EP0051327A1 - Machine à ondes de pression à dynamique des gaz pour la suralimentation des moteurs à combustion interne - Google Patents

Machine à ondes de pression à dynamique des gaz pour la suralimentation des moteurs à combustion interne Download PDF

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Publication number
EP0051327A1
EP0051327A1 EP81201139A EP81201139A EP0051327A1 EP 0051327 A1 EP0051327 A1 EP 0051327A1 EP 81201139 A EP81201139 A EP 81201139A EP 81201139 A EP81201139 A EP 81201139A EP 0051327 A1 EP0051327 A1 EP 0051327A1
Authority
EP
European Patent Office
Prior art keywords
rotor
housing
gas
pressure wave
wave machine
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
EP81201139A
Other languages
German (de)
English (en)
Other versions
EP0051327B1 (fr
Inventor
Andreas Dipl.-Ing. Mayer
Werner Dr. Dipl.-Ing. Haase
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.)
BBC Brown Boveri AG Switzerland
Original Assignee
BBC Brown Boveri AG Switzerland
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 BBC Brown Boveri AG Switzerland filed Critical BBC Brown Boveri AG Switzerland
Priority to AT81201139T priority Critical patent/ATE13581T1/de
Publication of EP0051327A1 publication Critical patent/EP0051327A1/fr
Application granted granted Critical
Publication of EP0051327B1 publication Critical patent/EP0051327B1/fr
Expired 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
    • 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
    • F02B1/00—Engines characterised by fuel-air mixture compression
    • F02B1/02—Engines characterised by fuel-air mixture compression with positive ignition
    • F02B1/04—Engines characterised by fuel-air mixture compression with positive ignition with fuel-air mixture admission into cylinder

