EP1532368B1 - Compresseur dans un turbocompresseur a gaz d'echappement pour un moteur a combustion interne - Google Patents

Compresseur dans un turbocompresseur a gaz d'echappement pour un moteur a combustion interne Download PDF

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Publication number
EP1532368B1
EP1532368B1 EP03797228A EP03797228A EP1532368B1 EP 1532368 B1 EP1532368 B1 EP 1532368B1 EP 03797228 A EP03797228 A EP 03797228A EP 03797228 A EP03797228 A EP 03797228A EP 1532368 B1 EP1532368 B1 EP 1532368B1
Authority
EP
European Patent Office
Prior art keywords
compressor
adjusting
ring
adjusting ring
diffuser
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.)
Expired - Fee Related
Application number
EP03797228A
Other languages
German (de)
English (en)
Other versions
EP1532368A1 (fr
Inventor
Helmut Daudel
Paul Löffler
Stephan Schenkel
Joseph Spurk
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.)
Mercedes Benz Group AG
Original Assignee
DaimlerChrysler AG
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 DaimlerChrysler AG filed Critical DaimlerChrysler AG
Publication of EP1532368A1 publication Critical patent/EP1532368A1/fr
Application granted granted Critical
Publication of EP1532368B1 publication Critical patent/EP1532368B1/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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/02—Surge control
    • F04D27/0246—Surge control by varying geometry within the pumps, e.g. by adjusting vanes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/46—Fluid-guiding means, e.g. diffusers adjustable
    • F04D29/462—Fluid-guiding means, e.g. diffusers adjustable especially adapted for elastic fluid pumps
    • 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
    • F05D2250/50—Inlet or outlet
    • F05D2250/52—Outlet

