WO2012110163A1 - Turbocompresseur - Google Patents

Turbocompresseur Download PDF

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Publication number
WO2012110163A1
WO2012110163A1 PCT/EP2011/074247 EP2011074247W WO2012110163A1 WO 2012110163 A1 WO2012110163 A1 WO 2012110163A1 EP 2011074247 W EP2011074247 W EP 2011074247W WO 2012110163 A1 WO2012110163 A1 WO 2012110163A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
exhaust gas
gas turbocharger
axis
valve element
Prior art date
Application number
PCT/EP2011/074247
Other languages
German (de)
English (en)
Inventor
Michael Baeuerle
Lukas GONO
Reiner Schweinfurth
Michael Nau
David TRTEK
Holger Knesch
Jan Vesely
Original Assignee
Robert Bosch Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Priority to EP11802964.4A priority Critical patent/EP2676019A1/fr
Publication of WO2012110163A1 publication Critical patent/WO2012110163A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/12—Control of the pumps
    • F02B37/18—Control of the pumps by bypassing exhaust from the inlet to the outlet of turbine or to the atmosphere
    • F02B37/183—Arrangements of bypass valves or actuators therefor
    • F02B37/186—Arrangements of actuators or linkage for bypass valves
    • 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
    • F01D17/105—Final actuators by passing part of the fluid
    • 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
    • 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
    • F05D2250/00—Geometry
    • F05D2250/30—Arrangement of components
    • F05D2250/31—Arrangement of components according to the direction of their main axis or their axis of rotation
    • F05D2250/312—Arrangement of components according to the direction of their main axis or their axis of rotation the axes being parallel to each other
    • 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
    • F05D2250/00—Geometry
    • F05D2250/30—Arrangement of components
    • F05D2250/31—Arrangement of components according to the direction of their main axis or their axis of rotation
    • F05D2250/313—Arrangement of components according to the direction of their main axis or their axis of rotation the axes being perpendicular to each other
    • 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
    • F05D2250/00—Geometry
    • F05D2250/40—Movement of components
    • F05D2250/41—Movement of components with one degree of freedom
    • F05D2250/411—Movement of components with one degree of freedom in rotation
    • 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
    • F05D2260/00—Function
    • F05D2260/50—Kinematic linkage, i.e. transmission of position
    • F05D2260/53—Kinematic linkage, i.e. transmission of position using gears
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • the invention relates to an exhaust gas turbocharger, in particular for a motor vehicle, with at least one turbine, which is associated with an actuatable bypass valve, and with an actuator, which is connected by a coupling rod with a displaceable about a valve axis valve element of the bypass valve.
  • exhaust gas turbochargers of the type mentioned are known from the prior art.
  • exhaust gas turbochargers serve to increase the performance of internal combustion engines.
  • they have a compressor which is arranged in the intake tract in order to compress the fresh air supplied to the internal combustion engine, so that a higher degree of filling in the combustion chambers is achieved.
  • the compressor is driven by a turbine which uses the energy of the exhaust gas produced by the internal combustion engine.
  • Modern exhaust gas turbochargers include means that allow to influence the performance of the exhaust gas turbocharger. In particular, this includes a bypass assigned to the turbine.
  • Valve located in a bypass that connects, for example, a high pressure side of the turbine with a low pressure side of the turbine. By opening the bypass valve, the pressure on the high-pressure side of the turbine can thus be reduced, whereby the power of the turbine and thus also the performance of the compressor is reduced.
  • the bypass valve is a
  • Assigned actuator which is connected by a coupling rod with a displaceable valve element of the bypass valve.
  • the coupling rod is parallel to the main axis of the
  • Exhaust gas turbocharger ie parallel to the axis of rotation of the compressor with the turbine aligned connecting shaft, while the valve axis about which the valve element is displaceable, perpendicular to the main axis. Due to the usual design of the bypass valve creates a non-linear force-displacement curve with high closing forces, which must be provided by the actuator. These depend on the displacement, degree of charge and others
  • the exhaust gas turbocharger according to the invention with the features of claim 1 has the advantage that a solution is offered, which takes advantage of the available space and yet meets the performance requirements.
  • the exhaust gas turbocharger according to the invention is characterized in that the
  • Coupling rod at least substantially perpendicular and the valve axis are aligned at least substantially parallel to the main axis of the exhaust gas turbocharger. This arrangement of the coupling rod and the valve axis opens the possibility to position the actuator in a more advantageous position on the exhaust gas turbocharger. Especially by the vertical
  • the arrangement according to the invention is also advantageous for the power transmission and the design of the housing of the exhaust gas turbocharger and / or the turbine as a sheet metal construction.
