EP0326663A2 - Slide-controlled screw rotor machine and supercharged internal-combustion engine equipped therewith - Google Patents

Slide-controlled screw rotor machine and supercharged internal-combustion engine equipped therewith Download PDF

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Publication number
EP0326663A2
EP0326663A2 EP88118719A EP88118719A EP0326663A2 EP 0326663 A2 EP0326663 A2 EP 0326663A2 EP 88118719 A EP88118719 A EP 88118719A EP 88118719 A EP88118719 A EP 88118719A EP 0326663 A2 EP0326663 A2 EP 0326663A2
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EP
European Patent Office
Prior art keywords
slide
screw
rotor machine
screw rotor
low
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
EP88118719A
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German (de)
French (fr)
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EP0326663B1 (en
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
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MAN Gutehoffnungshutte GmbH
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Publication of EP0326663A3 publication Critical patent/EP0326663A3/en
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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 invention further relates to a slider-controlled screw rotor machine which can be used in particular for use as a supercharger in an internal combustion engine of the aforementioned type.
  • Screw compressors of various types can be used 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 screw rotor machines
  • Previously known screw compressors are not readily available for use as superchargers suitable because there are some disadvantages:
  • the charger power must be taken from the engine crankshaft in both operating modes.
  • 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.
  • the essence of the invention is the teaching to use the slide provided on the suction side of a screw compressor instead of the throttle valve of conventional suction motors and to actuate it accordingly.
  • 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 transmitted 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. 2.
  • 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. 2.
  • 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 illustration 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 designed according to the invention use pressor 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.

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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)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

A slide-controlled screw rotor machine is used as supercharger in the intake duct of an internal combustion engine, the slide valve controllable by the accelerator pedal or the like exercising the function of a throttle valve and being capable of completely closing the connection between the low pressure pipe and the working chamber of the screw rotor machine or opening this to a greater or lesser extent.

Description

Die Erfindung betrifft einen aufgeladenen Verbrennungs­motor mit im Ansaugweg angeordnetem Kompressor. Die Er­findung bezieht sich ferner auf eine schiebergeregelte Schraubenrotormaschine, die insbesondere zur Verwendung als Auflader bei einem Verbrennungsmotor der vorgenannten Art verwendbar ist.The invention relates to a supercharged internal combustion engine with a compressor arranged in the intake path. The invention further relates to a slider-controlled screw rotor machine which can be used in particular for use as a supercharger in an internal combustion engine of the aforementioned type.

Für die Aufladung, d.h. für die Vorverdichtung der Ver­brennungsluft bei einem Verbrennungsmotor kommen Kompresso­ren der verschiedensten Bauart in Frage, unter anderem auch Schraubenrotormaschinen (im folgenden Schraubenkom­pressor genannt). Bisher bekannte Schraubenkompressoren sind aber zur Verwendung als Auflader nicht ohne weiteres geeignet, da hierbei einige Nachteile auftreten:Compressors of various types can be used 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). Previously known screw compressors are not readily available for use as superchargers suitable because there are some disadvantages:

Wird die Verbrennungsluft des Motors im Drossel - sowie im Kompressionsbetrieb durch den Lader geführt, muß bei beiden Betriebsarten die Laderleistung der Kurbelwelle des Motors entnommen werden. Im gedrossel­ten Betrieb muß darüber hinaus der Druck vor dem Lader entsprechend dem eingebauten Druckverhältnis des Laders abgesenkt werden, um nach dem Lader den geforderten Saugdruck des Motors bereitstellen zu können. Diese Druckabsenkung führt zu einer relativ hohen Verlust­leistung, die vom Motor aufgebracht werden muß.If the combustion air of the engine is led through the charger in throttle and compression mode, the charger 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.

Wird im gedrosselten Betriebszustand der Lader z.B. durch einen Bypass umgangen und erst im Kompressions­betrieb über eine Kupplung zugeschaltet, was einen erheblichen Regel- und Bauaufwand erfordert, ergibt sich ein sprunghafter Drehmomentanstieg des Motors bei Zuschaltung des Laders.If, in the throttled operating state, 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.

Darüber hinaus hat der Motor nach wie vor die an der Drosselklappe entstehenden Verluste aufzubringen.In addition, the engine still has to incur the losses resulting from the throttle valve.

