EP1347157A1 - Echangeur de pression dynamique à ondes - Google Patents

Echangeur de pression dynamique à ondes Download PDF

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Publication number
EP1347157A1
EP1347157A1 EP02006066A EP02006066A EP1347157A1 EP 1347157 A1 EP1347157 A1 EP 1347157A1 EP 02006066 A EP02006066 A EP 02006066A EP 02006066 A EP02006066 A EP 02006066A EP 1347157 A1 EP1347157 A1 EP 1347157A1
Authority
EP
European Patent Office
Prior art keywords
pressure
gas
duct
exhaust gas
pressure exhaust
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
EP02006066A
Other languages
German (de)
English (en)
Other versions
EP1347157B1 (fr
Inventor
Urs Wenger
Roger Martin
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.)
Swissauto Engineering SA
Original Assignee
Swissauto Engineering SA
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
Priority to DE50204848T priority Critical patent/DE50204848D1/de
Application filed by Swissauto Engineering SA filed Critical Swissauto Engineering SA
Priority to AT02006066T priority patent/ATE309455T1/de
Priority to ES02006066T priority patent/ES2252338T3/es
Priority to EP02006066A priority patent/EP1347157B1/fr
Priority to AU2003200866A priority patent/AU2003200866A1/en
Priority to US10/384,898 priority patent/US7080633B2/en
Priority to JP2003074333A priority patent/JP4335558B2/ja
Publication of EP1347157A1 publication Critical patent/EP1347157A1/fr
Application granted granted Critical
Publication of EP1347157B1 publication Critical patent/EP1347157B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F13/00—Pressure exchangers
    • 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
    • F02B33/00—Engines characterised by provision of pumps for charging or scavenging
    • F02B33/32—Engines with pumps other than of reciprocating-piston type
    • F02B33/42—Engines with pumps other than of reciprocating-piston type with driven apparatus for immediate conversion of combustion gas pressure into pressure of fresh charge, e.g. with cell-type pressure exchangers

