WO2012048785A1 - Machine à onde de pression, en particulier compresseur à onde de pression, pour un moteur à combustion interne, et moteur à combustion interne - Google Patents

Machine à onde de pression, en particulier compresseur à onde de pression, pour un moteur à combustion interne, et moteur à combustion interne Download PDF

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Publication number
WO2012048785A1
WO2012048785A1 PCT/EP2011/004691 EP2011004691W WO2012048785A1 WO 2012048785 A1 WO2012048785 A1 WO 2012048785A1 EP 2011004691 W EP2011004691 W EP 2011004691W WO 2012048785 A1 WO2012048785 A1 WO 2012048785A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure wave
channel
exhaust gas
wave machine
combustion engine
Prior art date
Application number
PCT/EP2011/004691
Other languages
German (de)
English (en)
Inventor
Benjamin Kraus
Original Assignee
Daimler 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 Daimler Ag filed Critical Daimler Ag
Publication of WO2012048785A1 publication Critical patent/WO2012048785A1/fr

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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

  • Pressure wave machine in particular pressure wave loader, for a
  • the invention relates to a pressure wave machine for an internal combustion engine specified in the preamble of claim 1 and a kind
  • EP 1 347 157 B1 discloses a gas-dynamic pressure wave machine which is intended to supply charge air to an internal combustion engine.
  • the pressure wave machine comprises a rotor having cells, a low pressure fresh air supply duct, a high pressure charge air duct leading to the internal combustion engine, a high pressure exhaust duct coming from the internal combustion engine and a low pressure exhaust duct.
  • the high-pressure exhaust passage and the low-pressure exhaust passage are arranged in a gas housing and the low-pressure fresh-air supply passage and the high-pressure charge air passage in an air housing.
  • the high-pressure exhaust gas channel has an enlargement on the rotor side, from which a bypass line to the
  • Exhaust gas stream is passed from the high-pressure exhaust gas channel in the enlargement before further exhaust gas is passed from the high pressure exhaust passage to the low pressure exhaust passage in the line.
  • the means comprises, without formation of a web to increase this change and wherein the means for changing the magnification are formed such that also the opening width of the bypass line is variable.
  • a pressure wave charger the type mentioned and a
  • the first aspect of the invention relates to a pressure wave machine, in particular a pressure wave supercharger, for an internal combustion engine, having a rotatably mounted rotor and having at least one chamber, with a first channel, via which the chamber exhaust gas of the internal combustion engine can be fed, and with at least one second channel, over which at least the exhaust gas is at least partially dischargeable from the chamber.
  • the second channel is subdivided at least in regions into at least two fluidically separated flows, wherein
  • the first of the floods following the first duct while the rotor is rotating during operation has a smaller angular range of the rotor than the subsequent second of the floods.
  • reaction of unburned hydrocarbons and oxygen is prevented, reduced or retarded, whereby the described negative effects of undesirable pressure and temperature increase due to this reaction are prevented or at least reduced.
  • the oxygen is, for example, in itself during the operation of the
  • Pressure wave loader in the chamber located air, in particular ambient air containing, which to compress by means of the pressure wave machine and the
  • the pressure wave machine comprises, for example, a third channel, via which the chamber, the air, in particular the ambient air to supply, whereby the air is to be compressed by the flowing into the chamber exhaust gas.
  • the pressure wave machine may have a fourth channel, via which the compressed air can be discharged from the chamber and to
  • Pressure wave machine is to compress the air so that pressure energy of the exhaust gas is transferred from this to the air by the two fluids (air and exhaust gas) in the chamber, in particular in a plurality of chambers of the pressure wave machine, called cells, for a very short time be brought into direct contact with each other.
  • the pressure wave machine according to the invention uses the physical effect that the pressure compensation takes place faster than the mixing after the fluids are brought into contact with each other at different pressure.
  • the fluid, in particular the exhaust gas, which is opposite the other fluid, in particular the air is present predominantly after the compression of the air in the chamber and in which optionally a smaller amount of the other fluid, in particular the air, is present, are discharged from or out of the chamber.