Aus DE-AS 1 293 384 ist eine schiebergeregelte Schrauben­rotormaschine von der im Oberbegriff des Anspruchs 2 an­ gegebenen Art bekannt. Durch axiale Verstellung des Schiebers kann dabei der Zeitpunkt, an welchem sich die von den ineinandergreifenden Rotoren und der Gehäuse­wand umschlossenen Verdichterzellen vom Niederdruck­einlaß abtrennen, verändert werden, wodurch die Durch­satzleistung der Maschine bzw. auch das Nenndruckver­hältnis verändert werden kann. Hierbei kann jedoch der Ansaugquerschnitt der Schraubenrotormaschine nur ver­ändert, aber nicht völlig geschlossen werden. Bei Ver­wendung einer solchen Maschine als Auflader eines Ver­brennungsmotors wäre deshalb immer noch ein zusätzliches Drosselorgan zum Verändern der Ansaugmenge des Verbren­nungsmotors, z.B. die übliche Drosselklappe, erforderlich.From DE-AS 1 293 384 is a slider-controlled screw rotor machine from the in the preamble of claim 2 given type known. By axially adjusting the slide, 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. However, the intake cross section of the screw rotor machine can only be changed, but not completely closed. When using such a machine as a supercharger for an internal combustion engine, an additional throttle element for changing the intake quantity of the internal combustion engine, for example the conventional throttle valve, would still be required.

Es ist Aufgabe der Erfindung, einen aufgeladenen Verbren­nungsmotor, sowie eine als Auflader für einen solchen Motor verwendbare Schraubenrotormaschine anzugeben, durch die ohne großen Bau- und Regelaufwand die im gedrosselten Betrieb entstehenden Verluste sowohl des Aufladers als auch der bisher erforderlichen Drosselklappe reduziert werden. Ferner soll sich ein stetiger Drehmomentverlauf des Motors beim Übergang vom gedrosselten zum aufgeladenen Betriebs­zustand ergeben.It is an object of the invention to provide a supercharged internal combustion engine and a screw rotor machine which can be used as a supercharger for such an engine, by means of which the losses in the throttled operation, both of the supercharger and of the previously required throttle valve, are reduced without great construction and control expenditure. Furthermore, there should be a steady torque curve of the engine during the transition from the throttled to the charged operating state.

Diese Aufgabe wird erfindungsgemäß gelöst durch den im Anspruch 1 gekennzeichneten aufgeladenen Verbrennungs­ motor bzw. durch die im Anspruch 2 gekennzeichnete Schraubenrotormaschine. Die Unteransprüche geben weitere vorteilhafte Ausgestaltungen an.This object is achieved by the charged combustion characterized in claim 1 motor or by the screw rotor machine characterized in claim 2. The subclaims indicate further advantageous refinements.

Kern der Erfindung ist die Lehre, den auf der Saugseite eines Schraubenkompressors vorgesehenen Schieber anstelle der Drosselklappe herkömmlicher Saugmotoren zu verwenden und entsprechend zu betätigen.The essence of the invention is the teaching to use the slide provided on the suction side of a screw compressor instead of the throttle valve of conventional suction motors and to actuate it accordingly.

Ausführungsformen der Erfindung werden anhand de Zeich­nungen näher erläutert. Es zeigt :

  • Fig. 1 einen Längsschnitt durch einen schieberge­steuerten Schraubenkompressor gemäß einer Ausführungsform der Erfindung;
  • Fig. 2 und 3 Schnitte gemäß den Linien A-A bzw. B-B von Fig. 1;
  • Fig. 4 eine Schemadarstellung eines mit dem Schrauben­kompressor nach Fig. 1 bis 3 als Auflader aus­gerüsteten Verbrennungsmotors;
  • Fig. 5 ein Diagramm, das die Abhängigkeit des Zellen­volumens in Abhängigkeit von der Winkelstellung der Schraubenrotoren wiedergibt;
  • Fig. 6 ein Druck-Volumen-Zustandsdiagramm der Schraubenrotormaschine;
  • Fig. 7, 8 und 9 vereinfachte Schnittdarstellungen ähnlich
  • Fig. 1 von Schraubenrotormaschinen mit ge­änderter Konstruktion des Schiebers.
Embodiments of the invention are explained in more detail with reference to the drawings. It shows :
  • 1 shows a longitudinal section through a slide-controlled screw compressor according to an embodiment of the invention.
  • Figures 2 and 3 sections along lines AA and BB of Fig. 1.
  • 4 shows a schematic representation of an internal combustion engine equipped with the screw compressor according to FIGS. 1 to 3 as a supercharger;
  • 5 shows a diagram which shows the dependence of the cell volume as a function of the angular position of the screw rotors;
  • 6 is a pressure-volume state diagram of the screw rotor machine;
  • 7, 8 and 9 simplified sectional views similar
  • Fig. 1 of screw rotor machines with a modified construction of the slide.