Definitions

  • the invention relates to a gas dynamic Pressure wave machine according to the preamble of claim 1.
  • the WO 99/11914 mentioned at the beginning in turn prevents this continuous use of a gas bag with its losses, and eliminates the web that disturbs the pressure wave process between the exhaust duct and the gas pocket when the Inflow, as well as through the piping to the gas pocket occurring energy losses in the form of flow and Temperature losses and the restrictions in the Design of the other channels.
  • a disadvantage of all these processes is that in Partial load range of the internal combustion engine by blowing off the excess high pressure gas in the gas pockets or the Enlargement of the high pressure exhaust duct, the pressure in the High-pressure exhaust duct still remains too high, that is, the resulting negative pressure difference Charge air outlet from the pressure wave machine opposite High-pressure exhaust gas entry into the pressure wave machine increased internal combustion engine output losses and thus poorer consumption values in the partial load range of the Combustion engine. At the same time, however, remains insufficient reduction of the exhaust gas pressure over the Pressure wave process an unwanted boost pressure after the Blast machine exist. With the gasoline engine with its Load control via the throttle valve must now be higher Pressure in the intake line through the partial closing of the throttle valve can be reduced, what causes further losses in the form of throttle losses.
  • Figure 1 shows a development of the rotor gas dynamic pressure wave machine 2 with the Internal combustion engine 1, the high pressure exhaust duct 3 and Low-pressure exhaust duct 4 including the purge air S, the rotor 6 with the individual cells 18, the fresh air inlet 8, or low-pressure fresh air supply duct 14, the high-pressure charge air duct 10, which merges into the charge air duct 11 and leads to the internal combustion engine 1.
  • the pressure wave machine is known with Methods, for example characteristic methods and Design calculations based on those from the combustion engine manufacturer desired point, usually at the nominal speed of the Motors, optimally designed, either without pockets or with one or two or all three pockets can happen.
  • FIG. 2 based on FIG. 1, there is a high-pressure exhaust duct 3 shown, which has no means for Influencing the high pressure exhaust gas flow has.
  • the rotor 6 with its cells 18 is shown in a developed form and the gas housing 24, the high-pressure exhaust duct, can also be seen 3 and the low-pressure exhaust duct 4.
  • gas pocket 21 is shown in FIG. 2, as for example in the above-mentioned CH-A-681 738 is available.
  • This gas bag and especially the one there necessarily existing web 21 A between high-pressure exhaust duct and gas bag creates additional losses, especially if at low to medium speeds, Temperatures and throughputs usually blow off is unnecessary.
  • Figures 3 to 6a relate to the present invention also affect the high-pressure exhaust gas flow.
  • the invention is the developed rotor 40 with the cells 41 shown and, in contrast to the gas pocket 21 in Figure 2, a recess 48 serving as a gas pocket in the gas housing 34 provided, which are changed by a slider 49 can, as indicated by arrow 50.
  • the slide 49 is fully engaged in the direction of the arrow, so that the high-pressure exhaust duct is widened without a Footbridge has arisen.
  • the slide can be controlled in such a way by a person skilled in the art be moved so that the high pressure exhaust duct is widened until the pressure in it has dropped so far is that generated by the pressure wave process Boost pressure drops to the desired level.
  • Figures 4 and 4A is a variant of the slide shown, which is a pivotable part 51st acts, which is hinged to a hinge 52 and by control electronics similar to those above can be moved, which causes a widening 53 of the exhaust gas high-pressure duct.
  • 3A is schematically a valve 58 in Figures 5, 5A shown, e.g. in CH-A-681 738 for control of the gas pocket inflow is used.
  • the Control that the valve 58 is only moved so far that a sufficiently large proportion of high-pressure exhaust gas 31 for Maintaining the rotor purge in the recess 48 is redirected.
  • the valve 58 is then opened further and a line 56 released.
  • This line 56 is via a suitable connection duct with the low pressure exhaust duct 35 connected. Via this line 56 can now additional amount of exhaust gas directly into the practically below Low-pressure exhaust duct 35 at ambient pressure be blown off. This reduces the pressure in the high-pressure exhaust duct 31 to the desired lower level.
  • a roller 59 is shown schematically in FIGS. 6 and 6A shown as in a similar form in EP-A-0 210 328 is used to control the inflow of gas pockets. Also here the roller 59 is only moved so far that a sufficient large proportion of high-pressure exhaust gas 31 to maintain the Rotor flushing is diverted into the widening 53.
  • the roller 59 is then rotated further and gives the Connection channel 57 free.
  • the connecting channel 57 is with connected to the low-pressure exhaust gas duct 35.
  • This line can now add an additional amount of exhaust gas directly into the practical low-pressure exhaust gas duct 35 under ambient pressure be blown off. This reduces the pressure in the high-pressure exhaust duct 31 to the desired lower level.
  • the same measures can of course also be used previously known other methods for controlling the high pressure exhaust gas flow into the gas pockets.
  • the additional, directly from the high pressure exhaust duct 31 in the Low-pressure exhaust duct 35 passed exhaust gas flow over additional actuator take place, for example, by a microprocessor is controlled. It is irrelevant whether this additional actuator is a flap, a valve, a roller or a similar regulating element for additional blow-off from the high-pressure exhaust duct 31 in the Low-pressure exhaust duct 35.
  • the pressure wave machine enables over the entire area of the map Internal combustion engine both the negative pressure difference and thus the increased output work of the internal combustion engine to keep it as low as possible, as well as the blow-off volume to increase so far that the pressure in the high pressure exhaust duct can be reduced so far that the pressure in the Charge air duct can be reduced to such an extent that a partial closure of the throttle valve Internal combustion engine in the partial load range can be omitted.
  • the Effectiveness of the invention is particularly given when can be guaranteed that a sufficiently large Flue gas volume first by enlarging the high pressure flue gas duct 31, or through the gas pockets, directly into the Rotor is blown off, otherwise the pressure wave process is disturbed and thus the flushing of the rotor breaks down and undesirable exhaust gas is directed to the engine. This is by appropriate control engineering design of the invention sure.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Supercharger (AREA)
  • Mechanical Treatment Of Semiconductor (AREA)
  • Control Of Fluid Pressure (AREA)
EP02006066A 2002-03-18 2002-03-18 Echangeur de pression dynamique à ondes Expired - Lifetime EP1347157B1 (fr)

