18 are present, at which the bearing shaft 6 is in tactile contact with the inner wall of the recess 7 .
- the rotational resistance of the bearing shaft i.e. the torque, which counteracts an adjusting torque used for adjusting the flow guide vane 5 can be reduced, since the support area of the bearing shaft 6 on the inner wall of the recess 7 is reduced.
- FIG. 4 shows a first embodiment of the flow guide vane 5 and the bearing shaft 6 according to the invention.
- the bearing locations 17 and 18 have different diameters.
- the diameter can for example be defined by the diameter with which the bearing shaft 6 enters into tactile contact with the inner wall of the recess 7 for forming the bearing locations 17 and 18 .
- the diameter of the bearing locations 17 and 18 can be assumed with the shaft diameter in the region of the bearing locations 17 and 18 .
- the diameter can also be defined as mean value of shaft diameter and recess diameter.
- the recess 7 is a stepped recess 19 or stepped bore. This can be easily produced in that two drilling operations with different diameters are carried out. It is provided that the bearing shaft 6 in the region of the first bearing location 17 , which is located on the side of the bearing shaft 6 facing the flow guide vane 5 , has a larger diameter than in the region of the second bearing location 18 . Thus, both a stepped bearing shaft 6 as well as a stepped recess 7 are present, which jointly form the bearing locations 17 and 18 .
- the flow guide vane 5 and the bearing shaft 6 are produced as a common component 20 .
- the stepped embodiment of the bearing shaft 6 with the diameters decreasing starting out from the flow guide vane 5 is advantageous: by stepping the diameters of the bearing shaft 6 a demoulding of the flow guide vane 5 and of the bearing shaft 6 from a die casting mould is easily possible without a slide having to be provided. Above all, no damages of the bearing shaft 6 occur during the demoulding, so that reworking (for example precision turning and/or grinding) is not necessary.
- the recess has the recess diameter d 1 and the bearing shaft 6 the shaft diameter d 2 .
- the recess diameter d′ 1 and the shaft diameter d′ 2 are present.
- d′ 1 ⁇ d 1 and d′ 2 ⁇ d 2 applies.
- the bearing disc 10 By means of the bearing disc 10 , a mounting of the flow guide vane 5 is initially achieved. It is subjected to hot exhaust gas on the side facing the flow guide vane 5 and thus serves for the unilateral limitation of the flow channel 14 (turbine space). Together with the contour of the flow guide vane 5 and the cover disc 11 , it forms the nozzle geometry of the turbine 2 . Jointly with these, it is thus responsible to a high degree for the efficiency of the turbine 2 .
- FIG. 5 shows a second embodiment of the flow guide vane 5 and the bearing shaft 6 according to the invention.
- the recess 7 however has no stepping, i.e. is not a stepped recess 19 .
- the recess 7 rather has a constant diameter d 1 .
- a bearing element 21 which offsets the difference between the shaft diameter d′ 2 and the recess diameter d 1 , is therefore arranged.
- the bearing element 21 for example is a ring element, i.e. ring-shaped.
- the inner diameter of the ring element in this case substantially corresponds to the shaft diameter and the outer one to the recess diameter.
- deviations in each case of the inner and/or outer diameter can be provided in order to ensure the easy-to-operate adjusting of the flow guide vane 5 .
- the bearing element 21 can be fastened either on the bearing shaft 6 or in the recess 7 . In the exemplary embodiment shown here it is pressed onto the bearing shaft 6 , i.e. non-positively or frictionally connected with the latter.
- the bearing element 21 is part of the adjusting device 13 and thereby operationally connected to an adjusting lever 22 .
- the adjusting lever 22 is actuated, by means of which a torque is imposed on the bearing shaft 6 , which causes the adjustment of the flow guide vane 5 .
- the exemplary embodiments of the flow guide vane 5 and bearing shaft 6 described by means of the FIGS. 4 and 5 have advantages with regard to the production as already described above, since they can be easily produced as common component 20 .
- the different diameters of the bearing locations 17 and 18 however bring about a clear reduction of the rotational resistance during an adjusting of the flow guide vane 5 .