Die in Fig. 1 bis 3 dargestellte Schraubenrotormaschine 1 hat einen Schraubenrippenrotor oder Hauptläufer 2 und einen Schraubennutenrotor oder Nebenläufer 3, die achs­parallel und miteinander kämmend in dem von zwei sich schneidenden Kreiszylindern gebildeten Arbeitsraum eines Gehäuses 13 angeordnet sind. Bei dem Ausführungsbeispiel ist der Hauptläufer 2 angetrieben, und der Antrieb wird über die Synchronisierzahnräder 10 und 9 auf den Neben­rotor 3 übertragen. Es ist aber auch möglich, den Nebenläufer 3 anzutreiben, und ferner kann das Synchro­nisiergetriebe 10, 9 weggelassen und der Antrieb direkt über die ineinandergreifenden Rotorflanken von dem einen auf den anderen Läufer übertragen werden.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. In the exemplary embodiment, the main rotor 2 is driven, and the drive is transmitted to the secondary rotor 3 via the synchronizing gears 10 and 9. However, 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 transmitted directly from one rotor to the other via the intermeshing rotor flanks.

In den Arbeitsraum des Gehäuses 13 münden auf der einen Gehäuseseite der Saugstutzen 7 und auf der anderen Ge­häuseseite der Druckstutzen 8. Der Arbeitsraum des Ge­häuses ist an dem dem Saugstutzen zugeordneten Ende durch die niederdruckseitige Arbeitsraumstirnwand 12 und an dem dem Druckstutzen 8 zugeordneten Ende durch die hochdruckseitige Arbeitsraumstirnwand 11 abgeschlossen.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.

Auf der dem Saugstutzen 7 zugewandten Gehäuseseite wird die Umfangswandung des Arbeitsraums im Verschneidungs­bereich der beiden Kreiszylinder durch einen axial ver­schieblich geführten Schieber 4 gebildet. Durch Axial­verstellung des Schiebers 4 kann die Verbindung des Saugstutzens 7 zum Arbeitsraum des Gehäuses 13 voll­ständig verschlossen bzw. mehr oder weniger freigegeben werden. An seiner in Schließrichtung vorne liegenden Stirnfläche hat der Schieber 4 eine schwalbenschwanzartige Kontur, die durch die Linie 4a in Fig. 2a angedeutet ist, und die an den Verlauf der schraubenförmigen Kopf- oder Gratlinien von zwei ineinandergreifenden Haupt- und Neben­rotorrippen im Bereich der Schieberöffnung angepaßt ist. Damit der Schieber 4 trotz dieser schwalbenschwanzartig ausgekerbten Stirnseite die Verbindung zum Saugstutzen 7 vollständig verschließen kann, muß der Schieber 4 so weit über die niederdruckseitige Stirnwand 12 des Arbeitsraums hinausbewegt werden können, bis auch die durch den stirn­seitigen Zwickel des Schiebers 4 entstehende Öffnung zwischen Saugstutzen 7 und Arbeitsraum geschlossen ist. In Fig. 2 ist die Lage der Stirnfläche des Schiebers 4 bei vollständig geschlossener Stellung durch die ge­strichelte Linie 4b angedeutet. Die niederdruckseitige Stirnwand 12 des Arbeitsraums muß deshalb eine die voll­ständige Schließbewegung des Schiebers 4 gestattende Aus­nehmung oder Tasche aufweisen, während die Öffnungsbewe­gung des Schiebers durch eine entsprechende Ausnehmung in der hochdruckseitigen Stirnwand 11 ermöglicht wird.On the housing side facing the suction port 7, 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. 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. So that the slider 4 can completely close the connection to the suction port 7 in spite of this dovetail notched end, 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.

Der Schieber 4 wird durch eine in seinem Inneren angeord­nete Schraubenfeder 5 selbsttätig in seine Schließlage gedrückt. Er kann entgegen der Kraft der Feder 5 durch eine Zugvorrichtung 6, z.B. einen Bowdenzug, in Öffnungsrichtung bewegt werden, um die Verbindung des Saugstutzens 7 zum Arbeitsraum mehr oder weniger, gege­benenfalls bis zum vollen Maximalwert, freizugeben.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.

