EP1418311A1 - Ensemble stator pour turbocompresseur à géométrie variable - Google Patents

Ensemble stator pour turbocompresseur à géométrie variable Download PDF

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Publication number
EP1418311A1
EP1418311A1 EP02025181A EP02025181A EP1418311A1 EP 1418311 A1 EP1418311 A1 EP 1418311A1 EP 02025181 A EP02025181 A EP 02025181A EP 02025181 A EP02025181 A EP 02025181A EP 1418311 A1 EP1418311 A1 EP 1418311A1
Authority
EP
European Patent Office
Prior art keywords
rocker arm
ring
guide
guide vane
approximately
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP02025181A
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German (de)
English (en)
Other versions
EP1418311B1 (fr
Inventor
Georg Scholz
Jennes Jörg
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
BorgWarner Inc
Original Assignee
BorgWarner Inc
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by BorgWarner Inc filed Critical BorgWarner Inc
Priority to DE50209301T priority Critical patent/DE50209301D1/de
Priority to EP02025181A priority patent/EP1418311B1/fr
Priority to US10/706,180 priority patent/US7114919B2/en
Publication of EP1418311A1 publication Critical patent/EP1418311A1/fr
Application granted granted Critical
Publication of EP1418311B1 publication Critical patent/EP1418311B1/fr
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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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
    • 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 guide vane of variable geometry for turbines, in particular for a turbocharger.
  • the invention relates to such a guide vane, which has a ring of guide vanes arranged around a central axis, which in turn are each pivotable about a pivot axis and with their Swivel axes are mounted in a blade ring around the central axis.
  • An adjustment ring is provided for pivoting, which in turn is relative to the blade bearing ring is pivotable about the central axis, as well as a connecting gear, via that the adjustment ring with the blades for adjusting their angular position in each case their pivot axes are connected and an opening in the first of the connecting links has, in which a second link is slidably guided.
  • the invention is therefore based on the object of a connecting gear on a guide vane to create of the type mentioned above, which works more reliably, especially for the adjustment Adjustment torque exerted on the guide vanes during its adjustment approximately also corresponds to the counter-moment acting on the guide vanes.
  • this object is achieved in a surprisingly uncomplicated manner solved that the second link as pivotally guided on the associated ring Handlebar is formed, and that the second link in an approximately radial direction dips into the opening of the first link.
  • the known sliding block transmission is made by a transmission replaced, which is a combination of a steering gear (there is a swivel and a sliding movement) with a crank or crank loop gear (the immersion movement the handlebar into the opening is roughly similar to the movement of a piston a steam locomotive) and possibly referred to as "rocker arm gear” could be.
  • a transmission replaced which is a combination of a steering gear (there is a swivel and a sliding movement) with a crank or crank loop gear (the immersion movement the handlebar into the opening is roughly similar to the movement of a piston a steam locomotive) and possibly referred to as "rocker arm gear” could be.
  • this will make an almost perfect fit of the adjusting torque to the moments acting on the guide vanes.
  • the handlebar could be attached to the respective pivot shaft of a guide vane be and immerse in an opening of the first link, which is on the adjusting ring is stored.
  • the second connecting link formed as a pivotally guided handlebar on the associated ring , and the second connecting member in an approximately radial direction into the opening of the first link.
  • the simplest training of the interacting pair of handlebars and Opening could be that the handlebar is designed as a round rod, which in a cylindrical bore of the first actuator is immersed.