Definitions

  • the invention relates to a compressor according to the preamble of claim 1.
  • Such a compressor is described both in the document US Pat. No. 5,207,559 and in the document US Pat. No. 3,992,128.
  • the compressor is fed via a compressor inlet channel fresh air, which is compressed by a compressor in the compressor housing and passed downstream of the compressor in a diffuser.
  • the compressor wheel is driven via a shaft by a turbine whose turbine wheel is acted upon by pressurized gas.
  • the compressor has a variably adjustable diffuser geometry, which allows, depending on the current operating point of the compressor Changing the geometry of the diffuser downstream of the compressor wheel.
  • the diffuser geometry comprises, distributed over the circumference of the diffuser, adjustable guide vanes, which are each rotatably mounted on a stator shaft, and a rotatable adjusting ring with adjusting members which rotate the vane shafts about their longitudinal axes, whereby the position of the guide vanes is variable and thus different flow conditions in the diffuser are to be adjusted.
  • the adjusting movement of the adjusting ring is transmitted via the adjusting members on the guide vane shafts, which are mounted fixed to the housing.
  • the adjusting members are rotatably received in the adjusting ring and bridge a radial distance between the adjusting ring and the guide vane shafts. Due to the housing-fixed bearing of the guide vane shafts and the distance between the guide vane shafts and the bearing axis of the adjusting a rotational movement of the Versteliring is possible only to a small extent in the context of the bearing clearance of the adjustment. Large positioning movements can not be generated with this actuator. Precise adjustment of the vane position can not be guaranteed safely.
  • the invention is based on the problem to provide a generic compressor with variably adjustable diffuser geometry, which is characterized by a simple structural design and exact adjustment.
  • the adjustment of the diffuser geometry should be accomplished with high security against jamming or distortion and with low restoring forces.
  • the compressor has in the region of the diffuser geometry an adjusting ring with adjusting elements, which act on the guide vanes of the diffuser geometry at a distance from the respective guide shaft in the direction of rotation.
  • the force acting on the vanes actuating force of the adjusting causes a torque around the guide vane shaft, which leads to the adjustment of the vanes.
  • the guide vane is now subjected to the adjusting force at a distance from its guide vane shaft, whereby for the adjustment of the guide vanes only smaller and better metered actuating forces are needed.
  • the useful ring-shaped distributed vanes are acted upon by the adjusting elements in particular in a radially outer region, which has a greater distance from the longitudinal axis of the diffuser geometry than the guide vane shafts.
  • the guide vanes are advantageously mounted on a bearing ring, in particular received only on one side of this bearing ring. Because of this one-sided storage on only one side of the compressor spiral or the diffuser in the region of the Ver Togetherrradaustrittes the risk of jamming of the vanes is eliminated, which would otherwise not be excluded in a double-sided storage in the region of opposite diffuser walls due to the significant temperature differences between the diffuser walls.
  • a further advantage of the embodiment according to the invention lies in the simple construction and in the small number of components required, in particular on moving components, which also reduces unwanted leaks, particularly in the area of the bearing shaft guides, and improves the efficiency.
  • the guide vanes are fork-shaped on their side facing away from the guide shaft and have two forks, between which an open receptacle is formed, in which the adjusting element of the adjusting protrudes.
  • the adjusting element is preferably designed as an adjusting pin, which is held firmly on the adjusting ring and adjusted by a rotation of the adjusting ring, the guide vanes about its guide vane shaft by the desired angular amount.
  • the guide vanes are adjusted by the desired angular amount about its guide shaft, wherein in the case of a coaxial arrangement of adjusting ring and compressor wheel, the distance of the adjusting elements to the compressor during the adjusting movement remains constant.
  • the diffuser geometry which comprises the pivotable guide vanes, mounted directly on a compressor rear wall of the compressor housing, which also limits the end face of the compressor wheel.
  • the diffuser geometry may also include the bearing ring, on which the stator shafts are mounted and which is fixed to the housing, in particular is held on the compressor rear wall of the compressor housing.
  • At an end face of the bearing ring a plurality of vanes are expediently evenly distributed in the form of a ring provided, the guide vane shafts are rotatably received on the bearing ring.
  • Each vane is to be actuated by an associated adjusting element on the adjusting ring, wherein in a preferred embodiment, the adjusting elements on the adjusting engage over the bearing ring on its radial outer side.
  • the bearing ring is advantageously arranged between the guide vanes and the adjusting ring, wherein in a preferred embodiment, the bearing ring is rotatably received in the adjusting ring, which is realized either by the fact that the radial outer side of the bearing ring is rotatably mounted on the radially inner side of the adjusting, or This is due to the fact that bearing axially projecting bearing elements are arranged on the bearing ring, which are rotatably mounted on the radially inner side of the adjusting ring.
  • the rotational movement of the adjusting ring about the Verstellringachse for adjusting the vanes between the vane end positions is advantageously realized via an engaging on the adjusting push rod, which is to be actuated by an actuator.
  • the exhaust gas turbocharger 1 shown in Fig. 1 is suitably used in internal combustion engines and includes an exhaust gas turbine 2, which is arranged in the exhaust line of the internal combustion engine, and a compressor 3, which is located in the intake tract of the internal combustion engine.