Fig. 4 zeigt schematisch die Anordnung einer Schraubenrotor­maschine 1 als Lader in dem vom Luftfilter 17 zu den Zylin­derräumen eines z.B. vierzylindrigen Verbrennungsmotors 20 führenden Luftansaugsystem. Mit 18 ist die vom Luftfilter 17 kommende Saugleitung des Laders 1 und mit 19 die von diesem beaufschlagte Saugleitung zum Verbrennungsmotor 20 bezeichnet. Der Lader 1 wird über z.B. einen Riemenantrieb 22 von der Kurbelwelle des Motors 20 angetrieben. 23 ist die Abgas­leitung des Verbrennungsmotors. Der Schieber 4 des Laders 1 wird über die Zugvorrichtung 6 durch das Gaspedal 21 des Verbrennungsmotors 20 gesteuert. Außer über die vom Schieber 4 gesteuerte Öffnung sowie die maschinenbedingten Leckspaltflächen des Aufladers 1 besteht keine weitere Verbindung von der Ansaugleitung 18 zum Arbeitsraum des Laders 1 und von da zu der vom Lader 1 beaufschlagten Leitung 19. Ferner ist in dem über die Leitungen 18, 19 verlaufenden Ansaugweg des Motors 20 außer dem Schieber 4 kein weiteres Drosselorgan, z.B. in Form der üblichen Drosselklappe, vorgesehen. Der Schieber 4 übernimmt die Funktion der Drosselklappe, so daß er z.B. über das Gas­pedal 21 geöffnet und beim Loslassen des Gaspedals durch die Feder 5 (Fig. 1) selbsttätig geschlossen wird.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. Except via the opening controlled by the slide 4 and the machine-related leakage gap areas of the supercharger 1, there is no further connection from the suction line 18 to the working space of the Loader 1 and from there to the line 19 acted upon by the loader 1. Furthermore, in the intake path of the engine 20 running via the lines 18, 19, no further throttle element, for example in the form of the usual throttle valve, is provided in addition to the slide 4. The slide 4 takes over the function of the throttle valve, so that it is opened, for example, via the accelerator pedal 21 and is automatically closed by the spring 5 (FIG. 1) when the accelerator pedal is released.

Durch die Kombination aller dieser Konstruktionsdetails ist es möglich, die geregelte Schraubenrotormaschine 1 sowohl als Kompressor (Schieber 4 voll geöffnet) sowie als kombinierten Expander und Kompressor (Schieber 4 teilweise geöffnet oder geschlossen) zu betreiben.The combination of all these construction details makes it possible to operate the regulated screw rotor machine 1 both as a compressor (slide 4 fully open) and as a combined expander and compressor (slide 4 partially open or closed).

Der Betrieb als Expander ist nur dann sinnvoll möglich, wenn die Arbeitsräume auf der Saugseite der Schrauben­rotormaschine 1 genauso dicht sind, wie auf der Druckseite. Diese Dichtheit wird durch die gleiche, zweckmäßigerweise aus Zykloiden aufgebaute Profilform der vor- und nach­laufenden Flanken der Rotorzähne erreicht, wie dies in Fig. 3 dargestellt ist.Operation as an expander is only sensibly possible if the working spaces on the suction side of the screw rotor machine 1 are just as tight as on the pressure side. This tightness is achieved by the same profile shape, expediently constructed from cycloids, of the leading and trailing flanks of the rotor teeth, as is shown in FIG. 3.

Die Funktionsweise dieses geregelten Schraubenladers, durch den im gedrosselten Betrieb Arbeit zurückgewonnen werden kann, wird anhand der Volumenkurve in Fig. 1 und des p-V-Diagramms in Fig. 2 beschrieben.The functioning of this regulated screw loader, by means of which work can be recovered in throttled operation, is described on the basis of the volume curve in FIG. 1 and the p-V diagram in FIG. 2.

Während der herkömmliche Schraubenlader die Luft ansaugt, bei Erreichen des maximalen Zellvolumens (Punkt Z in Fig. 1) die Arbeitsräume schließt, bis zum Erreichen der Auslaß­steuerkanten das Volumen verkleinert (Punkt 2 in Fig. 1) und anschließend die Luft ausschiebt, besteht beim ge­regelten Schraubenlader die Möglichkeit, das Schließen der Arbeitsräume zum Saugraum hin, je nach Schieberstellung, zwischen dem minimalen (Punkt 1) und maximalen Zellvolumen (Punkt Z) zu variieren.While the conventional screw loader sucks in the air, closes the work area when the maximum cell volume is reached (point Z in Fig. 1), reduces the volume until the outlet control edges are reached (point 2 in Fig. 1) and then expels the air Screw loader the possibility to vary the closing of the work rooms towards the suction chamber, depending on the slide position, between the minimum (point 1) and maximum cell volume (point Z).