  • this requires one very precise guidance on a relatively short route. That's why it is preferred if the pivotable handlebar (rocker arm) has an angular cross-section, possibly with rounded corners, in particular has an approximately square cross section, because practice has shown that leadership problems do not arise with this. It is an additional axial degree of freedom of the handlebar or rocker arm is given.
  • the opening of the first adjusting member as a groove, in particular as against the Guide vanes facing groove, is formed, in which one simply in the axial direction Direction. Above all, this makes it easier to put all of the handlebars in their associated Insert openings.
  • a turbocharger 1 has a turbine housing part 2 and an associated compressor housing part 3, which along an axis of rotation R are arranged.
  • the turbine housing part 2 is partially shown in section, so that therein a vane bearing ring 6 forming a radially outer guide vane, distributed over the circumference Guide blades 7 about their pivot axes 8 passing through the blade bearing ring 6 twisted so that they form nozzle cross sections between each other, depending on the location of the guide vanes 7, namely radial (as shown) or more tangential, larger or are smaller and the turbine rotor 4 located in the middle on the axis R more or less with the supplied via a feed channel 9 and a central nozzle 10 discharged exhaust gas of an engine to a via the turbine rotor 4 to drive compressor rotor 21 seated on the same shaft.
  • an actuating device 11 In order to control the movement or the position of the guide vanes 7, there is an actuating device 11 provided.
  • This can be of any nature in itself, but it is preferred if, in a conventional manner per se, it has a control housing 12 which controls the control movement a tappet member 14 attached to it controls its movement via an adjustment gear with a link part 16 and a rocker arm 17 on a rear the paddle bearing ring 6 (left behind in Fig. 1) located adjustment ring 5 in a light Implement rotary movement of the same. the details of this link gear will be explained later.
  • the guide vanes 7 are moved with respect to the shafts 8 their rotational position relative to the turbine rotor 4 so adjusted that they are approximately tangential extending one extreme position in an approximately radially extending other extreme position are adjustable.
  • the exhaust gas supplied via the supply channel becomes one Internal combustion engine more or less fed to the turbine rotor 4 before it the axial connector 10 extending along the axis of rotation R emerges again.
  • a relatively narrow space 13 remains around the blades 7, allowing free movement to allow.
  • this bucket space 13 may not be significantly larger than that Width of the blades 7, because then the exhaust gas energy would suffer leakage losses.
  • the bucket space 13 must not be too small, because then the blades 7 could jam.
  • Fig. 2 is to clarify the interaction of the blade bearing ring only dash-dotted lines indicated, so that behind it the rocker arm 17 in circular holes 18 immerses.
  • the rocker arms 17 are each by means of pivot pins 19 mounted on the adjusting ring 5 and each extend in an approximately radial direction (from which direction, however, they swing out a little to one side and the other).
  • the adjusting ring 5 is used here instead of a pneumatic control housing from an electric motor 12 'to a slight rotary movement around the central R axis driven.
  • the electric motor 12 ' can be part of a control loop, as described in one of the above-mentioned U.S.
  • Patents 5,123,246; 5,444,980 and 6,148,793 is described, which essentially work with characteristic parameters of the internal combustion engine.
  • it may be advantageous to include the temperature of a in the control loop Include catalyst as a parameter, for example, to bypass the turbocharger By-pass line, be it via an exhaust manifold of the internal combustion engine by-pass line connecting directly to the catalyst or via a so-called Wastegate to connect to the catalyst (to heat it up quickly after starting).
  • This is an invention that is independent of the other features described here. This allows the hot exhaust gas to avoid cooling in the turbocharger directly be fed to the catalyst for heating.
  • the algorithm or link of the measured temperature value with the motor-specific values can be Fuzzy control or a neural network - i.e. thus a weighting function.