Priority Applications (7)

Application Number Priority Date Filing Date Title
AT02006066T ATE309455T1 (de) 2002-03-18 2002-03-18 Gasdynamische druckwellenmaschine
ES02006066T ES2252338T3 (es) 2002-03-18 2002-03-18 Sobrealimentador por ondas de presion gasodinamico.
EP02006066A EP1347157B1 (fr) 2002-03-18 2002-03-18 Echangeur de pression dynamique à ondes
DE50204848T DE50204848D1 (de) 2002-03-18 2002-03-18 Gasdynamische Druckwellenmaschine
AU2003200866A AU2003200866A1 (en) 2002-03-18 2003-03-06 Gas-dynamic pressure wave machine
US10/384,898 US7080633B2 (en) 2002-03-18 2003-03-07 Gas-dynamic pressure wave machine
JP2003074333A JP4335558B2 (ja) 2002-03-18 2003-03-18 ガス・ダイナミック圧力波過給機

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP02006066A EP1347157B1 (fr) 2002-03-18 2002-03-18 Echangeur de pression dynamique à ondes

Publications (2)

Publication Number Publication Date
EP1347157A1 true EP1347157A1 (fr) 2003-09-24
EP1347157B1 EP1347157B1 (fr) 2005-11-09

Family

ID=27771847

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02006066A Expired - Lifetime EP1347157B1 (fr) 2002-03-18 2002-03-18 Echangeur de pression dynamique à ondes

Country Status (7)

Country Link
US (1) US7080633B2 (fr)
EP (1) EP1347157B1 (fr)
JP (1) JP4335558B2 (fr)
AT (1) ATE309455T1 (fr)
AU (1) AU2003200866A1 (fr)
DE (1) DE50204848D1 (fr)
ES (1) ES2252338T3 (fr)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006020522A1 (de) 2006-05-03 2007-11-08 Robert Bosch Gmbh Verfahren zum Betreiben einer Brennkraftmaschine
WO2011132259A1 (fr) * 2010-04-20 2011-10-27 トヨタ自動車株式会社 Compresseur à ondes de pression
DE102010048345A1 (de) 2010-10-13 2012-04-19 Daimler Ag Druckwellenmaschine, insbesondere Druckwellenlader für eine Verbrennungskraftmaschine sowie Verbrennungskraftmaschine
DE102010054505B4 (de) * 2010-12-14 2014-06-12 Benteler Automobiltechnik Gmbh Druckwellenladeranordnung und Verfahren zum Betreiben einer Druckwellenladeranordnung
EP2837824B1 (fr) * 2013-08-15 2015-12-30 Danfoss A/S Machine hydraulique, en particulier échangeur de pression hydraulique
CN106321291A (zh) * 2015-07-07 2017-01-11 上海汽车集团股份有限公司 排量可调节的压力波增压器
US10724450B2 (en) * 2016-07-18 2020-07-28 Aerodyn Combustion LLC Enhanced pressure wave supercharger system and method thereof
DE102019208045B4 (de) * 2019-06-03 2023-05-11 Ford Global Technologies, Llc Mittels Comprex-Lader aufgeladene Brennkraftmaschine

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4488532A (en) * 1981-11-30 1984-12-18 Bbc Brown, Boveri & Company, Limited Gas-dynamic pressure wave machine with exhaust gas bypass
EP0210328A1 (fr) 1985-04-30 1987-02-04 BBC Brown Boveri AG Turbochargeur pour un moteur à combustion interne avec un dispositif de commande de l'écoulement du gaz d'échappement à haute pression
CH681738A5 (fr) 1989-11-16 1993-05-14 Comprex Ag
WO1999011914A1 (fr) 1997-08-29 1999-03-11 Swissauto Engineering S.A. Machine a ondes de pression gazodynamique
WO1999011194A1 (fr) 1997-09-05 1999-03-11 Funt Lawrence A Systeme reservoir medical

