EP0326663B1 - Machine à vis contrôlée par tiroir et moteur à combustion interne suralimenté qui en est muni - Google Patents

Machine à vis contrôlée par tiroir et moteur à combustion interne suralimenté qui en est muni Download PDF

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Publication number
EP0326663B1
EP0326663B1 EP88118719A EP88118719A EP0326663B1 EP 0326663 B1 EP0326663 B1 EP 0326663B1 EP 88118719 A EP88118719 A EP 88118719A EP 88118719 A EP88118719 A EP 88118719A EP 0326663 B1 EP0326663 B1 EP 0326663B1
Authority
EP
European Patent Office
Prior art keywords
slide
screw
operating space
connecting piece
low pressure
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.)
Expired - Lifetime
Application number
EP88118719A
Other languages
German (de)
English (en)
Other versions
EP0326663A2 (fr
EP0326663A3 (en
Inventor
Peter Dr.-Ing. Buthmann
Arno Dipl.-Ing. Heinz
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.)
MAN Gutehoffnungshutte GmbH
Original Assignee
MAN Gutehoffnungshutte GmbH
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 MAN Gutehoffnungshutte GmbH filed Critical MAN Gutehoffnungshutte GmbH
Publication of EP0326663A2 publication Critical patent/EP0326663A2/fr
Publication of EP0326663A3 publication Critical patent/EP0326663A3/de
Application granted granted Critical
Publication of EP0326663B1 publication Critical patent/EP0326663B1/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
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/10—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
    • F04C28/12—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using sliding valves
    • F04C28/125—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using sliding valves with sliding valves controlled by the use of fluid other than the working fluid
    • 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
    • F02B33/34—Engines with pumps other than of reciprocating-piston type with rotary pumps
    • F02B33/36—Engines with pumps other than of reciprocating-piston type with rotary pumps of positive-displacement type
    • 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
    • F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
    • F02B39/16—Other safety measures for, or other control of, pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00