  • the discharge of the other fluid from the chamber via the second flood at a lower pressure wherein optionally a particularly small amount of the first fluid, in particular of the exhaust gas, is contained in the second fluid, in particular the air.
  • combustion air ratio ( ⁇ , lambda) which is less than 1, which is a rich mixture. It is likewise possible, for example, for a stoichiometric mixture to be present in the first flow, that is to say for the combustion air ratio to be 1. In the second flood, for example, there is a lean mixture, wherein the combustion air ratio is significantly greater than 1.
  • the pressure wave machine according to the invention thus enables a particularly efficient compression of the air, so that by means of the internal combustion engine and particularly high torque and power can be displayed while achieving a low displacement of the internal combustion engine.
  • the pressure wave machine according to the invention makes it possible to design the internal combustion engine according to the downsizing principle and thus contributes to the reduction of the
  • Pressure wave machine can be operated in particularly wide power ranges and has an efficient operation, which is particularly robust against otherwise adverse compositions and pressures of the exhaust gas in the second channel.
  • the flow separation of the second channel can be designed such that during the Operating the pressure wave machine from each other are different pressures in the two floods.
  • the exhaust backpressure in one of the floods may be greater than in the other of the floods. This allows the
  • Pressure wave machine is less prone to exhaust back pressure and even at high exhaust back pressures a particularly efficient operation with high
  • Pressure wave machine can be dimensioned very small, so that the
  • Pressure wave machine can be kept small in size and has only a very small space requirement. This leads to the solution and to the avoidance of package problems, in particular in a space-critical area such as a motor compartment of a motor vehicle, in particular a passenger car.
  • the channels in particular at least the first and the second channel, at least partially formed by a housing of the pressure wave machine. This allows the particularly good subdivision of the second channel into the floods, so that the reaction of the oxygen and the
  • a branch device is provided with at least one branch channel fluidically connected to the first channel, via which exhaust gas can be branched off from the first channel and introduced at least partially, in particular directly, into the second channel.
  • the branching device comprises an adjusting device, in particular an actuator, by means of which the amount of the exhaust gas to be branched off and / or the amount of exhaust gas to be introduced into the second duct is variably adjustable.
  • the pressure wave machine can be adapted particularly advantageously to a plurality of different operating points of the internal combustion engine.
  • the compression of the air can be adjusted as needed.
  • Words different degrees of charging of the air can be represented, which
  • the pressure wave machine comprises a bypass device having a bypass channel, wherein exhaust gas can be branched off from the first channel and introduced into the chamber via the bypass channel upstream of the chamber. This allows a part of the enthalpy of the exhaust gas over the
  • the branching device comprises a web, which is arranged for example in a central region of the housing and the housing in the radial direction, wherein the web has a cavity in which a sleeve having at least one slot is rotatably received, by means of which a branched off and / or to be introduced into the second channel amount of the exhaust gas is adjustable.
  • the branching device and thus the entire pressure wave machine have a particularly small space requirement while displaying a very flexible adjustability of the boost pressure, which means a particularly flexible adaptability of the pressure wave machine to a plurality of different operating points of the internal combustion engine.
  • the configuration of the separating element can take into account the rotation of the rotor in a direction of rotation during operation of the pressure wave machine and be adapted thereto.
  • the rotor of the pressure wave machine is for example drivable such that it is coupled, for example via a corresponding drive means with a crankshaft of the internal combustion engine.
  • the drive device may comprise a belt or at least two gear wheels meshing with one another, by means of which or by means of which the rotor can be driven by the crankshaft.
  • a drive device in particular an electric motor, is provided, by means of which the rotor can be driven. This way, the rotor regardless of the crankshaft
