EP1061265A1 - Groupe de suralimentation pour un gros moteur diesel - Google Patents

Groupe de suralimentation pour un gros moteur diesel Download PDF

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Publication number
EP1061265A1
EP1061265A1 EP00810411A EP00810411A EP1061265A1 EP 1061265 A1 EP1061265 A1 EP 1061265A1 EP 00810411 A EP00810411 A EP 00810411A EP 00810411 A EP00810411 A EP 00810411A EP 1061265 A1 EP1061265 A1 EP 1061265A1
Authority
EP
European Patent Office
Prior art keywords
compressor
diffuser
air
outlet
impeller
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
EP00810411A
Other languages
German (de)
English (en)
Other versions
EP1061265B1 (fr
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
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First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=8242876&utm_source=***_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP1061265(A1) "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/fr
Publication of EP1061265A1 publication Critical patent/EP1061265A1/fr
Application granted granted Critical
Publication of EP1061265B1 publication Critical patent/EP1061265B1/fr
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
    • 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
    • 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 supercharger for a large diesel engine according to the preamble of the independent claim.
  • purge or charge air which the cylinders for purging and for the combustion process is fed to compress.
  • a charging group usually comprises a compressor in which fresh air is sucked in by means of an impeller, compressed and by a Exit spiral is ejected, as well as a turbine, which the impeller of the compressor drives and an intercooler.
  • the turbine is powered by the hot exhaust gases that occur in the cylinders during combustion, driven.
  • the turbine and the compressor are also called turbochargers designated. Downstream of the turbocharger is an intercooler, in which the compressed air is cooled. After going through the The charge air cooler mostly gets its air through an inlet receiver designated container to the individual cylinders. Depending on the type of Large diesel engines feed the air into the cylinders different places.
  • the diffuser is, for example, as a self expanding tube in which the flow cross-section for the Air is constantly expanding.
  • the charging group should make the best possible use of space guarantee.
  • the charging group solving this task is characterized by the characteristics of the characterized independent claim.
  • a supercharger for a large diesel engine proposed using a compressor for compressing air that acts as purge air Cylinders of the large diesel engine is supplied, which compressor one Outlet for the compressed air and one arranged on an axis Has impeller for compressing the air, with a turbine for driving of the impeller of the compressor, the turbine with exhaust gases from the Is driven by cylinders, and with a diffuser to reduce the Flow rate of the compressed air, which with the outlet of the compressor is connected.
  • the compressor outlet is on one Height level arranged, which with respect to the normal use is on or above the axis of the compressor.
  • turbocharger The unit consisting of compressor and turbine is called a turbocharger.
  • compressor and turbine are in one Housing housed. Therefore in the following the "foot level of the Compressor "as synonymous with the" base level of the turbocharger " understand.
  • the diffuser is preferably tubular in the direction of flow of the air designed to extend and extends essentially to the foot level of the compressor or turbocharger.
  • the compressor or turbocharger is on mounted on a platform so that its base level rests on the platform.
  • the fact that the diffuser is the base of the compressor or Turbocharger does not fall below an intercooler, in which the from Air coming into the diffuser flows in, just below the platform to be ordered. This reduces the overall height of the Charging group, which is particularly with a view to being as compact as possible Design of the large diesel engine is advantageous.
  • the diffuser is particularly efficient when it turns essentially flared at least over part of its length, where the half opening angle of the extension is less than 12 °, is in particular 4 ° to 8 °.
  • the diffuser with respect to the flow direction the air is at least partially curved.
  • the diffuser can for example at its with the outlet of the compressor connected end so that it is a continuation of the Exit spiral of the compressor forms.
  • the diffuser one at its end connected to the discharge of the compressor Has entry surface that is at most half, in particular at most one Third of the exit surface at the other end of the diffuser is.
  • the high flow rate of air e.g. 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 exit of the diffuser. This can create significant pressure regain what, especially from a thermodynamic point of view the efficiency of charging is advantageous.
  • the diffuser is designed in one piece.
  • the diffuser comprises at least two arranged one behind the other with respect to the direction of flow of the air Parts, a compensator being provided between the two parts.
  • the compensator can cause thermal changes the expansion of the diffuser and volute casing can be compensated.