  • the pivot pins thus shift 19 by a certain angular amount compared to the stationary Swivel shafts 8 on which the guide vanes 7 are seated. But with that, too Swivel shafts with a special movement and torque characteristic within of the blade bearing ring 6 pivoted. It turns out that the maximum surface pressure of rocker arm 17 relative to the surfaces of the opening 18 or vice versa is low, so that wear is low and reliability is high. Because that Pressing is always at least approximately perpendicular to the respective surface, so that there is no one-sided burden.
  • the adjusting ring 5 is a relatively narrow ring, the inner limit of which is shown 2 is approximately where the dash-dotted contour 6 'of the blade bearing ring 6 can be seen.
  • the adjusting ring can thus be placed on the ends of the pivot shafts 8 be stored and centered. But because of the translation ratio between Adjusting ring 5 and adjusting shafts 8 the latter rotate faster than adjusting ring 5, it is advantageous to have a free at the ends of at least part of the pivot shafts 8 mount rotatable bearing roller 22, as can be seen particularly from FIG. 3.
  • rocker arms 17 are mounted on the adjusting ring 5 results in a simple one and easily producible form of the unit from guide vanes 7 and pivot shafts 8, as illustrated in FIG. 3.
  • the reverse would also be the case conceivable by a link part corresponding to part 16 instead of the pivot pin 19 arranged and the rocker arms 17 protrude at right angles from the pivot shafts would.
  • this would complicate the manufacture of the unit shown in FIG. 3.
  • the rings 5 and 6 and a mounting ring 23 can be seen. Between the mounting ring 23 and the blade bearing ring 6 extends the blade space 13 in which the Ring of guide vanes 7 is accommodated around the central axis R. In the paddle bearing ring 6 are then again the swivel shafts 8 which are not visible here (cf. FIG. 3) stored, which are preferably formed in one piece with the respective guide blade 7, such as this is also illustrated in FIG. 3.
  • a part 16 'forming the backdrop is again provided, however a groove 18 'which runs transversely to its pivot axis and is open towards the adjusting ring has, which forms the respective rocker arm 17 receiving opening.
  • the Rocker arms 17 can be particularly in this embodiment with flat surfaces on the Press the inner surface of the groove 18 'and are thus a uniform, low surface pressure exposed. In order to maintain these flat surfaces, it is advantageous if the respective rocker arms 17 which can be pivoted about the pivot pin 19 have an angular cross section, at most with rounded corners, in particular an approximately square cross-section has.
  • FIGS. 5-7 There is in everyone the figures only a single backdrop part 16 in different positions together with the associated rocker arm 17 shown.
  • the adjusting ring 5 moves in the direction the arrow a (clockwise), it can be seen from a comparison of FIGS. 5 to 7 that also pivot the pivot lever 17 clockwise about its pivot point 19. This latter pivoting makes up about 40 ° in the present example, while the Pivotal movement of the adjusting ring 5 is much smaller. This results - depending on the consideration - an over or a reduction effect.
  • the lower end surface 17a closes in cross section approximately rectangular rocker arm 17 with the outer surface of the link part 16 flush.
  • the introduction of force is low and the rocker arm 17 thus covers the as Groove 18 'formed opening completely.
  • This groove 18 ' is of those not shown here Guide vanes facing away, but constructions would be conceivable in which they are the guide vanes are facing, but such constructions are more complicated and space-consuming and therefore not preferred.
  • the cross-sectional shape of the Rocker arm 17 will preferably be a quadrangular, but also other cross-sectional shapes are conceivable without changing the basic function. For example a (not preferred) hexagonal cross-sectional shape would be conceivable. Further would be conceivable that the rocker arms 17 are approximately T-shaped, the crossbar of the T as a cover surface over the end face of the link part 16 and one Tribe of the T forming rib engages in the groove 18 '. However, this would be the axial Increase the size of the building somewhat and would also bring a more difficult shape to manufacture with himself.