  • the design as a sheet metal construction is less expensive and has advantages in terms of emission behavior, since it forms a smaller heat sink when heating a catalytic converter.
  • the actuator has an electromechanical or electromagnetic actuator. Due to the vertical orientation of the coupling rod, in particular the electromechanical servo motor can be arranged sufficiently far away from the exhaust gas turbocharger, so that sufficient cooling of the servomotor is ensured.
  • the valve element is designed to open or close the bypass valve to the valve axis hinged.
  • the particular plate-shaped valve element is folded onto the valve seat.
  • the valve axis lies in or parallel to the plane in which the opening to be closed or the valve seat are located.
  • the particular plate-shaped valve element for opening or closing the bypass valve is formed laterally pivotable about the valve axis.
  • the valve axis is at least substantially perpendicular or more preferably obliquely, in particular at an angle between 80 ° and 5 °, preferably between 45 ° and 10 °, to the plane in which the
  • valve element By the lateral pivoting of the valve element lower actuating forces are necessary, since the valve element now, for example, not against the pressure force of
  • the laterally pivotable valve element is tilted aligned with the pivoting plane. Due to the thus obtained inclined position of the valve element, in particular of the plate-shaped valve element, only one of the gas forces resulting partial force component acts on the
  • valve seat is also tilted or aligned obliquely with respect to the pivot plane, so that in the closed state, the valve element rests tightly on the valve seat.
  • the laterally pivotable valve element is tilted about a valve longitudinal axis lying perpendicular to the valve axis.
  • the valve longitudinal axis is in particular the Axle, which preferably extends from the valve axis perpendicular and forms the main longitudinal axis of the valve element.
  • valve seat is aligned accordingly, so that in an end pivotal position, the valve element rests sealingly on the valve seat.
  • bypass valve is designed as a flat seat valve.
  • valve element is substantially plate-shaped and cooperates with one of its end faces with a flat valve seat. Under a flat valve seat is here
  • Valve element sealingly rests in the closed position of the bypass.
  • the design as a flat seat valve, a cost-effective and reliable valve is used.
  • the actuator further comprises a transmission gear, in particular gear transmission, which connects the servomotor with the coupling rod.
  • a transmission gear in particular gear transmission, which connects the servomotor with the coupling rod.
  • the required actuating forces, in particular closing forces of the bypass valve can also be provided with a less powerful electromechanical actuator.
  • the transmission gear has three transmission axes, which are in a row or offset from each other.
  • each of the transmission axes is associated with at least one gear, which meshes with at least one adjacent gear.
  • a first transmission axis is formed by the output shaft of the electromechanical servo motor, on which a Input-side drive gear is arranged rotatably. This gear is engaged with a first idler gear on a second gear axis.
  • a third intermediate gear is further preferably arranged non-rotatably, which meshes with an arranged on the third transmission axis, output-side gear, wherein on the third transmission axis preferably a crank is arranged, with which the coupling rod is connected.
  • the three transmission axes are triangular to each other and / or on a radius, in particular with respect to the main axis of the
  • Exhaust gas turbocharger As a result, a particularly compact arrangement of the transmission gear is ensured, in particular takes place while adapting the shape of the transmission gear to the shape of the exhaust gas turbocharger.
  • Figure 2 shows a first embodiment of an inventive
  • Figure 3 shows a second embodiment of the invention
  • Figure 6 shows an advantageous development of the transmission gear.
  • FIG. 1 shows a perspective partial sectional view of a
  • Exhaust gas turbocharger 1 for a motor vehicle.
  • the exhaust gas turbocharger 1 comprises a turbine 2 and a compressor 3, which are operatively connected to each other.
  • a turbine wheel 4 of the turbine 2 is rotatably mounted on a shaft 5, on which also a turbine wheel 6 of the compressor 3 is arranged rotationally fixed.
  • valve element 9 is plate-shaped to form the bypass valve 8 as a flat seat valve 10, and rotatably connected to a valve shaft 1 1, which is rotatably held in the housing of the exhaust gas turbocharger 1.
  • the valve shaft 1 1 forms a valve axis 12 about which the valve element 9 is displaceable.
  • a lever 13 is further arranged non-rotatably, which is pivotally connected to a coupling rod 14.
  • Coupling rod 14 is in turn connected at its other end with an actuator, not shown in Figure 1, which displaces the coupling rod 14 along its axis when actuated to actuate the bypass valve 8.
  • Coupling rod is parallel to the shaft 5, which forms a main axis 15 of the exhaust gas turbocharger 1, arranged, while the valve axis 12th
  • valve shaft 1 1 substantially perpendicular to the
  • Main axis 15 are aligned. This results in high adjusting forces for actuating the bypass valve 8, which usually by means of an over- or
  • Vacuum box can be provided.
  • Figure 2 shows a preferred embodiment of the exhaust gas turbocharger 1, in which a more advantageous arrangement of coupling rod 14 and valve axis 12 has been selected.
  • Figure 2 shows a preferred embodiment of the exhaust gas turbocharger 1, in which a more advantageous arrangement of coupling rod 14 and valve axis 12 has been selected.