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0123990B1 (fr) * 1983-05-02 1986-12-30 BBC Brown Boveri AG Dispositif de réglage d'un appareil de suralimentation à ondes de pression
CH667696A5 (de) * 1985-06-26 1988-10-31 Bbc Brown Boveri & Cie Verbrennungsmotor mit einem druckwellenlader.
DE3762535D1 (de) * 1986-02-28 1990-06-07 Bbc Brown Boveri & Cie Durch die gaskraefte angetriebener, freilaufender druckwellenlader.
US4928640A (en) * 1989-07-20 1990-05-29 Siemens-Bendix Automotive Electronics L.P. Autocalibration of camshaft phasing feedback in a variable valve timing system
US5172659A (en) * 1989-10-16 1992-12-22 Borg-Warner Automotive Transmission & Engine Components Corporation Differential pressure control system for variable camshaft timing system
US5361735A (en) * 1989-10-16 1994-11-08 Borg-Warner Automotive Transmission & Engine Components Corporation Belt driven variable camshaft timing system
US5002023A (en) * 1989-10-16 1991-03-26 Borg-Warner Automotive, Inc. Variable camshaft timing for internal combustion engine
US5107804A (en) * 1989-10-16 1992-04-28 Borg-Warner Automotive Transmission & Engine Components Corporation Variable camshaft timing for internal combustion engine
JP3089689B2 (ja) * 1991-03-20 2000-09-18 スズキ株式会社 シリンダヘッドのオイル通路構造
US5196793A (en) * 1991-07-24 1993-03-23 Delco Electronics Corporation Crankshaft position voltage developing apparatus having a voltage clamp
FR2681425B1 (fr) * 1991-09-12 1993-11-26 Renault Regie Nale Usines Procede et dispositif de mesure du couple d'un moteur thermique a combustion interne.
US5289805A (en) * 1992-03-05 1994-03-01 Borg-Warner Automotive Transmission & Engine Components Corporation Self-calibrating variable camshaft timing system
US5497738A (en) * 1992-09-03 1996-03-12 Borg-Warner Automotive, Inc. VCT control with a direct electromechanical actuator
US6089211A (en) 1996-03-05 2000-07-18 Swissauto Engineering S.A. Spark ignition engine with pressure-wave supercharger
EP1203872A1 (fr) * 2000-11-01 2002-05-08 BorgWarner Inc. Turbocompresseur à soupape de dérivation pouvant être commandée de façon à promouvoir l'activation rapide d'un convertisseur catalytique

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4488532A (en) * 1981-11-30 1984-12-18 Bbc Brown, Boveri & Company, Limited Gas-dynamic pressure wave machine with exhaust gas bypass
EP0210328A1 (fr) 1985-04-30 1987-02-04 BBC Brown Boveri AG Turbochargeur pour un moteur à combustion interne avec un dispositif de commande de l'écoulement du gaz d'échappement à haute pression
CH681738A5 (fr) 1989-11-16 1993-05-14 Comprex Ag
WO1999011914A1 (fr) 1997-08-29 1999-03-11 Swissauto Engineering S.A. Machine a ondes de pression gazodynamique
WO1999011194A1 (fr) 1997-09-05 1999-03-11 Funt Lawrence A Systeme reservoir medical

Also Published As

Publication number Publication date
EP1347157B1 (fr) 2005-11-09
ATE309455T1 (de) 2005-11-15
AU2003200866A1 (en) 2003-10-02
US20030226353A1 (en) 2003-12-11
ES2252338T3 (es) 2006-05-16
DE50204848D1 (de) 2005-12-15
JP2004003451A (ja) 2004-01-08
US7080633B2 (en) 2006-07-25
JP4335558B2 (ja) 2009-09-30

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