  • FIG. 8 is an embodiment variant with cranked rocker arms in a position which corresponds approximately to that of FIG. 5 (Closed position of the guide vanes 7, maximum moment acting on them). It can be seen that the closed position of the guide vanes 7 (for example during braking operation) is approximately reached when the fork 28 is at least almost parallel to one Middle plane P3 lies.
  • the invention is not so limited; rather could the fork 28 instead of mutually parallel fork tines also have curved, if one special modification of the characteristic is desired.
  • the adjusting ring 5 is attached to the blade bearing ring 6 (not shown) Bearing rollers 24 stored and so a little further away from the pivot shafts 8, so that the length of the rocker arm 17 increases compared to the previous embodiments.
  • bearing rollers 24 stored and so a little further away from the pivot shafts 8, so that the length of the rocker arm 17 increases compared to the previous embodiments.
  • cylindrical rollers 22 for storage of the adjusting ring 5 distributed over the circumference, for example, only three such roles 22 may be provided. However, if you want cylindrical rollers 22 instead of bearing rollers 24 (Fig. 3) use, this leads to problems when using a groove 18 'as an opening.
  • the adjusting ring 5 has a square sliding block 25 attached to its circumference is pivotable about an axis of rotation 26. On this sliding block 25 one grips with one Shaft 27 pivotable fork 28 forming the associated link. On the shaft 27 is an adjusting arm 29 is attached, either from the geometric axis of the shaft 27 Plunger 14 of the control housing 12 (see FIG. 1) or can be pivoted by the servo motor 12 ', to pivot the adjustment ring 5 about the central axis R via the fork 28.
  • the crank is so dimensioned that two planes P1, P2 through the central axis R with each other an angle Include ⁇ .
  • This angle ⁇ is relatively small and should be a maximum of 12 ° but preferably below, so that it is a maximum of 9 °. In practice, there was an angle ⁇ of maximum 6 °, e.g. about 2 ° found to be particularly favorable.
  • This angle ⁇ becomes with a small pressure drop in room 13 (FIG. 1) be large and decrease with the enlargement of the guide vanes 7 acting load (i.e., Fig. 8 shows the smallest, in this embodiment occurring angle ⁇ ).
  • the Angle ⁇ is for the respective construction (occurring forces, surface pressure between Opening 18 or 18 'and outer surface of the rocker arm, available actuating forces) to choose, but should preferably be between 25 ° and 15 °, for example approximately 20 °. In the present exemplary embodiment, it is somewhat between 21 ° and 22 °, is in the preferred range of 20 ° ⁇ 2 °.
  • Another definition can be defined by the offset angle ⁇ between those offset by the offset Reach sections of the rocker arm 17 extending longitudinal axes A, A '.
  • This angle ⁇ should be in the range of 170-120 ° and preferably about 140 ° be.
  • this arrangement can produce significantly more force can be induced, which means that the rotary actuator (12 or 12 ') is considerably relieved.
  • cranked rocker arms 17 ' is - based on the positions 5-7 - in the area between the positions of FIGS. 6 and 7 more adjustment implemented with less force. But the more the position of the rocker arms 17 ' approaches that corresponding to FIG. 5, the greater the force.
  • FIG. 1 shows the characteristic curve of a conventional guide vane c 1 in a turbocharger in comparison with the course c 2 of a guide vane according to the invention.
  • the bucket torque M s in Nm is compared to the adjustment angle ⁇ of the adjustment lever 29 (FIG. 8) which absorbs the moments. It can be seen that the greatest moment M s at 0 ° (di compared to the radial orientation -20 °), that is to say it is reached when the guide blades 7 and the adjusting lever 29 are in the position shown in FIG to withstand the greatest moment acting on them. To the right, however, the torque drops sharply, but never reaches a zero value up to 40 ° (ie in relation to the radial orientation + 20 °).
  • the curve c 2 drops to a moment from zero soon after its intersection D2 (end of the working range) and is therefore approximately symmetrical within the working range between zero load (in points D2) and braking load (upper left point), which is represents a further advantage of the construction according to the invention.
  • the adjustment angle for curve c 1 is smaller than for c 2 .