  • the exhaust gas turbine 2 comprises a turbine wheel 5 to be driven by the exhaust gases of the internal combustion engine to which the exhaust gas under pressure is to be supplied via a spiral channel 6.
  • the exhaust gas can leave the exhaust gas turbine 2 axially via a discharge channel 7.
  • the rotational movement of the turbine wheel 5 is transmitted via a shaft 8 to a compressor 9 in the compressor housing 15, compressed by the rotational movement of the compressor wheel 9 via an inlet channel 10 combustion air compressed to an increased boost pressure and discharged on the downstream side of the compressor in a radial diffuser 11 ,
  • the diffuser 11 terminates in a helical calming channel 12 from which the compressed air is discharged from the compressor and via the suction line the cylinders of the internal combustion engine is supplied.
  • the diffuser 11 is embodied as a radially extending, annular outflow channel between the radial outflow region of the compressor wheel 9 and the settling channel 12 and has a variably adjustable diffuser geometry 13, via which the effective cross section of the diffuser 11 in dependence on state and operating variables of the internal combustion engine or from the internal combustion engine associated units is adjustable.
  • the flow cross section of the diffuser is changed by acting on the variable diffuser geometry, in particular to increase the compressor working range. This makes it possible to stabilize the compressor operation in the boundary region of the still permissible compressor working range near the stuffing limit, but in particular near the surge limit, so that an inadmissible exceeding the surge limit and thus an undesirable compressor pumps can be avoided.
  • the diffuser geometry can be variably adjusted by means of adjustable guide vanes, which are arranged in the diffuser cross section. If appropriate, the diffuser geometry can also be altered by an axial displacement of the diffuser side walls.
  • a compressor rear wall 14 forms one of the side walls of the diffuser 11, wherein the compressor rear wall 14 limits both an axial end face of the compressor wheel 9 and the variable diffuser geometry 13.
  • variable diffuser geometry 13 can be designed as a prefabricated module, which can be inserted into the diffuser 11.
  • the exhaust gas turbine 2 may optionally also be equipped with a variably adjustable turbine geometry, via which a variable adjustment of the effective turbine inlet cross section to the turbine wheel is possible.
  • variable diffuser geometry 13 is shown in front of the compressor rear wall 14.
  • the variable diffuser geometry 13 comprises a plurality of annularly arranged and evenly distributed over the circumference vanes 16, each having a guide vane shaft 17 and are rotatably mounted about the guide vane shaft 17.
  • the guide vane shaft 17 of each vane 16 is rotatably received in a bearing ring 18 which is held fixed to the housing, in particular fixed and immovable to the compressor rear wall 14 is connected.
  • the bearing ring 18 is surrounded by a coaxial with the bearing ring arranged adjusting ring 19, wherein the radially inner side of the adjusting ring 19 is rotatably mounted on the radial outer side of the bearing ring 18.
  • the adjusting ring 19 has a plurality of adjusting elements 20, which are designed as pins and are located on an axial end face of the adjusting ring 19, wherein in each case an adjusting element 20 of a guide blade 16 is assigned to the bearing ring 18.
  • the adjusting ring 19 is acted upon by a designed as a push rod actuator 21 and pivoted about its axis of rotation.
  • the actuator 21 is actuated by an actuator, not shown.
  • the adjusting elements 20 are adjusted on the adjusting ring 19 in the circumferential direction by a predetermined angle, whereupon the guide vanes 16 are pivoted on the bearing ring 18 by a corresponding angular amount about its guide vane shafts 17.
  • the free flow cross section between each two adjacent vanes changes, whereby the pressure ratio between the compressor inlet side and the compressor outlet side changes and in particular the operation of the compressor near the surge line can be affected.
  • the guide vane shafts 17 of the guide vanes 16 have a smaller distance from the axis of the bearing ring 18 or the adjusting ring 19 than the adjusting elements 20 on the adjusting ring, which has the consequence that already a relatively small, acting in the circumferential direction of the adjusting force for pivoting the guide vanes to the guide vane enough.
  • Each vane 16 is fork-shaped and has two forks 22 and 23, between which a radially outwardly open receptacle 24 is formed, into which in each position of the adjusting 19, the adjusting element 20 protrudes. This ensures that in an adjustment of the adjusting ring 19 in the direction of arrow 25 in each position of the adjusting ring, the movement of the guide vanes 16 is forcibly guided.
  • the bearing of the bearing ring 18 in the adjusting ring 19 can be carried out in an alternative embodiment in such a way that connected to the bearing ring and axially projecting beyond the bearing ring bearing elements are rotatably mounted on the radially inner side of the adjusting ring.
  • variable diffuser allows by the free adjustability of the adjustable vanes from the respective operating point individually demand-dependent control or controllability of the motor air mass to be supplied or the air ratio ⁇ .
  • the particle filter regeneration can be supported by short-term reduction of the air ratio ⁇ and concomitant increase in the engine exhaust temperature of the exhaust gases.
  • an individually demand-dependent catalyst operating temperature is adjustable.
  • the engine temperature in the starting area can reduce emissions and raised to raise the catalyst operating temperature. Increasing the engine temperature in certain operating ranges can also increase the conversion rate when using an SCR system.
  • the variable diffuser also allows the exhaust gas turbocharger speed to be reduced in the event of a larger compressor being used without degrading the surge limit of the compressor.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Supercharger (AREA)