  • the pressure wave machine can be adapted particularly flexibly to different operating points and a very high boost pressure can be displayed even at low speeds. Furthermore, thereby the friction loss and thus the burden of
  • Fuel consumption of the internal combustion engine benefits.
  • the second aspect of the invention relates to an internal combustion engine comprising a pressure wave machine according to the invention.
  • Advantageous embodiments of the first aspect of the invention are to be regarded as advantageous embodiments of the second aspect of the invention and vice versa.
  • inventive embodiments of the first aspect of the invention are to be regarded as advantageous embodiments of the second aspect of the invention and vice versa.
  • pressure wave machine described advantages to bear, according to which the internal combustion engine according to the invention has a particularly efficient and fuel-efficient operation over a particularly wide operating point range. Furthermore, particularly high powers and torques due to the charging by the pressure wave machine are possible.
  • Internal combustion engine also has the advantage that the high power and torque at least almost without delay, that is without so-called
  • an exhaust pipe connected to the pressure wave machine and at least partially subdivided into at least two fluidly separated floods, via which exhaust gas from the second channel can be discharged, wherein one of the floods of the exhaust pipe with the first of the Fluids of the second channel fluidly connected and the other of the flows of the exhaust pipe is fluidly connected to the second of the flows of the second channel.
  • the flow separation of the second channel through or in the exhaust piping is at least partially continued, so that the reaction of the unburned hydrocarbons with the
  • Oxygen and thus the unwanted inflammation is further reduced at least.
  • FIG. 1 is a schematic perspective view of a housing part of a
  • Pressure wave supercharger for an internal combustion engine through which discharge ducts is formed, via which at least exhaust gas from the
  • Pressure wave loader can be discharged
  • FIG. 3 a detail of a schematic perspective view of the housing part according to FIG. 2;
  • FIG. 4 is a schematic perspective view of an exhaust pipe to be connected to the housing part according to FIGS. 2 and 3;
  • FIG. 5 shows a detail of a further schematic perspective view of FIG
  • FIG. 6 shows a detail of a schematic and developed sectional view of a
  • Pressure wave charger with an embodiment of the housing part according to FIGS. 2 and 3.
  • Fig. 1 shows a housing part 10 of a pressure wave supercharger for a
  • the exhaust gas which is under a relatively high pressure, can flow in via the supply channels 2 and 14 into the cells in the axial direction of the pressure wave charger according to a directional arrow 18.
  • the cells of the rotor 16 can also flow via corresponding feed channels air in the axial direction of the pressure wave supercharger according to a direction arrow 20.
  • the directional arrows 18 and 20 can be seen, while the exhaust gas flows in the opposite direction in the cells as the air.
  • the pressure energy of the exhaust gas is transferred to the air by bringing the exhaust gas and the air in the cells into direct contact with each other for a very short time. It uses the
  • Pressure wave superchargers the physical principle that the pressure equalization between the exhaust gas and the air takes place faster than the mixing, after the exhaust gas and the air are brought into contact with different pressure. This represents the so-called pressure wave process.
  • Abbrekanälen 24 and 26 comes.
  • the exhaust gas is so the cells in particular a small amount of the air contained in the cells can be discharged.
  • the exhaust gas and the air for example, be feasible to an exhaust pipe and discharged from the pressure wave supercharger 10.
  • the pressure wave loader further comprises a bypass device, which has a bypass channel, by means of which the feed channel 82 with the discharge channels 24th and / or 26 are fluidically connectable or fluidically separable from each other.
  • the bypass device comprises a web 28 formed by the housing part 10, in which the bypass channel is formed at least partially.
  • By-pass channel 28 is a slotted sleeve 30 rotatably mounted. Furthermore, the web 28 has a passage opening 32, via which the exhaust gas from the feed channel 82 can flow directly into the discharge channels 24 and / or 26. Due to the rotatability of the sleeve, a quantity of exhaust gas to be branched off from the feed channel 82 and introduced into the feed channels 24 and / or 26 can be set by rotating the sleeve 30 between a closed position and at least one open position at least partially open the passage opening 32 can be.
  • bypassing which is also referred to as bypassing, can be adjusted how much or how weak the air in the cells of the rotor 16 should be compressed.