  • the coupling rod 14 is oriented at least essentially perpendicular to the main axis 15, while the valve axis 12 lies at least substantially parallel to the main axis 15.
  • the coupling rod 14 is connected to a crank 16 of a transmission gear 17, which of a
  • electromechanical actuator 18 is driven.
  • the transmission 17 will be discussed later in more detail. Due to the advantageous arrangement of the coupling rod 14 and the valve axis 12 of the servomotor 18 is sufficiently spaced to the exhaust gas turbocharger 1 can be arranged, yet a compact design is guaranteed. Due to the vertical orientation of the coupling rod 14 to the main axis 15 of the Electric motor and the transmission gear 17, which together a
  • the advantageous embodiment also has advantages in terms of the construction of the
  • the plate-shaped valve element 9 lies at least substantially in a plane which is aligned parallel to the valve axis 12. Accordingly it behaves with one of the
  • Valve element 9 to be closed valve seat 20, which in the
  • Exhaust gas turbocharger housing is formed. Due to the design as a flat seat valve 10, the plate-shaped valve element 9 is folded by actuation of the actuator 19 on the valve seat 20 or removed by this by unfolding.
  • valve seat 20 As a result, an opening surrounded by the valve seat 20 is closed
  • bypass valve 8 is thus aligned radially with respect to the main axis 15,
  • valve element 9 is folded substantially radially with respect to the main axis.
  • FIG. 3 shows a preferred alternative embodiment of the exhaust gas turbocharger 1, wherein already known elements of Figure 2 are provided with the same reference numerals, so reference is made in this respect to the above description. In the following, only the differences will be discussed.
  • the essential difference of the second embodiment according to Figure 3 is that the valve element 9 of the bypass valve 8 is not hinged to the valve seat 20, but is formed laterally pivotable. The valve element 9 is thus not opened, but laterally pushed over the valve seat 20 to release the bypass 7 or to close.
  • Embodiment of the bypass 7 extends radially from the turbine housing, according to the second embodiment, the bypass 7 or at least its inlet opening is substantially aligned axially thereto.
  • the embodiment according to FIG. 3 furthermore has the advantage that the actuating forces for closing the bypass valve 8 are lower, since in operation the pressure of the exhaust gas flowing to the turbine 2 forces the valve element 9 against the valve seat 20 and thereby the closing force generated by the actuator 19 supported.
  • Figure 4 shows a preferred embodiment of the exhaust gas turbocharger 1 according to the second embodiment of Figure 3.
  • Figure 4 shows the bypass valve 8 in a side view.
  • the dish-shaped valve element 9 is
  • valve element axis 21 is aligned at an acute angle ⁇ to the valve axis 12, so that the
  • Valve element 9 is tilted to the valve axis 12.
  • the valve seat 20 has a corresponding valve seat axis 22, which is also inclined at an angle ß with respect to the valve axis 12, wherein preferably ⁇ is equal to ⁇ .
  • ß is also inclined at an angle ß with respect to the valve axis 12, wherein preferably ⁇ is equal to ⁇ .
  • ⁇ and ⁇ are about 11 °.
  • ⁇ and ß another Wnkelwert, in particular between 45 ° and 10 °.
  • the described construction has the advantage that, when the bypass valve 8 is actuated, the valve element 9 is slid obliquely onto the valve seat 20 is, as indicated by an arrow, so that the force that is used to pivot the valve element 9, at the same time for pressing the
  • Valve element 9 is used against the valve seat 20. As a result, the tightness of the closed bypass valve 8 is ensured at all times. Due to the tilted arrangement of the valve element 9, only a partial force component resulting from the exhaust gas forces is transmitted to the lever 16 or the coupling rod 14, so that the forces to be transmitted are reduced overall. As a result, the electromechanical actuating motor 18 can also be dimensioned smaller, which results in further packaging advantages, in particular with regard to the available installation space.
  • FIGs 4 and 5 show the transmission gear 17 each in one
  • the transmission gear 17 includes a
  • electromechanical servo motor 8 - not shown here - is arranged.
  • the gear 23 meshes with a first intermediate gear 24 which is rotatably mounted on an intermediate shaft 25.
  • a second intermediate gear is further arranged, which is not visible in the illustrated plan view, since it is behind the intermediate gear 24.
  • Figure 5 shows a common arrangement of the transmission axes 28, 29 and 30 to each other, which in this case lie in a row or in a common plane.
  • FIG. 6 shows a particularly preferred arrangement of the transmission axes relative to each other, in which the transmission axis 29 is offset relative to the plane in which the transmission axes 28 and 30 lie.
  • Transmission gear 17 is reduced overall.
  • the transmission gear 17 is thereby replaced by a banana shape, which leads to corresponding packaging Benefits leads.
  • the transmission axes are arranged to each other such that they are adapted to the radius of the compressor and / or turbine volutes to a particularly favorable adaptation to the
  • a corresponding transmission gear 17 is also used for the above-mentioned variable turbine geometry, regardless of the formation of the rest of the exhaust gas turbocharger, in particular independent of the presence or the formation of the bypass valve. 8