Definitions

  • the invention relates to a supercharged internal combustion engine with a compressor arranged in the intake path, the compressor being designed as a screw rotor machine, in particular for use as a supercharger in an internal combustion engine, the screw rotor machine having at least two screw rotors which engage with one another with their screw ribs and grooves and which run in the axially parallel manner and penetrating cylinder bores formed and bounded by end walls are arranged in the working space of a housing, the housing each having a low-pressure nozzle and a high-pressure nozzle opening into the working space and a slide which is displaceably mounted parallel to the rotor axes and which part of the circumferential wall of the working space on the one assigned to the low-pressure nozzle Page forms and depending on its position the flow path from the low-pressure nozzle in the work space more or less free.
  • Compressors of various types are suitable for charging, ie for the pre-compression of the combustion air in an internal combustion engine, including screw rotor machines (hereinafter referred to as screw compressors).
  • screw compressors are not suitable for use as a supercharger, since there are some disadvantages: If the combustion air of the engine is led through the supercharger in throttle and compression mode, the supercharger power must be taken from the engine crankshaft in both operating modes. In throttled operation, the pressure in front of the charger must also be reduced in accordance with the built-in pressure ratio of the charger in order to be able to provide the required suction pressure of the engine after the charger. This reduction in pressure leads to a relatively high power loss, which must be applied by the motor.
  • the charger is e.g. bypassed and only switched on in compression mode via a clutch, which requires considerable control and construction work, there is a sudden increase in torque of the engine when the charger is switched on.
  • a slide-controlled screw rotor machine is known from DE-B-1 293 384 and FR-A-1 258 650.
  • the time at which the compressor cells enclosed by the interlocking rotors and the housing wall separate from the low-pressure inlet can be changed, as a result of which the throughput of the machine or the nominal pressure ratio can be changed.
  • the intake cross section of the screw rotor machine can only be changed, but not completely closed. Using such a machine as a supercharger for an internal combustion engine would therefore still be a Additional throttle device for changing the intake quantity of the internal combustion engine, for example the usual throttle valve, is required.
  • a turbocharged internal combustion engine with a compressor arranged in the intake path is known from WO 87/02 417 A1.
  • the compressor is designed as a screw rotor machine and has a slide on its suction side through which the suction cross section of the screw rotor machine can be closed and released in a controlled manner.
  • the compressor according to this document does not disclose rotors with symmetrical profile shapes, but the rotors have asymmetrical profiles.
  • the slide hits the wall when it closes. When opening, there is a sudden increase in the amount of air.
  • Modern screw compressors including the one in the above Compressor described, are generally equipped with asymmetrical rotor profiles.
  • the transitions of the tooth flanks to the tip circle on one side of the profile tooth are formed by sharp edges or very small radii.
  • the cycloidal shape of the tooth flank means that the so-called blow hole formed by the tooth heads and the pressure-side cut edge of the main housing bores can be kept very small. Efficiency-reducing leakages from tooth gaps of higher pressure to tooth gaps of lower pressure can be largely avoided in this way during the compression phase.
  • the other side of the profile teeth can be provided with large roundings in the area of the tooth heads in the sense of good manufacturability, since these are in the area of engage the second housing cut edge, where the same pressure (suction pressure) prevails in all tooth gaps. Leakages can therefore not occur here.
  • the essence of the invention is the teaching to use a symmetrical screw rotor profile, i.e. a screw rotor profile in which the leading and trailing ones are used in a slide provided on the suction side of a screw compressor instead of a throttle valve of conventional suction motors for the purpose of recovering drive energy and to improve the machine efficiency Profile edges and heads are built according to the same principles.
  • a symmetrical screw rotor profile i.e. a screw rotor profile in which the leading and trailing ones are used in a slide provided on the suction side of a screw compressor instead of a throttle valve of conventional suction motors for the purpose of recovering drive energy and to improve the machine efficiency
  • Profile edges and heads are built according to the same principles.
  • the screw rotor machine 1 shown in FIGS. 1 to 3 has a screw rib rotor or main rotor 2 and a screw groove rotor or secondary rotor 3, which are arranged axially parallel and intermeshing in the working space of a housing 13 formed by two intersecting circular cylinders.
  • the main rotor 2 is driven, and the drive is transmitted to the secondary rotor 3 via the synchronizing gears 10 and 9.
  • the secondary rotor 3 it is also possible to drive the secondary rotor 3, and furthermore the synchronizing gear 10, 9 can be omitted and the drive can be transferred directly from one rotor to the other via the intermeshing rotor flanks.
  • the suction port 7 and the pressure port 8 on the other side of the housing open into the working area of the housing 13.
  • the working area of the housing is at the end assigned to the suction port through the low-pressure-side working area end wall 12 and the end assigned to the pressure port 8 is closed off by the high-pressure side work space end wall 11.
  • the peripheral wall of the working space in the intersection area of the two circular cylinders is formed by an axially displaceably guided slide 4.
  • the connection of the suction nozzle 7 to the working space of the housing 13 can be completely closed or more or less released by axially adjusting the slide 4.
  • the slide 4 On its front face lying in the closing direction at the front, the slide 4 has a dovetail-like contour, which is indicated by the line 4a in FIG. 2a, and which is adapted to the course of the helical head or ridge lines of two intermeshing main and secondary rotor ribs in the region of the slide opening is.
  • the slider 4 must be able to be moved beyond the low-pressure side end wall 12 of the working area until the opening between the suction port 7 created by the frontal gusset of the slider 4 and work space is closed. 2, the position of the end face of the slide 4 is indicated by the broken line 4b when the position is completely closed.
  • the low pressure side The end wall 12 of the working space must therefore have a recess or pocket which allows the complete closing movement of the slide 4, while the opening movement of the slide is made possible by a corresponding recess in the high-pressure side end wall 11.
  • the slide 4 is automatically pressed into its closed position by a coil spring 5 arranged in its interior. It can be counter to the force of the spring 5 by a pulling device 6, e.g. a Bowden cable, are moved in the opening direction to release the connection of the suction nozzle 7 to the work space more or less, possibly up to the full maximum value.
  • a pulling device 6 e.g. a Bowden cable
  • Fig. 4 shows schematically the arrangement of a screw rotor machine 1 as a loader in the air intake system leading from the air filter 17 to the cylinder chambers of, for example, a four-cylinder internal combustion engine 20.
  • the suction line of the charger 1 coming from the air filter 17 is designated by 18, and the suction line to the internal combustion engine 20 which is acted upon by this is indicated by 19.
  • the loader 1 is driven by the crankshaft of the engine 20 via, for example, a belt drive 22. 23 is the exhaust pipe of the internal combustion engine.
  • the slide 4 of the loader 1 is controlled via the pulling device 6 by the accelerator pedal 21 of the internal combustion engine 20.
  • the work taken up by the compression corresponds to the area hatched in FIG. 6.
  • the work recovered by the regulated screw loader thus corresponds to the area between points A-B-C-D in the p-V diagram in Fig. 6.
  • the independent closing of the slide 4 when the pulling device 6 is relieved can be achieved according to the schematic illustration in FIG. 7 and the constructive embodiment in FIG. 1 by one or more springs 5 which act against the pulling device 6, e.g. can be designed as a Bowden cable, work.
  • a hydraulic return system according to the schematic representation in Fig. 8 can also be used, the slide return e.g. by increasing the pressure of the oil in the slide.
  • the pulling device can also be omitted if the slide 4 can be moved in both directions (opening or closing) via the electric motor, which is regulated, for example, as a function of the accelerator pedal position of a vehicle.
  • the torque between the main rotor 2 and the secondary rotor 3 can be transmitted either via the synchronization gear 9, 10 or via the profile area of the rotors of the screw loader in order to achieve a shorter construction.
  • the internal combustion engine 20 shown schematically in FIG. 4 is preferably a diesel engine or a gasoline engine with injection, so that the charger 1 compresses only the intake air.
  • the screw compressor designed according to the invention to use as a supercharger in a carburetor engine in such a way that it pre-compresses the mixture coming from the carburetor.
  • the supercharger 1 is continuously driven by the crankshaft of the engine 20 via the transmission 22.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Supercharger (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)