  • the already set by the pressure wave supercharger boost pressure that is, the degree of supercharging of the internal combustion engine
  • FIGS. 2 and 3 show a housing part 10 'which is another
  • Embodiment of the housing part 10 of FIG. 1 represents. As can be seen in FIGS. 2 and 3, the discharge channels 24 and 26 are each through a respective one
  • Wall element 42 and 44 divided into two fluidly separated floods 34 and 36 and 38 and 40, respectively.
  • the pressure wave supercharger has a particularly efficient operation in a particularly wide characteristic field.
  • the wall elements 42 and 44 have an arcuate cross-section and are adapted, for example, to the rotation of the rotor 16 in order to achieve an efficient removal of the air and of the exhaust gas as well as an efficient distribution of the mass flow ,
  • the pressure wave loader is more robust with respect to undesirable high exhaust back pressures and also with correspondingly high
  • the housing part 10 'and the housing part 10 have a respective joining flange 46 with four passage openings, which are penetrated by respective screws 48.
  • the exhaust piping 50 has a joining flange 52 with respective passage openings 54, through which the screws 48 can pass through and are countered with corresponding lock nuts.
  • the exhaust piping 50 also has wall elements 56 and 58 corresponding to the wall elements 42 and 44, wherein the cross sections of the wall elements 56 and 58 are at least substantially adapted to the corresponding cross sections of the wall elements 42 and 44 ,
  • the flow separation of the discharge channels 24 and 26 is continued by or in the exhaust piping 50, so that the Exhaust piping 50 respective separate flooding 34 'and 36'
  • the flood 36 ' is fluidly connected to an exhaust pipe 60, the flood 38' with an exhaust pipe 62 and the floods 34 'and 40' with another exhaust pipe 64, wherein the exhaust pipes 60, 62 and 64 merged fluidically at a junction 66 and in a the exhaust pipes 60, 62 and 64 common exhaust pipe 68 open.
  • FIGS. 2 and 3 shows a schematic and developed sectional view of an at least substantially cylindrical pressure wave charger 70 with a housing part 10 ", which is referred to as a gas housing part and an embodiment of the housing part 10 'according to FIGS. 2 and 3 may be.
  • the housing part 0 "has the feed channel 12, via which exhaust gas according to the directional arrow 18 can flow into cells 72 of the rotor 16.
  • the pressure wave charger 70 comprises a further housing part 10 "', which is also referred to as an air housing part.”
  • a discharge channel 74 is formed through the housing part 10 "', via which the air compressed by the exhaust gas according to a
  • Directional arrow 18 'from the cells 72 can be discharged and the internal combustion engine is feasible.
  • the housing part 10 "'comprises a so-called expansion pocket 76.
  • a feed channel 78 is formed, via which the air according to the directional arrow 20 can flow into the cells 72 of the revolver 16.
  • the pressure wave loader 70 comprises a branching device with a branch channel 82 and a so-called gas pocket valve.
  • a branching device with a branch channel 82 and a so-called gas pocket valve.
  • the gas pocket valve which on the one hand reduces the pressure in the feed channel 12 and thus the compression of the air in the discharge channel 74, on the other hand, the pressure in the cells 72 shortly before reaching the discharge channel formed by the housing part 10 "
  • the cells 72 are rinsed particularly well, which means that the exhaust gas and the air, and in particular the exhaust gas, flow particularly well and quickly from the cells 72 via the discharge channel 24 or the floods 34 and 36 according to directional arrows 20 'can flow, so that over the
  • Supply channel 78 new air, which is referred to as fresh gas, can flow.
  • the discharge channel 24 is subdivided into the first flow 34 and the second flow 36 by means of a separating element 80.
  • the cells 72 loaded with exhaust gas first sweep the flood 34 during operation of the pressure wave charger 70, whereupon they sweep over the flood 36.
  • the combustion air ratio ( ⁇ , lambda) is less than 1.
  • Combustion air ratio is significantly greater than 1. Due to this fact, there is no or only to a very limited extent in the flood 36 to a reaction of hydrocarbons and oxygen, so that it is not in the flood 36 as in the flood 34 to undesirable pressure and temperature rises may occur which could adversely affect the efficient operation of the blast loader 70. This means that the negative effects of the undesirable pressure and temperature increases are prevented or at least reduced, so that the pressure wave loader 70 can be operated particularly efficiently in a particularly wide characteristic map. This comes with low fuel consumption and low C0 2 emissions