  • the diffuser has a fastening device for Fixing the diffuser and for removing those acting on the diffuser Has forces, the fastening device substantially on the is arranged at the same height level as the axis of the impeller of the Compressor. Because the diffuser is not yet at this level maximum flow cross-section has also been reached by the pressure forces in the air are not so great.
  • the charging group according to the invention is particularly suitable for such Large diesel engines, which are particularly compact and space-saving Design is sought.
  • Fig. 1 shows essential in a partially highly schematic representation Parts of an embodiment of a large diesel engine, which as longitudinally flushed two-stroke engine is formed and overall with the Reference numeral 10 is designated. With the reference numeral 11 is one of the Usually designated several cylinders of the large diesel engine 10.
  • a piston 14 is arranged in the cylinder 11 so as to be movable up and down.
  • the Piston is by means of a piston rod 15 with a not shown Cross head connected, which on the other hand via a push rod with the Crankshaft of the large diesel engine 10 is connected.
  • a plurality of purge air slots 16 are provided, which depending on Position of the piston 14 are covered or released by this.
  • the purge air slots 16 can the fresh air referred to as purge or charge air flow into the cylinder 11, as indicated by the arrow S.
  • One or more injection nozzles 12 are located in the upper region of the cylinder 11 for introducing fuel into the combustion chamber of the cylinder 11 provided, and a centrally arranged outlet valve 13 through which the gases generated during combustion flow out as exhaust gas.
  • the Exhaust gas flows through an exhaust pipe 8, which is connected to the exhaust valve 13 connects into an exhaust gas receiver 6.
  • the Exhaust gas receiver 6 also connected to the other cylinders.
  • the charging group 1 includes one Compressor 2 for compressing air, a turbine 3 for driving the Compressor 2, a diffuser 4 connected downstream of the compressor 2 for Reduce the flow velocity of the compressed air, as well as one Charge air cooler 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 air flows through a pressure line 17 to an inlet receiver 18, from which the purge air to the Purge air slots 16 of the cylinder 11 arrives. If the piston 14 the Purge air slots 16 then releases the purge air into the cylinder 11 flow in as indicated by arrow S in Fig. 1.
  • the compressor 2 (see FIG. 2) comprises an impeller 21 which is on an axis A is arranged and with several each extending away from the axis A. Buckets or wings 211 is provided. The direction of rotation of the impeller 21 is indicated by the arrow D in FIG. 2. Around the impeller 21 an exit spiral 22 is provided. Regarding the radial direction between the impeller 21 and the outlet spiral 22 in a known manner Several stationary guide vanes 25 are provided.
  • the Outlet 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 increases seen in the direction of rotation D.
  • the admission of the Compressor 2 is arranged so that the fresh air drawn in in the direction the 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 22a, of which the compressed air reaches the outlet 23 of the compressor 2.
  • the outlet 23 means the end of the outlet spiral 22, the means the cross-sectional area of the exit spiral 22 that lies where the spiral space 22a is just making its first turn through 360 ° around the axis A. (ie a complete course of the spiral).
  • the spiral space 22a begins at that with B. designated place and expands - seen in the direction of rotation D - with respect to the radial direction.
  • the outer wall of the exit spiral 22 thus describes a spiral in this representation.
  • the outlet 23 of the compressor 2 According to the illustration in FIG. 2, the cross section of the outlet 23 is radial extension of the connecting line from axis A to Point B.
  • the outlet 23 of the compressor 2 is on one Height level arranged which with respect to that shown in Fig. 2 normal position of use lies above the axis A of the compressor 2.
  • the compressor 2 or the housing of the turbocharger 2, 3 also has one Foot 24, which is mounted on a platform 19 which is on the motor housing is fixed.
  • the lower boundary surface of the foot 24 with which the foot 24 contacts the platform 19, is used as the base level 24a of the compressor 2 designated.
  • the impeller 21 of the compressor is in a known manner from the Turbine 3 (see Fig. 1) driven.
  • the turbine 3 is preferably on the same axis A is mounted on which the impeller 21 is also arranged.
  • the exhaust gas flows out of the exhaust gas receiver 6 through an exhaust gas line 7 the turbine 3 and drives it. After flowing through the turbine 3, the Exhaust gas discharged through a further exhaust pipe, not shown, like this the arrow G in Fig. 1 indicates.
  • the rotating turbine 3 drives the impeller 21 of the axis A.
  • Compressor 2 This draws in fresh air through the inlet shown in FIG. 1 lies behind the drawing plane and is therefore not visible.
  • the fresh air flows from the direction of the axis A on the impeller 21 and is by the latter Wings 211 promoted in the spiral space 22a. Then the flows compressed air out of the compressor 2 through the outlet 23.
  • the outlet 23 of the compressor 2 is connected to the diffuser 4.
  • the Diffuser 4 is tubular, widening in the direction of air flow designed.
  • the diffuser 4 has an entry surface 41 at one end and at its other end an exit surface 42 for the compressed Air.
  • the diffuser is 4th designed in one piece.
  • the diffuser 4 is such curved that he is a continuation of the exit spiral 22 of the Compressor 2 forms.