Ist der Steuerschieber teilweise geschlossen, ergibt sich ein Zustandsverlauf entsprechend der Kurve I in Fig. 2. Beim Er­reichen des Volumens VI werden die Arbeitsräume zur Um­gebung hin geschlossen. Im Anschluß daran wird die ange­saugte Luft solange expandiert, bis das maximale Zell­volumen Vmax erreicht ist. Die in Fig. 2 punktiert darge­stellte Fläche stellt die Arbeit dar, die durch die Expan­sion abgegeben wird. Nach Erreichen des maximalen Zell­volumens wird die Luft solange komprimiert, bis das durch die eingebauten Steuerkanten vorgegebene Volumen V₂ erreicht ist.If the control slide is partially closed, there is a state curve corresponding to curve I in FIG. 2. When volume V I is reached , the working spaces are closed to the surroundings. The sucked-in air is then expanded until the maximum cell volume V max is reached. The area shown in dotted lines in FIG. 2 represents the work which is given off by the expansion. After reaching the maximum cell volume, the air is compressed until it is through the built-in control edges predetermined volume V₂ is reached.

Die durch die Kompression aufgenommene Arbeit entspricht der in Fig. 2 schraffierten Fläche.The work taken up by the compression corresponds to the area hatched in FIG. 2.

Die durch den geregelten Schraubenlader zurückgewonnene Arbeit entspricht damit der Fläche zwischen den Punkten A-B-C-D im p-V-Diagramm in Fig. 2.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. 2.

Ist der Schieber im Kompressionsbetrieb (Zustandsverlauf entsprechend der Kurve II in Fig. 2) voll geöffnet, findet keine Expansion statt, und die vom Kompressor aufgenommene Arbeit entspricht im p-V-Diagramm in Fig. 2 der Fläche zwischen den Punkten A-E-F-G.If the slide is fully open in the compression mode (state curve corresponding to curve II in FIG. 2), no expansion takes place and the work taken up by the compressor corresponds to the area between points A-E-F-G in the p-V diagram in FIG. 2.

Der Ersatz der Drosselklappe durch einen Schieber sowie der damit verbundene Arbeitsrückgewinn kann allerdings nur dann optimal erreicht werden, wenn durch den Schieber und die Rotorgeometrie die Arbeitsräume des Schrauben­laders auf der Saug- und Druckseite, abgesehen von den maschinenbedingten Leckspalten, vollständig abgeschlossen werden und der Schieber darüber hinaus alle Funktionen der Drosselklappe, wie z.B. das vollständige Schließen bei Entladung der Zugvorrichtung oder den kontiuierlichen Übergang vom Drossel- zum Kompressionsbetrieb über nimmt.However, the replacement of the throttle valve by a slide and the associated work recovery can only be achieved optimally if, through the slide and the rotor geometry, the work spaces of the screw loader on the suction and pressure side, apart from the machine-related leakage gaps, are completely closed and the slide In addition, all functions of the throttle valve, such as the complete closing when the towing device is unloaded or the continuous Transition from throttle to compression mode.

Bei herkömmlichen Steuerschiebern ist zwar die Re­gulierung der Luftmenge in bestimmten Bereichen mög­lich, eine vollständiges, kontinuierliches Schließen der Arbeitsräume sowie Arbeitsrückgewinn jedoch nicht.With conventional spool valves, it is possible to regulate the air volume in certain areas, but complete, continuous closing of the work rooms and work recovery is not.

Das selbständige Schließen des Schiebers 4 bei Entlastung der Zugvorrichtung 6 kann entsprechend der schematischen Darstellung in Fig. 7 und der konstruktiven Ausführung in Fig. 1 durch eine oder mehrere Federn 5 erreicht wer­den, die gegen die Zugvorrichtung 6, die z.B. als Bowden­zug ausgebildet sein kann, arbeiten.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.

Anstatt des Federsystems kann auch ein hydraulisches Rückstellsystem entsprechend der schematischen Darstellung in Fig. 8 benutzt werden, wobei die Schieberrückstellung z.B. durch die Druckerhöhung des im Schieber befindlichen Öls erfolgt.Instead of the spring system, a hydraulic return system according to the schematic illustration in Fig. 8 can also be used, the slide return e.g. by increasing the pressure of the oil in the slide.