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

Abstract

L'invention porte sur une machine à onde de pression (70), en particulier sur un compresseur à onde de pression (70), pour un moteur à combustion interne, comprenant un rotor (16) monté rotatif et présentant au moins une chambre (72), un premier canal (12, 14) par l'intermédiaire duquel au moins des gaz d'échappement du moteur à combustion interne peuvent être amenés à la chambre (72), et au moins un deuxième canal (24, 26) par l'intermédiaire duquel les gaz d'échappement peuvent être évacués au moins partiellement de la chambre (72), le deuxième canal (24, 26) étant subdivisé, au moins par endroits, en au moins deux arrivées (34, 36, 38, 40) séparées fluidiquement l'une de l'autre. L'invention porte aussi sur un moteur à combustion interne équipé d'une telle machine à onde de pression, la première des arrivées (34, 36, 38, 40) qui fait immédiatement suite au premier canal (12, 14), lorsque le rotor (16) tourne pendant le fonctionnement, présentant une plus petite plage angulaire du rotor (16) que la deuxième des arrivées (34, 36, 38, 40) qui y fait suite.
PCT/EP2011/004691 2010-10-13 2011-09-20 Machine à onde de pression, en particulier compresseur à onde de pression, pour un moteur à combustion interne, et moteur à combustion interne WO2012048785A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010048345.1 2010-10-13
DE201010048345 DE102010048345A1 (de) 2010-10-13 2010-10-13 Druckwellenmaschine, insbesondere Druckwellenlader für eine Verbrennungskraftmaschine sowie Verbrennungskraftmaschine

Publications (1)

Publication Number Publication Date
WO2012048785A1 true WO2012048785A1 (fr) 2012-04-19

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PCT/EP2011/004691 WO2012048785A1 (fr) 2010-10-13 2011-09-20 Machine à onde de pression, en particulier compresseur à onde de pression, pour un moteur à combustion interne, et moteur à combustion interne

Country Status (2)

Country Link
DE (1) DE102010048345A1 (fr)
WO (1) WO2012048785A1 (fr)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB765732A (en) * 1951-06-25 1957-01-09 Jendrassik Developments Ltd Improvements relating to pressure exchangers
GB802019A (en) * 1955-12-01 1958-09-24 Dudley Brian Spalding Improvements in or relating to pressure exchangers
GB827798A (en) * 1957-08-29 1960-02-10 Dudley Brian Spalding Improvements in or relating to pressure exchangers
EP1347157B1 (fr) 2002-03-18 2005-11-09 Swissauto Engineering S.A. Echangeur de pression dynamique à ondes

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1060085B (de) * 1957-08-29 1959-06-25 Dudley Brian Spalding Druckaustauscher
CH552135A (de) * 1972-11-29 1974-07-31 Bbc Brown Boveri & Cie Verfahren zur verminderung der schadstoffemission von verbrennungsmotoren und einrichtung zur durchfuehrung des verfahrens.
US4488532A (en) * 1981-11-30 1984-12-18 Bbc Brown, Boveri & Company, Limited Gas-dynamic pressure wave machine with exhaust gas bypass
CH681738A5 (fr) * 1989-11-16 1993-05-14 Comprex Ag
AT408785B (de) * 1995-11-30 2002-03-25 Blank Otto Ing Aufladeeinrichtung für die ladeluft einer verbrennungskraftmaschine
FR2879249A1 (fr) * 2004-12-09 2006-06-16 Renault Sas Dispositif de suralimentation et de stratification de gaz d'echappement recycles pour moteur a combustion interne, notamment pour vehicule automobile, et procede associe.

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB765732A (en) * 1951-06-25 1957-01-09 Jendrassik Developments Ltd Improvements relating to pressure exchangers
GB802019A (en) * 1955-12-01 1958-09-24 Dudley Brian Spalding Improvements in or relating to pressure exchangers
GB827798A (en) * 1957-08-29 1960-02-10 Dudley Brian Spalding Improvements in or relating to pressure exchangers
EP1347157B1 (fr) 2002-03-18 2005-11-09 Swissauto Engineering S.A. Echangeur de pression dynamique à ondes

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
MOTORTECHNISCHEN ZEITSCHRIFT (MTZ), AUSGABE MTZ 1212006, pages 946 - 954

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Publication number Publication date
DE102010048345A1 (de) 2012-04-19

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