  • the diffuser 4 adjoins the outlet directly 23 of the compressor 2 and is in the direction of flow increasing cross section. That connected to the outlet 23
  • the end of the diffuser 4 forms the entry surface 41 of the diffuser 4, which is the same is the cross-sectional area of the outlet 23 of the compressor 2.
  • the diffuser 4 can, together with the outlet spiral 22, as a structural unit be designed so that it is an integral part of the compressor 2. It it is also possible to manufacture the diffuser 4 as a separate component and then to be connected to the outlet spiral 22, for example by means of a Flange connection or a welded connection.
  • the charge air cooler comprises 5, which is arranged directly under the platform 19, an air transfer duct 51, which is connected to the lower end of the diffuser 4, so that the air flowing through the outlet surface 42 of the diffuser 4 through the latter Air passage 51 can flow into the charge air cooler 5.
  • a compensator 43 provided for thermal expansion of the diffuser and the Compensate the spiral casing of the outlet spiral 22.
  • the compensator 43 is designed, for example, as a bellows and via flange connections 43a connected to the diffuser 4.
  • the compensator 43 is connected then the air inlet duct 51 of the charge air cooler 5.
  • Fastening means (not shown) on the diffuser 4 are also preferred provided the forces and torques on the motor housing to derive.
  • the entire diffuser 4 is preferably designed such that its Exit surface 42 at least twice as large and preferably at least is three times the size of its entrance area 41.
  • the flow velocity of the compressed can be measured Air, for example, up to 100 m / s through the entrance surface 41 of the Diffuser 4 flows, reduce to typically 40 m / s to 30 m / s, which air pressure is obtained to a considerable extent.
  • FIG. 3 shows in a representation analogous to Fig. 2, the compressor 2 and Diffuser 4 of a further embodiment of the invention Charger group 1.
  • the following is mainly the differences received, otherwise the explanations apply to that in FIG. 2 shown embodiment in an analogous manner also for the 3 shown in FIG. In particular, they have The same reference numerals in FIG. 3 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 part 4a immediately adjoins the outlet 23 of the compressor 2 and is preferably with one in the flow direction increasing cross section. That connected to the outlet 23
  • the end of the upper part 4a forms the entry surface 41 of the diffuser 4 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 level at which the axis A of the impeller 21 lies so that the exit surface of the upper part 4a in is 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 to be connected to the outlet spiral 22, for example by means of a Flange connection or a welded connection.
  • the compensator 43 is between the top Part 4a and the lower part 4b provided.
  • the compensator is for example via flange connections 43a to the upper and the lower part 4a, 4b of the diffuser connected.
  • 3 are preferred Fasteners provided on the diffuser 4 to the forces and Derive torques on the motor housing. Because the diffuser 4 on Height of the axis A has not yet reached its maximum cross section here in particular the forces caused by the static pressure not so great. Therefore, it is in terms of mechanical stress Fasteners advantageous, this essentially 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 therefore on the same height as the base level 24a of the compressor 2 or Turbocharger 2.3.
  • the lower part 4b is funnel-shaped, that is it broadens conically from the compensator 43 to Exit surface 42.
  • the cross-sectional area of the lower part 4b can angular, e.g. B. square, or round, z. B. circular. in the With regard to the best possible efficiency of the diffuser 4, it is advantageous for the Design the extension so that half the opening angle a is less than 12 ° and in particular 4 ° to 8 °.
  • the diffuser 4 widens from the outlet 23 of the compressor 2 to Level 24a of the compressor 2, where the diffuser 4 ends.
  • the Expansion such that the size of the entry surface 41 of the diffuser 4 again at most half, preferably at most a third of Size of the exit surface 42 of the diffuser 4 is.
  • the outlet 23 of the compressor at height or above the axis A of the impeller 21 is between the outlet 23 and the Foot level 24a of the compressor 2 or the platform 19 has sufficient space around there a diffuser 4 with the geometries described above regarding the opening angle a and the ratio of input and Place exit surface 41.42.
  • the diffuser 4 thus ends at the height the base level 24a of the compressor 2 or the turbocharger 2, 3 without the effective diffuser length must be reduced. Since the diffuser 4 not down over the base level 24a of the compressor 2 or the Platform 19 protrudes, the charge air cooler 5 directly, that is without Distance, are arranged below the platform 19, whereby the total height of charging group 1 reduced.
  • the charging group 1 according to the invention also for other large diesel engines than the longitudinally purged described here Two-stroke engine is suitable.
  • the inventive Charging group 1 in an analogous manner also part of a Four-stroke large diesel engine, in which the charge air via one or more inlet 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 Groupe de suralimentation pour un gros moteur diesel Revoked EP1061265B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP00810411A EP1061265B1 (fr) 1999-06-14 2000-05-15 Groupe de suralimentation pour un gros moteur diesel