Definitions

  • the present invention relates to a pressure wave machine for charging internal combustion engines according to the preamble of claim 1.
  • One of the measures with which one strives to improve the efficiency of pressure wave machines is to reduce the play between the end faces of the rotor body and the gas housing or the air housing. In order to keep the leakage losses as low as possible, efforts are made to keep these games as small as possible, while keeping them as constant as possible throughout the operating area.
  • the wall thickness of the rotor housing is made as thin as possible, so that it heats up or cools down rapidly during load changes and is therefore able to follow the rapid changes in length and diameter of the rotor sufficiently quickly.
  • Small wall thicknesses of the rotor housing mean greater heat losses and therefore a we loss of efficiency.
  • the present invention defined in the characterizing part of patent claim 1, arose from the object of finding a design for the rotor and the rotor housing of a pressure wave machine in which the disadvantages described above are avoided, ie in which in all operating states and especially in the case of load changes for the aforementioned games between the rotor end faces and the end faces of the gas or air housing are maintained at consistently small values, in order to avoid flushing losses or rubbing, and in which, thanks to higher thermal resilience, better efficiency can be achieved and better acceleration capability is achieved.
  • the gas housing for supplying and discharging the exhaust gases of the engine into and from the rotor 1 with 2 and the air housing for sucking in the combustion air and supplying the compressed charge air into the engine with 3 designated.
  • the rotor 1 is mounted with its rotor shaft 4 overhung in the air housing 3. Outside of the same sits a V-belt pulley 5 at the shaft end for the positive drive of the rotor 1 by the motor.
  • the rotor 1, like the rotor housing 6 surrounding it, is made of ceramic material, for example of reaction-sintered silicon nitride ceramic or silicon carbide, which is fired in a known manner after pressing, casting or extruding and drying the green body, that is to say the raw, unfired molded body, and a chemical hardening process is subjected.
  • this housing 6 made of ceramic has the problem because of the different thermal expansion coefficients of the housing material and the metallic connecting elements with which the housing 6 is connected to the gas housing 2 and air housing 3 made of metal. to design these connecting elements in such a way that inadmissibly high thermal stresses, in particular tensile stresses in the ceramic, as a result of expansion differences are avoided with certainty.
  • these connecting means consist of expansion stud bolts 7 distributed over the circumference at equal distances, which have threads at both ends and are provided at the screw-in end with a collar 8 with key surfaces for tightening and tensioning against the gas housing 2.
  • expansion stud bolts 7 distributed over the circumference at equal distances, which have threads at both ends and are provided at the screw-in end with a collar 8 with key surfaces for tightening and tensioning against the gas housing 2.
  • the rotor housing 6 consists of a simple circular cylindrical jacket with the longitudinal bores for the expansion pin screws 7. The production of such a jacket made of ceramic presents no difficulties. In the case of series production, even economical extrusion could be considered.
  • ductile metallic sealing rings 11 are provided, which allow an 'unimpeded radial displacement of the sealing ring surfaces against the metallic seat of the gas or air housing.
  • a ductile metal layer can also be sprayed onto the end faces of the ceramic rotor housing 6. In order to facilitate their mutual radial movement, these seats could be treated with a lubricant. Harmful tensions due to different radial expansions of the metallic gas or air housing compared to the ceramic rotor housing can thereby be avoided.
  • a ceramic rotor housing 12 is even simpler in the embodiment according to FIG. 3.
  • This rotor housing is formed by a simple circular cylindrical tube.
  • a two-part clamping collar 13 is used, the two parts of which are contracted in the longitudinal direction with screws and flanges 14 indicated by their center lines.
  • the two halves of the clamping sleeve are provided with flexible peripheral beads 15, which prevents the occurrence of inadmissible longitudinal stresses.
  • the two halves of the clamping sleeve are also divided lengthways. The two edges of the parting line are in a known, not shown manner, e.g. connected by screws or straps.
  • the clamping sleeves 13 and 16 simultaneously form a protection for the shock-sensitive ceramic rotor housing.
  • a variant of this seal shown in FIG. 7 has a compensating ring 48, part of which is shown in FIG. 8. Its circumference is divided on the side facing the rotor housing 6 by a series of slots 49 into elastic tabs 50, which allow easy radial displacement between the gas or air housing and the rotor housing. This easy mobility is also ensured by the fact that the ring acts as a spacer ring between the forehead surfaces of the housing and the air or gas housing leaves a gap 51. This eliminates any end face friction.
  • FIGS. 9 and 10 An embodiment of a two-flow ceramic rotor 20, which can be paired with a ceramic rotor housing, is shown in FIGS. 9 and 10 in an axial section or in a side view, only a few of the channels being shown in the latter for the sake of simplicity.
  • the flooding and the hub are made in one piece.
  • the hub can be designed with a web 21 and have holes 22. The connection of the hub to the shaft is dealt with in the rotor designs according to FIGS. 11-17.
  • the hubs are manufactured separately from the rotor body, which here is double-flow in all cases, and are connected to the latter in a ceramic manner, so that these rotor bodies can be mass-produced economically by extrusion.
  • the rotor hub 25 is inserted without a stop into the bore of the rotor body 24 of the same size throughout.
  • the connecting joint is designated 26.
  • connection of the metallic shaft 52 to the rotor body always takes place from the point of view that significant tensile stresses are to be avoided in the ceramic components.
  • an expansion screw 53 screwed into the shaft 52 is provided and a centering ring 54 formed at the shaft end by a recess serves to center the shaft relative to the rotor.
  • An adjusting disk 55 within the centering ring 54 is used to adjust the exact axial position of the rotor body 24 with respect to the inner end faces of the gas and air housing and thus the axial running play of the rotor relative to these end faces from case to case by appropriate dimensioning of their thickness.
  • the centering ring 54 provides the centering of the rotor hub 25 with respect to the shaft 52 in cooperation with an outer surface 56 of the hub 25 which is ground concentrically with respect to the outside diameter of the rotor body 24.
  • a nut 57 with a washer 58 are used for axially fixing the rotor body.
  • a commercially available so-called “tolerance ring” 62 which is shown on a larger scale in FIG. 13, serves to center the hub 59 on a centering pin 60 of the shaft 61.
  • This tolerance ring has axially parallel, radially flexible longitudinal beads, the entirety of which forms a wavy cross section as shown in FIG. 13.
  • the circumscribed and inscribed circle of this cross section have a slight oversize or undersize compared to the hub bore or the shaft.
  • the inner and outer crests of the beads deform during installation and result in a weak centering press fit which only slightly pulls the ceramic material of the hub in accordance with the requirement mentioned above.
  • an adjusting disk 55, a nut 57 and a disk 58 are used to adjust the lateral running play of the rotor and to fix it axially on the shaft.
  • connection of the shaft 27 to the rotor 23 takes place by means of an expansion screw 28 screwed into the shaft, a centering pin 29 provided at the shaft end, a pair of disks 30, 31 with cooperating concave or convex spherical surfaces; and a nut 32.
  • an adjusting washer may also be required.
  • the centering of the shaft 27 relative to the hub 33 takes place here by means of a long centering pin 35 with play relative to the bore of the hub 33 and a disk 36 with an inner cone, which sits on the centering pin 35 without play and by a nut 37 against a frustoconical shoulder 38 of the hub 33 is tensioned.
  • the hub 33 can be provided with holes 39 or other cutouts.
  • the hub is centered relative to the shaft by a short centering pin 42 and braced by an expansion screw 43, a plane-parallel disk 44 and a nut 45.
  • adjusting disks may also be required in these latter two versions.
  • the mass moment of inertia and thus the transient torques of the ceramic rotor are smaller in the same ratio. This improves the engine's ability to accelerate.
  • Belt tension and slippage i.e. the belt load and the bearing load on the pressure wave machine, are correspondingly lower.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Supercharger (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
  • Ceramic Products (AREA)
EP81201139A 1980-11-04 1981-10-13 Machine à ondes de pression à dynamique des gaz pour la suralimentation des moteurs à combustion interne Expired EP0051327B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT81201139T ATE13581T1 (de) 1980-11-04 1981-10-13 Druckwellenmaschine zur aufladung von verbrennungsmotoren.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH818880 1980-11-04
CH8188/80 1980-11-04