Claims (2)

  1. Moteur à combustion interne suralimenté (20) avec un compresseur disposé sur le trajet d'aspiration, ce compresseur étant réalisé sous la forme d'une machine à rotor à vis (1), cette machine à rotor à vis (1) étant équipée d'au moins deux retors à vis (2, 3) dont les nervures et les rainures s'engrenent les unes dans les autres, et qui sont disposés dans la chambre de travail d'un carter (13), chambre constituée par des alésages cylindriques s'interpénétrant et dont les axes sont parallèles et délimitée par des parois frontales (11, 12), tandis que le carter (13) comporte respectivement une tubulure basse pression (7) et une tubulure haute pression (8) débouchant dans la chambre de travail, ainsi qu'un tiroir (4) monté de façon à pouvoir se déplacer parallèlement aux axes des rotors, ce tiroir constituant une partie de la paroi périphérique de la chambre de travail sur le côté associé à la tubulure basse pression (7) et libérant plus ou moins selon sa position le trajet d'écoulement à partir de la tubulure basse pression (7) dans la chambre de travail,
       Moteur à combustion interne, caractérisé en ce que les rotors à vis (2, 3) engrenant les uns dans les autres, comportent respectivement des formes de profil respectivement symétriques avec les flancs avant et arrière réalisés de façon identique, en ce que le tiroir (4) constitue l'organe d'étranglement commandant l'aspiration du moteur (20), et est susceptible d'être actionné par la pédale d'accélérateur (21) ou un organe de commande analogue de la puissance du moteur (20), et en ce que la communication entre la tubulure basse pression (7) et la chambre de travail, peut être fermée complètement par le tiroir (4), en ce que le tiroir (4) a sur sa face frontale placée en avant dans la direction de fermeture un contour (4a), qui correspond au tracé des lignes de tête des dents de rotor engrenant les unes dans les autres au voisinage de l'ouverture du tiroir, et en ce que le tiroir (4), grâce à un évidement dans la paroi frontale (12) côté basse pression peut être déplacé vers l'extérieur suffisamment loin au delà de celle-ci pour que l'ouverture formée par le coin du contour du tiroir entre la tubulure basse pression (7) et la chambre de travail soit fermée.
  2. Machine à rotor à vis selon la revendication 1, caractérisée en ce que le tiroir (4) est maintenu dans sa position de fermeture par un dispositif de rappel (5) et est susceptible d'être déplacé dans le sens de l'ouverture contre l'effort de rappel au moyen d'un dispositif de réglage (6).
EP88118719A 1988-02-02 1988-11-10 Machine à vis contrôlée par tiroir et moteur à combustion interne suralimenté qui en est muni Expired - Lifetime EP0326663B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3803044A DE3803044A1 (de) 1988-02-02 1988-02-02 Schiebergeregelte schraubenrotormaschine und damit ausgeruesteter aufgeladener verbrennungsmotor
DE3803044 1988-02-02