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP99810521 1999-06-14
EP99810521 1999-06-14
EP00810411A EP1061265B1 (fr) 1999-06-14 2000-05-15 Groupe de suralimentation pour un gros moteur diesel

Publications (2)

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

Family

ID=8242876

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00810411A Revoked EP1061265B1 (fr) 1999-06-14 2000-05-15 Groupe de suralimentation pour un gros moteur diesel

Country Status (7)

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

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN100404878C (zh) * 2003-06-05 2008-07-23 星光化工机株式会社 离心鼓风机
EP2918790A1 (fr) * 2014-03-12 2015-09-16 Mitsubishi Turbocharger and Engine Europe B.V. Carter de compresseur
WO2020057855A1 (fr) * 2018-09-19 2020-03-26 Robert Bosch Gmbh Compresseur
EP3036441B1 (fr) * 2013-08-19 2020-11-25 Dynamic Boosting Systems Limited Diffuseur pour compresseur à écoulement tangentiel en flèche négative

Families Citing this family (7)

* 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
PL1881173T3 (pl) * 2006-07-19 2009-10-30 Waertsilae Nsd Schweiz Ag Multidyfuzor do tłokowego silnika spalinowego oraz tłokowy silnik spalinowy
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
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

Citations (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.
DE19710408A1 (de) * 1997-03-13 1998-09-17 Man B & W Diesel Gmbh Hubkolben-Brennkraftmaschine

Patent Citations (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.
DE19710408A1 (de) * 1997-03-13 1998-09-17 Man B & W Diesel Gmbh Hubkolben-Brennkraftmaschine

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN100404878C (zh) * 2003-06-05 2008-07-23 星光化工机株式会社 离心鼓风机
EP3036441B1 (fr) * 2013-08-19 2020-11-25 Dynamic Boosting Systems Limited Diffuseur pour compresseur à écoulement tangentiel en flèche négative
EP2918790A1 (fr) * 2014-03-12 2015-09-16 Mitsubishi Turbocharger and Engine Europe B.V. Carter de compresseur
WO2020057855A1 (fr) * 2018-09-19 2020-03-26 Robert Bosch Gmbh Compresseur

Also Published As

Publication number Publication date
JP2001020747A (ja) 2001-01-23
EP1061265B1 (fr) 2005-12-14
KR100659677B1 (ko) 2006-12-21
CN1277317A (zh) 2000-12-20
KR20010007159A (ko) 2001-01-26
DE50011843D1 (de) 2006-01-19
CN1175189C (zh) 2004-11-10
DK1061265T3 (da) 2006-02-06
PL340532A1 (en) 2000-12-18

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