- the difference between the shaft diameter and the recess diameter in the region of the second bearing location 18 can in turn be offset by the bearing element 21 in this case.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical Kinetics & Catalysis (AREA)
- General Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Supercharger (AREA)
- Control Of Turbines (AREA)
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102009047006A DE102009047006A1 (de) | 2009-11-23 | 2009-11-23 | Aufladeeinrichtung |
DE102009047006.9 | 2009-11-23 | ||
PCT/EP2010/066921 WO2011061077A1 (de) | 2009-11-23 | 2010-11-05 | Aufladeeinrichtung |
Publications (1)
Publication Number | Publication Date |
---|---|
US20120301288A1 true US20120301288A1 (en) | 2012-11-29 |
Family
ID=43709204
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US13/511,334 Abandoned US20120301288A1 (en) | 2009-11-23 | 2010-11-05 | Charging device |
Country Status (6)
Country | Link |
---|---|
US (1) | US20120301288A1 (zh) |
EP (1) | EP2504530B1 (zh) |
JP (1) | JP2013511661A (zh) |
CN (1) | CN102725482B (zh) |
DE (1) | DE102009047006A1 (zh) |
WO (1) | WO2011061077A1 (zh) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20150071762A1 (en) * | 2013-09-12 | 2015-03-12 | Bosch Mahle Turbo Systems Gmbh | Exhaust gas turbocharger with turbine |
US20150110607A1 (en) * | 2012-09-13 | 2015-04-23 | Ihi Corporation | Variable nozzle unit and variable geometry system turbocharger |
US20160195006A1 (en) * | 2015-01-07 | 2016-07-07 | Borgwarner Inc. | Variable turbine geometry turbocharger vane ring assembly retention device |
US20160215687A1 (en) * | 2015-01-22 | 2016-07-28 | Bosch Mahle Turbo Systems Gmbh & Co. Kg | Method for producing a variable turbine geometry |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102011077135A1 (de) * | 2011-06-07 | 2012-12-13 | Bosch Mahle Turbo Systems Gmbh & Co. Kg | Variable Turbinen-/Verdichtergeometrie |
DE102011079580A1 (de) * | 2011-07-21 | 2013-01-24 | Bosch Mahle Turbo Systems Gmbh & Co. Kg | Variable Turbinen-/Verdichtergeometrie und zugehöriges Herstellverfahren |
CN103375197B (zh) * | 2012-04-17 | 2016-12-07 | 博世马勒涡轮系统有限两合公司 | 可变涡轮/压缩机几何结构 |
DE102016226036A1 (de) * | 2016-12-22 | 2018-06-28 | Bosch Mahle Turbo Systems Gmbh & Co. Kg | Ladeeinrichtung |
CN112594012A (zh) * | 2020-11-30 | 2021-04-02 | 苏州诺迅汽车部件有限公司 | 用于涡轮增压器的喷嘴环 |
Citations (7)
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US3521974A (en) * | 1968-03-26 | 1970-07-28 | Sulzer Ag | Turbine blade construction |
US3542484A (en) * | 1968-08-19 | 1970-11-24 | Gen Motors Corp | Variable vanes |
US5601401A (en) * | 1995-12-21 | 1997-02-11 | United Technologies Corporation | Variable stage vane actuating apparatus |
US20030147743A1 (en) * | 2002-02-07 | 2003-08-07 | Snecma Moteurs | Stator blade pivoting arrangement in a turbomachine |
US20040047727A1 (en) * | 2002-09-05 | 2004-03-11 | Costas Vogiatzis | Cambered vane for use in turbochargers |
US20070172347A1 (en) * | 2006-01-23 | 2007-07-26 | Abb Turbo Systems Ag | Adjustable guide device |
US20100104423A1 (en) * | 2008-10-23 | 2010-04-29 | Emmanuel Severin | Turbocharger Vane |
Family Cites Families (18)
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BE496713A (zh) * | 1949-07-01 | |||
US2857092A (en) * | 1951-05-25 | 1958-10-21 | Gen Motors Corp | Variable compressor vanes |
DE1004766B (de) | 1954-09-23 | 1957-03-21 | Voith Gmbh J M | Einrichtung zur mechanischen Verstellung der Laufrad- oder Leitschaufeln bzw. Jalousieklappen von Stroemungsmaschinen, insbesondere Axialventilatoren |
US3033519A (en) * | 1958-09-12 | 1962-05-08 | United Aircraft Corp | Turbine nozzle vane construction |
US3325087A (en) * | 1965-04-28 | 1967-06-13 | David R Davis | Stator casing construction for gas turbine engines |
CH470590A (de) * | 1967-02-10 | 1969-03-31 | Sulzer Ag | Verfahren zur Montage eines mehrstufigen Axialverdichters und Montagering zur Durchführung des Verfahrens |
JPH0352987Y2 (zh) * | 1984-10-04 | 1991-11-19 | ||
DE59205387D1 (de) * | 1991-09-19 | 1996-03-28 | Asea Brown Boveri | Axialdurchströmte Turbine |
US5947681A (en) | 1997-03-17 | 1999-09-07 | Alliedsignal Inc. | Pressure balanced dual axle variable nozzle turbocharger |