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Supercharger (AREA)

Abstract

L'invention concerne un turbocompresseur (1), notamment pour un véhicule à moteur, comportant au moins une turbine (2), à laquelle est associée une soupape de dérivation (8) actionnable, un mécanisme de commande (19) qui est relié, par l'intermédiaire d'une tige d'accouplement (14), à un élément (9) de la soupape de dérivation (8) mobile autour d'un axe de soupape (12). Selon l'invention, la tige d'accouplement (14) est orientée au moins sensiblement perpendiculairement et l'axe de soupape (12) est orienté au moins sensiblement parallèlement à l'axe principal (15) du turbocompresseur (1).
PCT/EP2011/074247 2011-02-14 2011-12-29 Turbocompresseur WO2012110163A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP11802964.4A EP2676019A1 (fr) 2011-02-14 2011-12-29 Turbocompresseur

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011004027.7 2011-02-14
DE102011004027A DE102011004027A1 (de) 2011-02-14 2011-02-14 Abgasturbolader

Publications (1)

Publication Number Publication Date
WO2012110163A1 true WO2012110163A1 (fr) 2012-08-23

Family

ID=45440553

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2011/074247 WO2012110163A1 (fr) 2011-02-14 2011-12-29 Turbocompresseur

Country Status (3)

Country Link
EP (1) EP2676019A1 (fr)
DE (1) DE102011004027A1 (fr)
WO (1) WO2012110163A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20180306103A1 (en) * 2017-04-20 2018-10-25 GM Global Technology Operations LLC Non-circular gears for rotary wastegate actuator

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2997153B1 (fr) * 2012-10-24 2016-09-16 Valeo Systemes De Controle Moteur Dispositif d'actionnement d'un ou plusieurs organes mobiles, notamment pour turbocompresseur de vehicule automobile
DE102012221911A1 (de) 2012-11-29 2014-06-05 Robert Bosch Gmbh Abgastorbolader
DE102012221910A1 (de) 2012-11-29 2014-06-05 Robert Bosch Gmbh Abgasturbolader
DE102012023802B4 (de) * 2012-12-05 2018-10-31 Audi Ag Abgasturbolader mit einer Abgasleitvorrichtung
DE102020132566A1 (de) 2020-12-08 2022-06-09 Harmonic Drive Se Flachgetriebe und Käfig für Flachgetriebe

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005028374A1 (de) * 2005-06-20 2006-12-21 Robert Bosch Gmbh Steller für ein Stellorgan
DE102005028372A1 (de) * 2005-06-20 2006-12-21 Robert Bosch Gmbh Steller für ein Stellorgan
US20090235766A1 (en) * 2006-04-07 2009-09-24 Borgwarner Inc Actuator With Integrated Drive Mechanism
WO2010104695A2 (fr) * 2009-03-09 2010-09-16 Borgwarner Inc. Turbocompresseur d'échappement

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Publication number Priority date Publication date Assignee Title
US4492519A (en) * 1979-02-15 1985-01-08 Wallace Murray Corporation Turbocharger exhaust gas by-pass valve
DE102008011416A1 (de) * 2008-02-27 2009-09-10 Continental Automotive Gmbh Turbolader mit einer Betätigungseinrichtung zum Öffnen und Schließen eines Wastegate-Kanals

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005028374A1 (de) * 2005-06-20 2006-12-21 Robert Bosch Gmbh Steller für ein Stellorgan
DE102005028372A1 (de) * 2005-06-20 2006-12-21 Robert Bosch Gmbh Steller für ein Stellorgan
US20090235766A1 (en) * 2006-04-07 2009-09-24 Borgwarner Inc Actuator With Integrated Drive Mechanism
WO2010104695A2 (fr) * 2009-03-09 2010-09-16 Borgwarner Inc. Turbocompresseur d'échappement

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20180306103A1 (en) * 2017-04-20 2018-10-25 GM Global Technology Operations LLC Non-circular gears for rotary wastegate actuator
CN108730021A (zh) * 2017-04-20 2018-11-02 通用汽车环球科技运作有限责任公司 用于旋转式废气门致动器的非圆齿轮
US10443487B2 (en) * 2017-04-20 2019-10-15 GM Global Technology Operations LLC Non-circular gears for rotary wastegate actuator

Also Published As

Publication number Publication date
EP2676019A1 (fr) 2013-12-25
DE102011004027A1 (de) 2012-08-16

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