Publications (2)

Publication Number Publication Date
EP0051327A1 true EP0051327A1 (fr) 1982-05-12
EP0051327B1 EP0051327B1 (fr) 1985-05-29

Family

ID=4336514

Family Applications (1)

Application Number Title Priority Date Filing Date
EP81201139A Expired EP0051327B1 (fr) 1980-11-04 1981-10-13 Machine à ondes de pression à dynamique des gaz pour la suralimentation des moteurs à combustion interne

Country Status (6)

Country Link
US (1) US4487552A (fr)
EP (1) EP0051327B1 (fr)
JP (1) JPS57108410A (fr)
AT (1) ATE13581T1 (fr)
CA (1) CA1229832A (fr)
DE (1) DE3170745D1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0285362A2 (fr) * 1987-03-31 1988-10-05 Ngk Insulators, Ltd. Rotors en céramique pour turbochargeur à ondes de pression et sa production
DE3830058A1 (de) * 1987-10-02 1989-02-02 Bbc Brown Boveri & Cie Druckwellenlader

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE8701379U1 (de) * 1987-01-29 1988-06-01 Carl Schenck Ag, 6100 Darmstadt Halterung zum Halten eines Rotors
NO180599C (no) * 1994-11-28 1997-05-14 Leif J Hauge Trykkveksler
KR100833063B1 (ko) 2007-05-15 2008-05-27 현대중공업 주식회사 선박용 엔진의 체결 장치
DE102009023217B4 (de) * 2009-05-29 2014-08-28 Benteler Automobiltechnik Gmbh Gebaute Nabe für einen Druckwellenlader
DE102012101922B4 (de) * 2012-03-07 2015-05-07 Benteler Automobiltechnik Gmbh Druckwellenlader mit Schiebesitz
EP2672123B1 (fr) * 2012-06-07 2017-08-16 MEC Lasertec AG Roue cellulaire, en particulier pour un système de suralimentation à ondes de pression