DE19752534C1 (de) * | 1997-11-27 | 1998-10-08 | Daimler Benz Ag | Radialdurchströmte Abgasturboladerturbine |
US6210106B1 (en) * | 1999-04-30 | 2001-04-03 | General Electric Company | Seal apparatus for gas turbine engine variable vane |
FR2835295B1 (fr) * | 2002-01-29 | 2004-04-16 | Snecma Moteurs | Dispositif de commande d'aube a angle de calage variable a liaison par pincement pour redresseur de compresseur de turbomachine |
DE10262006B4 (de) * | 2002-03-05 | 2005-09-22 | Borgwarner Turbo Systems Gmbh | Turbolader für Fahrzeuge mit verbesserter Aufhängung für den Betätigungsmechanismus der variablen Düsen |
DE10225679A1 (de) * | 2002-06-10 | 2003-12-18 | Rolls Royce Deutschland | Lagerring zur Lagerung von Schaufelfüßen von verstellbaren Statorschaufeln im Hochdruckverdichter einer Gasturbine |
EP1794416B1 (en) * | 2004-09-21 | 2017-12-13 | Honeywell International Inc. | Variable nozzle turbine comprising pressure balanced vanes and method of operation |
DE202005008606U1 (de) * | 2005-06-02 | 2005-08-04 | Borgwarner Inc., Auburn Hills | Verstellwellenanordnung eines Turboladers |
EP1811135A1 (de) * | 2006-01-23 | 2007-07-25 | ABB Turbo Systems AG | Verstellbare Leitvorrichtung |
DE102008000859B4 (de) * | 2008-03-27 | 2020-09-03 | BMTS Technology GmbH & Co. KG | Abgasturbolader für ein Kraftfahrzeug |
-
2009
- 2009-11-23 DE DE102009047006A patent/DE102009047006A1/de not_active Withdrawn
-
2010
- 2010-11-05 WO PCT/EP2010/066921 patent/WO2011061077A1/de active Application Filing
- 2010-11-05 JP JP2012540351A patent/JP2013511661A/ja active Pending
- 2010-11-05 EP EP10778987.7A patent/EP2504530B1/de not_active Not-in-force
- 2010-11-05 CN CN201080053151.3A patent/CN102725482B/zh active Active
- 2010-11-05 US US13/511,334 patent/US20120301288A1/en not_active Abandoned
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3521974A (en) * | 1968-03-26 | 1970-07-28 | Sulzer Ag | Turbine blade construction |
US3542484A (en) * | 1968-08-19 | 1970-11-24 | Gen Motors Corp | Variable vanes |
US5601401A (en) * | 1995-12-21 | 1997-02-11 | United Technologies Corporation | Variable stage vane actuating apparatus |
US20030147743A1 (en) * | 2002-02-07 | 2003-08-07 | Snecma Moteurs | Stator blade pivoting arrangement in a turbomachine |
US20040047727A1 (en) * | 2002-09-05 | 2004-03-11 | Costas Vogiatzis | Cambered vane for use in turbochargers |
US20070172347A1 (en) * | 2006-01-23 | 2007-07-26 | Abb Turbo Systems Ag | Adjustable guide device |
US20100104423A1 (en) * | 2008-10-23 | 2010-04-29 | Emmanuel Severin | Turbocharger Vane |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20150110607A1 (en) * | 2012-09-13 | 2015-04-23 | Ihi Corporation | Variable nozzle unit and variable geometry system turbocharger |
US9903379B2 (en) * | 2012-09-13 | 2018-02-27 | Ihi Corporation | Variable nozzle unit and variable geometry system turbocharger |
US20150071762A1 (en) * | 2013-09-12 | 2015-03-12 | Bosch Mahle Turbo Systems Gmbh | Exhaust gas turbocharger with turbine |
US20160195006A1 (en) * | 2015-01-07 | 2016-07-07 | Borgwarner Inc. | Variable turbine geometry turbocharger vane ring assembly retention device |
US10378434B2 (en) * | 2015-01-07 | 2019-08-13 | Borgwarner Inc. | Variable turbine geometry turbocharger vane ring assembly retention device |
US20160215687A1 (en) * | 2015-01-22 | 2016-07-28 | Bosch Mahle Turbo Systems Gmbh & Co. Kg | Method for producing a variable turbine geometry |
US10190488B2 (en) * | 2015-01-22 | 2019-01-29 | Bosch Mahle Turbo Systems Gmbh & Co. Kg | Method for producing a variable turbine geometry |
Also Published As
Publication number | Publication date |
---|---|
EP2504530B1 (de) | 2019-01-09 |
CN102725482B (zh) | 2015-06-10 |
EP2504530A1 (de) | 2012-10-03 |
JP2013511661A (ja) | 2013-04-04 |
WO2011061077A1 (de) | 2011-05-26 |
DE102009047006A1 (de) | 2011-05-26 |
CN102725482A (zh) | 2012-10-10 |
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AS | Assignment |
Owner name: BOSCH MAHLE TURBO SYSTEMS GMBH & CO. KG, GERMANY Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:MAIER, DIETER;ROHRMOSER, KLAUS;KAWA, DIETER;AND OTHERS;SIGNING DATES FROM 20120601 TO 20120628;REEL/FRAME:028776/0324 |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |