EP1061265B1 - Aufladegruppe für einen Grossdieselmotor - Google Patents

Aufladegruppe für einen Grossdieselmotor Download PDF

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Publication number
EP1061265B1
EP1061265B1 EP00810411A EP00810411A EP1061265B1 EP 1061265 B1 EP1061265 B1 EP 1061265B1 EP 00810411 A EP00810411 A EP 00810411A EP 00810411 A EP00810411 A EP 00810411A EP 1061265 B1 EP1061265 B1 EP 1061265B1
Authority
EP
European Patent Office
Prior art keywords
compressor
air
diffusor
diffuser
outlet
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.)
Revoked
Application number
EP00810411A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1061265A1 (de
Inventor
Henri Ruch
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.)
Wartsila NSD Schweiz AG
Original Assignee
Wartsila NSD Schweiz 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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=8242876&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP1061265(B1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Wartsila NSD Schweiz AG filed Critical Wartsila NSD Schweiz AG
Priority to EP00810411A priority Critical patent/EP1061265B1/de
Publication of EP1061265A1 publication Critical patent/EP1061265A1/de
Application granted granted Critical
Publication of EP1061265B1 publication Critical patent/EP1061265B1/de
Anticipated expiration legal-status Critical
Revoked legal-status Critical Current

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Classifications

    • 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
    • F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
    • 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
    • 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
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F7/00—Casings, e.g. crankcases or frames
    • F02F2007/0097—Casings, e.g. crankcases or frames for large diesel engines
    • 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 Aufladeoli for a large diesel engine according the preamble of the independent claim (see DE-A-197 10 408).
  • a charging group usually comprises a compressor in which By means of an impeller sucked fresh air, compressed and by a Exit spiral is ejected, as well as a turbine, which is the impeller of the compressor drives and a charge air cooler.
  • the turbine is using the hot exhaust gases that are produced during combustion in the cylinders, driven.
  • the turbine and the compressor are also called turbochargers designated. Downstream of the turbocharger is a charge air cooler, in which the compressed air is cooled. After going through the Intercooler usually enters the air via an inlet receiver designated container to the individual cylinders. Depending on the type of Large diesel engine is the supply of air into the cylinder different places.
  • the air via scavenging air slots, in the lower part of the cylinder are arranged, introduced into the cylinder.
  • the charge air via one or more intake valves in the cylinder cover are arranged, introduced into the cylinder.
  • a diffuser provided in which the flow velocity of the Compressor escaping air is reduced, causing pressure recovers.
  • the diffuser is for example as a expanding tube formed in which the flow cross section for the Air constantly expanding.
  • the charging group solving this problem is characterized by the features of independent claim characterized.
  • a charging group for a large diesel engine proposed with a compressor for compressing air, which is called purge air Cylinders of the large diesel engine is supplied, which compressor a Outlet for the compressed air and one arranged on an axis Impeller for compressing the air, with a turbine for driving the impeller of the compressor, the turbine with exhaust gases from the Cylinders is driven, and with a diffuser to reduce the Flow velocity of the compressed air, which with the outlet the compressor is connected.
  • the outlet of the compressor is on one Height level arranged, which with respect to the normal position of use is on or above the axis of the compressor.
  • the diffuser can be arranged laterally on the compressor be, whereby the distance between the compressor and the downstream modules, such as a charge air cooler, clearly can be reduced without the length seen in the flow direction of the diffuser, which is essential to its effectiveness, be downsized got to. This allows a particularly compact embodiment of the Charging group, and the available space is optimal exploited.
  • the unit of compressor and turbine is called a turbocharger.
  • the compressor and the turbine are in a common Housing housed. Therefore, in the following, the "foot level of the Compressor "as synonymous with the" foot plane of the turbocharger "to understand.
  • the diffuser is tubular, in the flow direction of the air designed widening and extends substantially to the foot level of the compressor or turbocharger.
  • the compressor or turbocharger is on mounted on a platform so that its foot level rests on the platform. Due to the fact that the diffuser the foot level of the compressor or the Turbocharger does not fall below, a charge air cooler, in which the incoming air coming from the diffuser, immediately below the platform to be ordered. This reduces the overall height of the Aufladeoli, which in particular with regard to a compact as possible Design of the large diesel engine is advantageous.
  • the diffuser is particularly efficient when it is expanded substantially conically over at least part of its length, half the opening angle of the extension being less than 12 °, in particular 4 ° to 8 °.
  • the diffuser with respect to the flow direction the air is at least partially curved.
  • the Diffuser be placed as close to the side of the compressor, thereby The available space is very well utilized.
  • the diffuser For example, it can be connected to the outlet of the compressor connected end so that it is a continuation of the Forming spiral of the compressor forms.
  • the diffuser at its end connected to the outlet of the compressor one Has inlet surface, which is at most half, in particular at most one One third of the exit area at the other end of the diffuser.
  • the z. B. at the outlet of the compressor can be up to 100 m / s, in the diffuser to significantly lower values, for example, 30 m / s to 40 m / s at the output of the diffuser, reduce. This allows considerable pressure recover, which in particular under thermodynamic aspects for the efficiency of charging is advantageous.
  • the diffuser is designed in one piece.
  • the diffuser comprises at least two with respect to the flow direction of the air arranged one behind the other Parts, wherein between the two parts a compensator is provided.
  • the compensator can cause thermal changes the expansion of the diffuser and volute casing are compensated.
  • the diffuser is a fastening device for Fix the diffuser and remove it from the diffuser Has forces, wherein the fastening device substantially on the same height level is arranged as the axis of the impeller of the Compressor. Since the diffuser at this height level is not his Maximum flow cross-section has also been achieved by the pressure the air did not cause such great forces.
  • the charging group according to the invention is particularly suitable for such Large diesel engines, where a particularly compact and space-saving Design is sought.
  • Fig. 1 shows in a partially highly schematic representation essential Parts of an embodiment of a large diesel engine, as longitudinally rinsed two-stroke engine is formed and overall with the Reference numeral 10 is designated.
  • Reference numeral 11 is one of Usually referred to several cylinders of the large diesel engine 10.
  • a piston 14 is arranged movable up and down. Of the Piston is by means of a piston rod 15 with a not shown Crosshead connected, on the other hand via a push rod with the Crankshaft of the large diesel engine 10 is connected.
  • a plurality of scavenging air slots 16 are provided, which depending on Position of the piston 14 are covered by this or release.
  • one or more injection nozzles 12 for introducing fuel into the combustion chamber of the cylinder 11 provided, and a centrally disposed outlet valve 13 through which the gases produced during combustion flow out as exhaust gas.
  • the Exhaust gas flows through an exhaust nozzle 8, which is connected to the outlet valve 13 connects, in an exhaust gas receiver 6.
  • the Exhaust gas receiver 6 also connected to the other cylinders.
  • the charging group 1 comprises a Compressor 2 for compressing air, a turbine 3 for driving the Compressor 2, a compressor 2 downstream of the diffuser 4 for Reduce the flow velocity of the compressed air, as well as a Intercooler 5, in which the compressed air is cooled.
  • a Compressor 2 for compressing air
  • a turbine 3 for driving the Compressor 2
  • a compressor 2 downstream of the diffuser 4 for Reduce the flow velocity of the compressed air
  • Intercooler 5 in which the compressed air is cooled.
  • the Compressor 2 and the turbine 3 are in a common housing arranged and form a turbocharger.
  • the compressor 2 (see FIG. 2) comprises an impeller 21 mounted on an axis A is arranged and with several each extending away from the axis A. Shovels or wings 211 is provided. The direction of rotation of the impeller 21 is indicated in Fig. 2 by the arrow D. To the impeller 21 is around an exit spiral 22 is provided. With respect to the radial direction between the impeller 21 and the outlet spiral 22 in per se known Way several stationary Nachleitschaufeln 25 is provided.
  • the Exit spiral 22 surrounds the radially outer ends of the guide vanes 25 and delimits a spiral space 22a which extends in the direction of rotation D of the Impeller 21 seen radially expanded so that the distance d between the radially outer ends of the guide vanes 25 and the wall of the Exit spiral 22 seen in the direction of rotation D increases.
  • the inlet of the Compressor 2 is arranged so that the intake fresh air in the direction A axis A flows to the impeller 21, as indicated by the arrow F in Fig. 2.
  • the impeller 21 conveys the fresh air into the spiral space 22 a, of which the compressed air to the outlet 23 of the compressor 2 passes.
  • the spiral space 22a begins at the B with designated point and expands - seen in the direction of rotation D - with respect to the radial direction.
  • the outer wall of the outlet spiral 22 thus describes a spiral in this illustration.
  • the cross section of the outlet 23 is the radially extending extension of the connecting line from the axis A to Point B.
  • the outlet 23 of the compressor 2 is on a Height level arranged which with respect to that shown in Fig. 2 normal operating position above the axis A of the compressor 2 is located.
  • the compressor 2 and the housing of the turbocharger 2,3 also has a Foot 24, which is mounted on a platform 19, which on the motor housing is fixed.
  • the lower boundary surface of the foot 24, with which the foot 24 contacted the platform 19, is used as foot level 24a of the compressor. 2 designated.
  • the impeller 21 of the compressor is in a conventional manner of the Turbine 3 (see Fig. 1) driven.
  • the turbine 3 is preferably on mounted on the same axis A, on which the impeller 21 is arranged.
  • the exhaust gas flows from the exhaust gas receiver 6 through an exhaust pipe 7 the turbine 3 and drives it. After flowing through the turbine 3 is the Exhaust through a further, not shown exhaust pipe removed as this the arrow G in Fig. 1 indicates.
  • the rotating turbine 3 drives over the axis A, the impeller 21 of the Compressor 2 on. This sucks fresh air through the inlet, which in Fig. 1 behind the drawing plane and therefore is not visible.
  • the fresh air flows from the direction of the axis A on the impeller 21 and is of the Wings 211 promoted in the spiral space 22a. Then flows the compressed air through the outlet 23 from the compressor 2 out.
  • the outlet 23 of the compressor 2 is connected to the diffuser 4.
  • the diffuser 4 Of the Diffuser 4 is tubular, expanding in the flow direction of the air designed.
  • the diffuser 4 has at its one end an entry surface 41st and at its other end an exit surface 42 for the compressed Air.
  • the diffuser 4 designed in one piece. As shown in FIG. 2, the diffuser 4 is such curved to form a continuation of the exit spiral 22 of the Compressor 2 forms.
  • the diffuser 4 closes immediately to the outlet 23 of the compressor 2 and is one in the flow direction formed increasing cross-section. That connected to the outlet 23 End of the diffuser 4 forms the entrance surface 41 of the diffuser 4, the same the cross-sectional area of the outlet 23 of the compressor 2 is.
  • the diffuser 4, together with the outlet spiral 22 as a structural unit be configured so that it is an integral part of the compressor 2. It But it is also possible to produce the diffuser 4 as a separate component and then connect to the exit spiral 22, for example by means of a Flanged connection or a welded connection.
  • the intercooler comprises 5, which is located directly under the platform 19, an air passage channel 51, which is connected to the lower end of the diffuser 4, so that the through the exit surface 42 of the diffuser 4 effluent air through this Air passage 51 can flow into the charge air cooler 5.
  • a compensator 43 provided to thermally induced expansions of the diffuser and the Spiral housing of the exit spiral 22 to compensate.
  • the compensator 43 is designed for example as a bellows and flange connections 43 a connected to the diffuser 4. The compensator 43 closes then the air inlet channel 51 of the charge air cooler 5 at.
  • fastening means on the diffuser 4th provided the forces and torques on the motor housing derive.
  • the entire diffuser 4 is preferably designed so that its Exit surface 42 at least twice as large and preferably at least three times as large as its entrance surface 41.
  • these geometric Dimensions can be the flow rate of the compressed Air, for example, up to 100 m / s through the entrance surface 41 of Diffuser 4 flows, typically reduce to 40 m / s to 30 m / s, which is gained in considerable measure pressure of the air.
  • Fig. 3 shows in a representation analogous to Fig. 2, the compressor 2 and the Diffuser 4 of a further embodiment of the inventive Charger group 1.
  • the following is mainly on the differences otherwise, the explanations regarding the in Fig. 2 apply shown embodiment in an analogous manner for the same in Fig. 3 embodiment shown.
  • the Reference sign in FIG. 3 has the same meaning as in FIG. 2.
  • the diffuser 4 comprises two parts 4a, 4b, which are each designed as pipe sections and with respect the flow direction of the air are arranged one behind the other.
  • the top, curved portion 4a closes immediately to the outlet 23rd of the compressor 2 and is preferably one in the flow direction formed increasing cross-section. That connected to the outlet 23 End of the upper part 4a forms the entrance surface 41 of the diffuser 4, the is equal to the cross-sectional area of the outlet 23 of the compressor 2.
  • the Upper part 4a is curved in the same direction as the exit spiral 22 and extends approximately to the height level on which the axis A of the impeller 21 is located so that the exit surface of the upper part 4a in essentially parallel to the platform 19.
  • the upper part 4a can be designed together with the outlet spiral 22 as a structural unit, so that the upper part 4a is an integral part of the compressor 2. It is but also possible to produce the upper part 4a as a separate component and then connect to the exit spiral 22, for example by means of a Flanged connection or a welded connection.
  • the compensator 43 is between the upper Part 4a and the lower part 4b provided.
  • the compensator is for example, via flange 43a with the top and the lower part 4a, 4b of the diffuser connected.
  • Fastening means provided on the diffuser 4 to the forces and Derive torques to the motor housing. Since the diffuser 4 on Height of the axis A has not yet reached its maximum cross-section are here in particular the forces caused by the static pressure forces not so great. Therefore, it is in terms of mechanical stress of Attachment advantageous, this substantially at the height level to provide the axis A of the impeller 21.
  • the lower part 4b of the diffuser extends from the compensator 43 to the Platform 19 on which the turbocharger 2,3 is mounted. Preferably the lower end of the lower part 4b by fastening means 44 on the Platform 19 attached.
  • the exit surface 42 of the diffuser 4 is thus on the the same height as the foot level 24a of the compressor 2 and the Turbocharger 2,3.
  • the lower part 4b is funnel-shaped, that is it expands substantially conically from the compensator 43 to the Exit surface 42.
  • the cross-sectional area of the lower part 4b can thereby angular, z. B. quadrangular, or round, z. B. circular, be formed. in the With regard to the best possible efficiency of the diffuser 4, it is advantageous that Extension so that half the opening angle a less than 12 ° and in particular 4 ° to 8 °.
  • the diffuser 4 extends from the outlet 23 of the compressor 2 to the Foot level 24a of the compressor 2, where the diffuser 4 ends. It is the Extension such that the size of the entrance surface 41 of the diffuser 4th again at most half, preferably at most one third of the Size of the exit surface 42 of the diffuser 4 is.
  • the outlet 23 of the compressor at or above The axis A of the impeller 21 is located between the outlet 23 and the Foot level 24a of the compressor 2 and the platform 19 sufficient space around there a diffuser 4 with the geometries described above concerning the opening angle a and the ratio of on and off Exit surface 41,42 to place.
  • the diffuser 4 thus ends at the height the foot level 24a of the compressor 2 and the turbocharger 2,3, without For this, the effective diffuser length must be reduced. Since the diffuser 4 not down over the foot level 24a of the compressor 2 and the Platform 19 projects, the intercooler 5 can directly, that is without Distance to be arranged below the platform 19, whereby the entire height of the charging group 1 reduced.
  • the charging group 1 according to the invention is also suitable for other large diesel engines than the longitudinally-flushed ones described here Two-stroke engine is suitable.
  • the inventive Charging group 1 in a similar manner also part of a Be four-stroke large diesel engine, in which the charge air over one or more Intake valves arranged in the cylinder cover are introduced into the cylinder becomes.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Supercharger (AREA)
EP00810411A 1999-06-14 2000-05-15 Aufladegruppe für einen Grossdieselmotor Revoked EP1061265B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP00810411A EP1061265B1 (de) 1999-06-14 2000-05-15 Aufladegruppe für einen Grossdieselmotor

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP99810521 1999-06-14
EP99810521 1999-06-14
EP00810411A EP1061265B1 (de) 1999-06-14 2000-05-15 Aufladegruppe für einen Grossdieselmotor

Publications (2)

Publication Number Publication Date
EP1061265A1 EP1061265A1 (de) 2000-12-20
EP1061265B1 true EP1061265B1 (de) 2005-12-14

Family

ID=8242876

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00810411A Revoked EP1061265B1 (de) 1999-06-14 2000-05-15 Aufladegruppe für einen Grossdieselmotor

Country Status (7)

Country Link
EP (1) EP1061265B1 (zh)
JP (1) JP2001020747A (zh)
KR (1) KR100659677B1 (zh)
CN (1) CN1175189C (zh)
DE (1) DE50011843D1 (zh)
DK (1) DK1061265T3 (zh)
PL (1) PL340532A1 (zh)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4011368B2 (ja) * 2002-02-27 2007-11-21 京セラ株式会社 無線通信システム及び無線通信方法
JP4590167B2 (ja) * 2003-06-05 2010-12-01 セイコー化工機株式会社 遠心送風機
DK1881173T3 (da) * 2006-07-19 2009-07-20 Waertsilae Nsd Schweiz Ag Multidiffusor til en stempelforbrændingsmotor samt stempelforbrændingsmotor
DE102010037969B4 (de) * 2010-10-05 2023-01-12 Ford Global Technologies, Llc. Brennkraftmaschine mit flüssigkeitsgekühlter Turbine und Verfahren zum Kühlen der Turbine
CN102606530B (zh) * 2011-01-18 2016-09-28 德昌电机(深圳)有限公司 离心装置及清洗装置
US8974178B2 (en) * 2012-01-17 2015-03-10 Hamilton Sundstrand Corporation Fuel system centrifugal boost pump volute
US9217369B2 (en) * 2012-03-15 2015-12-22 Siemens Aktiengesellschaft Compressor inlet manifold for a gas turbine engine
GB2519503B (en) * 2013-08-19 2015-08-12 Dynamic Boosting Systems Ltd Diffuser for a forward-swept tangential flow compressor
NL1040722B1 (en) * 2014-03-12 2015-11-19 Mitsubishi Turbocharger And Engine Europe B V Compressor housing.
CN106050700A (zh) * 2016-07-19 2016-10-26 东莞市宏铭通风设备有限公司 一种静音风机结构
DE102018215888A1 (de) * 2018-09-19 2020-03-19 Robert Bosch Gmbh Verdichter

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB567156A (en) * 1943-06-22 1945-01-31 Oswald Wans Improvements in or relating to turbo-blowers
CH286975A (de) * 1951-05-01 1952-11-15 Karrer Josef Fliehkraftgebläse, insbesondere Ventilator mit Spiralgehäuse.
DE19710408B4 (de) * 1997-03-13 2010-08-05 Man B & W Diesel A/S Hubkolben-Brennkraftmaschine

Also Published As

Publication number Publication date
CN1175189C (zh) 2004-11-10
KR20010007159A (ko) 2001-01-26
KR100659677B1 (ko) 2006-12-21
DE50011843D1 (de) 2006-01-19
PL340532A1 (en) 2000-12-18
DK1061265T3 (da) 2006-02-06
EP1061265A1 (de) 2000-12-20
CN1277317A (zh) 2000-12-20
JP2001020747A (ja) 2001-01-23

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