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Supercharger (AREA)
  • Control Of Turbines (AREA)
EP02025181A 2002-11-11 2002-11-11 Ensemble stator pour turbocompresseur à géométrie variable Expired - Fee Related EP1418311B1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DE50209301T DE50209301D1 (de) 2002-11-11 2002-11-11 Leitgitter variabler Geometrie
EP02025181A EP1418311B1 (fr) 2002-11-11 2002-11-11 Ensemble stator pour turbocompresseur à géométrie variable
US10/706,180 US7114919B2 (en) 2002-11-11 2003-11-12 Guiding grid of variable geometry

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP02025181A EP1418311B1 (fr) 2002-11-11 2002-11-11 Ensemble stator pour turbocompresseur à géométrie variable

Publications (2)

Publication Number Publication Date
EP1418311A1 true EP1418311A1 (fr) 2004-05-12
EP1418311B1 EP1418311B1 (fr) 2007-01-17

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EP02025181A Expired - Fee Related EP1418311B1 (fr) 2002-11-11 2002-11-11 Ensemble stator pour turbocompresseur à géométrie variable

Country Status (3)

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US (1) US7114919B2 (fr)
EP (1) EP1418311B1 (fr)
DE (1) DE50209301D1 (fr)

Cited By (6)

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DE102008053170A1 (de) * 2008-10-24 2010-04-29 Bosch Mahle Turbo Systems Gmbh & Co. Kg Ladeeinrichtung mit variabler Turbinen-/Verdichtergeometrie, insbesondere für einen Abgasturbolader eines Kraftfahrzeugs
CN103492688A (zh) * 2011-05-10 2014-01-01 博格华纳公司 具有可变涡轮几何形状的涡轮增压器
CN104220720A (zh) * 2012-04-27 2014-12-17 博格华纳公司 排气涡轮增压器
EP2733328A4 (fr) * 2011-07-14 2015-03-11 Xiangtan Electric Mfg Co Ltd Système générateur d'énergie thermique à énergie solaire et dispositif de conversion thermoélectrique de ce système
CN108278132A (zh) * 2014-09-12 2018-07-13 博世马勒涡轮系统有限两合公司 用于废气涡轮增压器的可变涡轮和/或压缩机几何构造
US10927702B1 (en) 2019-03-30 2021-02-23 Savant Holdings LLC Turbocharger or turbocharger component

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CN1561431B (zh) * 2001-08-03 2010-05-26 株式会社秋田精密冲压 Vgs型涡轮增压器中的涡轮框架的制造方法
EP1394364B1 (fr) * 2002-08-26 2006-03-08 BorgWarner Inc. Turbosoufflante et son anneau de guidage
DE102004057864A1 (de) * 2004-11-30 2006-06-01 Borgwarner Inc.(N.D.Ges.D.Staates Delaware), Auburn Hills Abgasturbolader, Leitapparat für einen Abgasturbolader sowie Schaufelhebel für einen Leitapparat
JP2010516945A (ja) * 2007-01-27 2010-05-20 ボーグワーナー・インコーポレーテッド 燃焼機関吸排気システム用の補助空気システム
CN101743379A (zh) * 2007-04-10 2010-06-16 艾利奥特公司 具有可调进口导向叶片的离心式压缩机
JP4885118B2 (ja) * 2007-12-21 2012-02-29 三菱重工業株式会社 可変ノズル機構を備えた可変容量型排気ターボ過給機
US8056336B2 (en) * 2008-05-05 2011-11-15 Honeywell International Inc. Turbocharger with variable nozzle having vane sealing surfaces
DE102009014917A1 (de) * 2009-03-25 2010-09-30 Bosch Mahle Turbo Systems Gmbh & Co. Kg Ladeeinrichtung
US8231326B2 (en) * 2009-03-31 2012-07-31 Nuovo Pignone S.P.A. Nozzle adjusting mechanism and method
US8393857B2 (en) * 2009-10-09 2013-03-12 Rolls-Royce Corporation Variable vane actuation system
FR2958967B1 (fr) * 2010-04-14 2013-03-15 Turbomeca Procede d'adaptation de debit d'air de turbomachine a compresseur centrifuge et diffuseur de mise en oeuvre
WO2012036328A1 (fr) * 2010-09-15 2012-03-22 (주)계양정밀 Dispositif à buse variable et turbocompresseur pourvu de ce dernier
US8967956B2 (en) * 2011-09-26 2015-03-03 Honeywell International Inc. Turbocharger variable-nozzle assembly with vane sealing arrangement
US8967955B2 (en) * 2011-09-26 2015-03-03 Honeywell International Inc. Turbocharger with variable nozzle having labyrinth seal for vanes
WO2013163024A1 (fr) * 2012-04-27 2013-10-31 Borgwarner Inc. Turbocompresseur à gaz d'échappement
CN104220722A (zh) * 2012-04-27 2014-12-17 博格华纳公司 排气涡轮增压器
US9429033B2 (en) 2013-11-08 2016-08-30 Honeywell International Inc. Drive arrangement for a unison ring of a variable-vane assembly
DE112014004824T5 (de) * 2013-11-26 2016-07-21 Borgwarner Inc. VTG-Turbolader mit durch ein gemeinsam genutztes Stellglied geregeltem Wastegate
US10227889B2 (en) * 2015-02-05 2019-03-12 Garrett Transportation I Inc. Variable geometry nozzle for partitioned volute
US10018107B2 (en) * 2015-07-10 2018-07-10 Kangyue Technology Co., Ltd Balanced vanes and integrated actuation system for a variable geometry turbocharger
US10227887B2 (en) * 2015-10-07 2019-03-12 Hanwha Power Systems Co., Ltd. Fluid machine with variable vanes
JP6908472B2 (ja) * 2017-08-31 2021-07-28 三菱重工コンプレッサ株式会社 遠心圧縮機
KR102585747B1 (ko) * 2018-05-04 2023-10-11 현대자동차주식회사 차량용 vgt
US10883379B2 (en) * 2018-05-11 2021-01-05 Rolls-Royce Corporation Variable diffuser having a respective penny for each vane
DE102018211094A1 (de) * 2018-07-05 2020-01-09 Volkswagen Aktiengesellschaft Verfahren zum Betreiben einer Brennkraftmaschine, Brennkraftmaschine und Kraftfahrzeug
US10927701B2 (en) * 2019-03-12 2021-02-23 Garrett Transportation I Inc. Turbocharger having variable-vane turbine nozzle including spacers that also serve as hard stops for the vanes
KR20210014450A (ko) * 2019-07-30 2021-02-09 현대자동차주식회사 가변 지오메트리 터보차저
CN113863992A (zh) * 2021-10-26 2021-12-31 中国航发沈阳发动机研究所 一种航空发动机中静子叶片转动角度调节机构
DE102021134071A1 (de) * 2021-12-21 2023-06-22 Borgwarner Inc. Radialturbine mit vtg-leitgitter
CN115350855B (zh) * 2022-09-21 2024-05-03 湖南九九智能环保股份有限公司 一种喷嘴角度调节装置及喷雾机