Abstract

L'invention concerne un compresseur (3) présentant, dans un carter de compresseur (15), une roue de compresseur (9) montée de façon rotative (9) ainsi qu'un diffuseur (11) installé en aval de la roue de compresseur et présentant une géométrie (13) à réglage variable. Cette géométrie (13) de diffuseur comporte des aubes directrices réglables (16), chacune montées de façon rotative sur un arbre d'aube directrice (17), et un anneau de réglage (19) rotatif actionnant les aubes directrices (16). Cet anneau de réglage (19) présente des éléments de réglage (20) qui actionnent ces aubes directrices (16) dans le sens de rotation à une certaine distance de l'arbre d'aube directrice correspondant (17).

Claims (8)

  1. Compresseur, en particulier compresseur dans un turbocompresseur pour un moteur à combustion interne, comportant une roue de compresseur (9), montée rotative dans un carter du compresseur (15), et un diffuseur (11), qui est monté dans le carter du compresseur (15) en aval de la roue de compresseur (9) et qui est conçu à géométrie (13) variable et comportant des aubes de guidage (16) réglables, qui sont montées rotatives chacune autour d'un arbre (17), et une bague de réglage (19) rotative, sollicitant les aubes de guidage (16), ladite bague de réglage (19) comportant des éléments de réglage (20) qui sollicitent les aubes de guidage (16) dans le sens de rotation à distance de chacun des arbres d'aube (17),
    caractérisé en ce que
    les aubes de guidage (16), sur leur côté opposé à l'arbre d'aube (17) sont réalisées en forme de fourche et possèdent deux dents (22, 23) entre lesquelles se forme un logement (24) ouvert, dans lequel s'engage l'élément de réglage (20) de la bague de réglage (19).
  2. Compresseur selon la revendication 1, caractérisé en ce que la géométrie du diffuseur (13) est montée directement sur une paroi arrière (14) du carter du compresseur (15) sur le côté aval de la roue de compresseur (9).
  3. Compresseur selon la revendication 1 ou 2,
    caractérisé en ce que les arbres d'aube (17) sont montés d'un côté sur une bague de support (18).
  4. Compresseur selon la revendication 3, caractérisé en ce que la bague de support (18) est positionnée entre les aubes de guidage (16) et la bague de réglage (19).
  5. Compresseur selon la revendication 3, caractérisé en ce que les éléments de réglage (20) sur la bague de réglage (19) s'engagent au-dessus de la bague de support (18) sur la face extérieure radiale de celle-ci.
  6. Compresseur selon la revendication 3 ou 4,
    caractérisé en ce que la bague de réglage (19) est montée sur la bague de support (18).
  7. Compresseur selon la revendication 5, caractérisé en ce que la bague de support (18) est reçue dans la bague de réglage (19) et la face extérieure radiale de la bague de support (18) est montée rotative sur la face intérieure radiale de la bague de réglage (19).
  8. Compresseur selon la revendication 5, caractérisé en ce que des éléments de support en saillie axiale sont agencés sur la bague de support (18) et sont montés rotatifs sur la face intérieure radiale de la bague de réglage (19).
EP03797228A 2002-08-23 2003-08-07 Compresseur dans un turbocompresseur a gaz d'echappement pour un moteur a combustion interne Expired - Fee Related EP1532368B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10238658A DE10238658A1 (de) 2002-08-23 2002-08-23 Verdichter, insbesondere in einem Abgasturbolader für eine Brennkraftmaschine
DE10238658 2002-08-23
PCT/EP2003/008741 WO2004027265A1 (fr) 2002-08-23 2003-08-07 Compresseur dans un turbocompresseur a gaz d'echappement pour un moteur a combustion interne

Publications (2)

Publication Number Publication Date
EP1532368A1 EP1532368A1 (fr) 2005-05-25
EP1532368B1 true EP1532368B1 (fr) 2006-05-10

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP03797228A Expired - Fee Related EP1532368B1 (fr) 2002-08-23 2003-08-07 Compresseur dans un turbocompresseur a gaz d'echappement pour un moteur a combustion interne

Country Status (4)

Country Link
US (1) US7186077B2 (fr)
EP (1) EP1532368B1 (fr)
DE (2) DE10238658A1 (fr)
WO (1) WO2004027265A1 (fr)

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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
DE102007023915B4 (de) 2006-06-09 2019-07-04 Borgwarner Inc. Turbolader und Verdichter für Turbolader
DE102007025128A1 (de) * 2007-05-30 2008-12-04 Mahle International Gmbh Ladeeinrichtung
CN102149911A (zh) * 2008-09-25 2011-08-10 博格华纳公司 涡轮增压器及其对应的调整环
US8118545B2 (en) * 2008-10-01 2012-02-21 Kansas State University Research Foundation Variable geometry turbocharger
US8540484B2 (en) * 2010-07-23 2013-09-24 United Technologies Corporation Low mass diffuser vane
CN103477087B (zh) * 2011-03-24 2016-07-13 皮尔伯格泵技术有限责任公司 机械式冷却剂泵
DE112012002901T5 (de) * 2011-08-24 2014-04-24 Borgwarner Inc. Luftzuführvorrichtung für eine Brennstoffzelle
KR101193871B1 (ko) 2012-02-24 2012-10-26 한국터보기계(주) 가변 디퓨저를 구비한 터보 압축기
US10030669B2 (en) * 2014-06-26 2018-07-24 General Electric Company Apparatus for transferring energy between a rotating element and fluid
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KR102659630B1 (ko) 2016-12-14 2024-04-22 한화에어로스페이스 주식회사 가변 베인 장치
DE102017118950A1 (de) * 2017-08-18 2019-02-21 Abb Turbo Systems Ag Diffusor für einen Radialverdichter
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US11092032B2 (en) * 2018-08-28 2021-08-17 Pratt & Whitney Canada Corp. Variable vane actuating system
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Also Published As

Publication number Publication date
US7186077B2 (en) 2007-03-06
US20050207885A1 (en) 2005-09-22
WO2004027265A1 (fr) 2004-04-01
DE10238658A1 (de) 2004-03-11
DE50303308D1 (de) 2006-06-14
EP1532368A1 (fr) 2005-05-25

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