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB867719A (en) * 1958-07-24 1961-05-10 Power Jets Res & Dev Ltd Improvements in or relating to pressure exchangers
GB871316A (en) * 1958-11-25 1961-06-28 Power Jets Res & Dev Ltd Improvements in and relating to pressure exchangers
US3086697A (en) * 1958-05-12 1963-04-23 Ite Circuit Breaker Ltd Rotor design for aero-dynamic wave machine
US3362620A (en) * 1965-07-13 1968-01-09 Power Jets Res & Dev Ltd Rotor
US3450334A (en) * 1966-06-28 1969-06-17 Power Jets Res & Dev Ltd Pressure exchangers
DE3014518A1 (de) * 1979-04-23 1980-10-30 Ford Werke Ag Turbolader

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3055577A (en) * 1958-11-25 1962-09-25 Power Jets Res & Dev Ltd Pressure exchanger cell-ring having energy conversion means
CH406739A (de) * 1963-08-14 1966-01-31 Bbc Brown Boveri & Cie Druckwellenmaschine
CH568476A5 (fr) * 1974-02-14 1975-10-31 Bbc Brown Boveri & Cie
US3905713A (en) * 1974-02-28 1975-09-16 Ingersoll Rand Co Tie bolt sealing means
US4207807A (en) * 1975-09-04 1980-06-17 Oiles Industry Co., Ltd. Plastic air cylinder assembly
DE2728823C2 (de) * 1977-06-27 1982-09-09 Aktiengesellschaft Kühnle, Kopp & Kausch, 6710 Frankenthal Gasturbine
JPS55107120A (en) * 1979-02-08 1980-08-16 Toyota Motor Corp Coupling mechanism for rotary body
JPS55107003A (en) * 1979-02-13 1980-08-16 Nissan Motor Co Ltd Radial turbine rotor
US4269570A (en) * 1979-04-23 1981-05-26 Ford Motor Company Elastomeric mounting for wave compressor supercharger

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3086697A (en) * 1958-05-12 1963-04-23 Ite Circuit Breaker Ltd Rotor design for aero-dynamic wave machine
GB867719A (en) * 1958-07-24 1961-05-10 Power Jets Res & Dev Ltd Improvements in or relating to pressure exchangers
GB871316A (en) * 1958-11-25 1961-06-28 Power Jets Res & Dev Ltd Improvements in and relating to pressure exchangers
US3362620A (en) * 1965-07-13 1968-01-09 Power Jets Res & Dev Ltd Rotor
US3450334A (en) * 1966-06-28 1969-06-17 Power Jets Res & Dev Ltd Pressure exchangers
DE3014518A1 (de) * 1979-04-23 1980-10-30 Ford Werke Ag Turbolader

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0285362A2 (fr) * 1987-03-31 1988-10-05 Ngk Insulators, Ltd. Rotors en céramique pour turbochargeur à ondes de pression et sa production
EP0285362A3 (en) * 1987-03-31 1989-05-10 Ngk Insulators, Ltd. Ceramic rotors for pressure wave type superchargers and production thereof
DE3830058A1 (de) * 1987-10-02 1989-02-02 Bbc Brown Boveri & Cie Druckwellenlader

Also Published As

Publication number Publication date
US4487552A (en) 1984-12-11
ATE13581T1 (de) 1985-06-15
CA1229832A (fr) 1987-12-01
JPS57108410A (en) 1982-07-06
JPH0123653B2 (fr) 1989-05-08
DE3170745D1 (en) 1985-07-04
EP0051327B1 (fr) 1985-05-29

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