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FR1442174A (fr) * 1964-10-01 1966-06-10 Escher Wyss Ag Dispositif de commande d'une couronne d'aubes aptes à pivoter selon des axes parallèles à l'axe de la couronne
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Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008053170A1 (de) * 2008-10-24 2010-04-29 Bosch Mahle Turbo Systems Gmbh & Co. Kg Ladeeinrichtung mit variabler Turbinen-/Verdichtergeometrie, insbesondere für einen Abgasturbolader eines Kraftfahrzeugs
CN103492688A (zh) * 2011-05-10 2014-01-01 博格华纳公司 具有可变涡轮几何形状的涡轮增压器
CN103492688B (zh) * 2011-05-10 2016-02-10 博格华纳公司 具有可变涡轮几何形状的涡轮增压器
EP2733328A4 (fr) * 2011-07-14 2015-03-11 Xiangtan Electric Mfg Co Ltd Système générateur d'énergie thermique à énergie solaire et dispositif de conversion thermoélectrique de ce système
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CN104220720A (zh) * 2012-04-27 2014-12-17 博格华纳公司 排气涡轮增压器
CN104220720B (zh) * 2012-04-27 2020-03-03 博格华纳公司 排气涡轮增压器
CN108278132A (zh) * 2014-09-12 2018-07-13 博世马勒涡轮系统有限两合公司 用于废气涡轮增压器的可变涡轮和/或压缩机几何构造
CN108278132B (zh) * 2014-09-12 2020-11-03 博马科技有限责任公司 用于废气涡轮增压器的可变涡轮和/或压缩机几何构造
US10927702B1 (en) 2019-03-30 2021-02-23 Savant Holdings LLC Turbocharger or turbocharger component

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US20040096317A1 (en) 2004-05-20
EP1418311B1 (fr) 2007-01-17
DE50209301D1 (de) 2007-03-08

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