Publications (3)

Publication Number Publication Date
EP0326663A2 EP0326663A2 (fr) 1989-08-09
EP0326663A3 EP0326663A3 (en) 1990-03-14
EP0326663B1 true EP0326663B1 (fr) 1992-10-21

Family

ID=6346453

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88118719A Expired - Lifetime EP0326663B1 (fr) 1988-02-02 1988-11-10 Machine à vis contrôlée par tiroir et moteur à combustion interne suralimenté qui en est muni

Country Status (5)

Country Link
EP (1) EP0326663B1 (fr)
JP (1) JPH0654092B2 (fr)
KR (1) KR930005961B1 (fr)
DE (2) DE3803044A1 (fr)
ES (1) ES2035220T3 (fr)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2524257B2 (ja) * 1990-11-06 1996-08-14 本田技研工業株式会社 内燃機関における過給圧制御方法
JPH0669993U (ja) * 1993-03-09 1994-09-30 清 秋生 玩具笛
SE501252C2 (sv) * 1993-04-21 1994-12-19 Opcon Autorotor Ab Överladdad förbränningsmotor
GB9912645D0 (en) * 1999-05-28 1999-07-28 Seneca Tech Ltd Super-charger for i.c. engine
JP2007085174A (ja) * 2004-01-08 2007-04-05 Koichi Hatamura 容積型圧縮機およびそれを用いた過給機
US8539769B2 (en) * 2009-10-14 2013-09-24 Craig N. Hansen Internal combustion engine and supercharger
US8813492B2 (en) * 2009-10-14 2014-08-26 Hansen Engine Corporation Internal combustion engine and supercharger
DE102015007552A1 (de) 2015-06-16 2016-12-22 Man Diesel & Turbo Se Schraubenmaschine und Verfahren zum Betreiben derselben
DE102021134652B3 (de) 2021-12-23 2023-05-11 Man Energy Solutions Se Schraubenkompressor

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB959831A (en) * 1959-06-04 1964-06-03 Svenska Rotor Maskiner Ab Improvements in or relating to screw rotor machines
FR1258650A (fr) * 1960-06-01 1961-04-14 Svenska Rotor Maskiner Ab Curseurs à déplacement axial pour machines à rotors hélicoïdaux
DE8415188U1 (de) * 1984-05-18 1985-08-22 Pierburg Gmbh & Co Kg, 4040 Neuss Vorrichtung zum Steuern der Einlaßöffnung eines Drehflügel- oder Flügelzellenverdichters
SE450511B (sv) * 1985-10-14 1987-06-29 Svenska Rotor Maskiner Ab Anordning vid en strypreglerad forbrenningsmotor med en overladdare

Also Published As

Publication number Publication date
DE3803044A1 (de) 1989-08-10
EP0326663A2 (fr) 1989-08-09
JPH0654092B2 (ja) 1994-07-20
KR890013321A (ko) 1989-09-22
DE3875471D1 (de) 1992-11-26
EP0326663A3 (en) 1990-03-14
ES2035220T3 (es) 1993-04-16
KR930005961B1 (ko) 1993-06-30
JPH01310119A (ja) 1989-12-14

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