Erfolgt der Antrieb des Schiebers entsprechend Fig. 9 über einen Elektromotor 14 und z.B. ein Zahnrad 15 auf der Motorwelle und eine Zahnstange 16 auf dem Schieber 4, so kann auch die Zugvorrichtung entfallen, wenn der Schieber 4 über den Elektromotor, der z.B. in Abhängig­keit von der Gaspedalstellung eines Fahrzeugs geregelt wird, in beide Richtungen (Öffnen oder Schließen) be­wegt werden kann.9 is driven by an electric motor 14 and, for example, a toothed wheel 15 on the motor shaft and a toothed rack 16 on the slide 4, 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.

Um eine möglichst leichte Betätigung des Schiebers 4 z.B. über das Gaspedal eines Fahrzeugs zu erreichen, kann es notwendig werden, die Gleitflächen des Schiebers mit Gleitlack oder ähnlichen, den Reibungskoeffizienten her­absetzenden,Beschichtungen zu versehen.In order to actuate the slide 4 as easily as possible, e.g. To reach the accelerator pedal of a vehicle, it may be necessary to provide the sliding surfaces of the slide with lubricating varnish or similar coatings that reduce the coefficient of friction.

Das Drehmoment zwischen Haupt- 2 und Nebenrotor 3 kann entweder über das Synchronisationsgetriebe 9, 10 oder über den Profilbereich der Rotoren des Schraubenladers über­tragen werden, um eine kürzere Bauweise zu erzielen. Bei der Leistungsübertragung über den Profilbereich der Rotoren ist es zur Verringerung des Verschleisses vorteilhaft, die Rotoren zu härten oder zu beschichten.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. In the case of power transmission over the profile area of the rotors, it is advantageous to harden or coat the rotors to reduce wear.

Bei dem in Fig. 4 schematisch dargestellten Verbrennungs­motor 20 handelt es sich vorzugsweise um einen Dieselmotor oder um einen Ottomotor mit Einspritzung, so daß der Lader 1 nur die Ansaugluft verdichtet. Es ist aber auch denkbar, den erfindungsgemäß ausgebildeten Schraubenkom­ pressor als Auflader auch bei einem Vergasermotor derart einzusetzen, daß er das vom Vergaser kommende Gemisch vorverdichtet.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. But it is also conceivable to use the screw designed according to the invention use pressor as a supercharger in a carburetor engine in such a way that it pre-compresses the mixture coming from the carburetor.

Bei der in Fig. 4 dargestellten bevorzugten Ausführungs­form wird der Lader 1 von der Kurbelwelle des Motors 20 über die Transmission 22 ständig angetrieben. Es ist aber auch denkbar, den Lader über eine ein- und auskuppel­bare Transmission nur bedarfsweise zuzuschalten.In the preferred embodiment shown in FIG. 4, the supercharger 1 is continuously driven by the crankshaft of the engine 20 via the transmission 22. However, it is also conceivable to connect the charger only as needed via a transmission that can be engaged and disengaged.

Claims (5)

1. Aufgeladener Verbrennungsmotor mit im Ansaugweg an­geordnetem Kompressor, dadurch gekennzeichnet, daß der Kompressor als Schraubenrotormaschine (1) ausgebildet ist und auf seiner Saugseite einen Schieber (4) aufweist, durch den der Ansaugquerschnitt der Schraubenrotormaschine vollständig verschließbar oder geregelt freigebbar ist, und daß der Schieber (4) das die Ansaugmenge des Motors (20) steuernde Drosselorgan darstellt und vom Gaspedal (21) od.dgl. Leistungssteuerglied des Motors (20) betätigbar ist.1. Supercharged internal combustion engine with a compressor arranged in the intake path, characterized in that the compressor is designed as a screw rotor machine (1) and has on its suction side a slide (4) through which the intake cross section of the screw rotor machine can be completely closed or released in a controlled manner, and that Slider (4) which represents the intake quantity of the engine (20) controlling the throttle element and the accelerator pedal (21) or the like. Power control member of the motor (20) can be actuated. 2. Schiebergeregelte Schraubenrotormaschine, insbe­sondere zur Verwendung als Lader bei einem Verbrennungs­motor nach Anspruch 1, mit mindestens zwei mit ihren Schraubenrippen und -nuten ineinandergreifenden Schrauben­rotoren, die in den von achsparallelen und einander durchdringenden Zylinderbohrungen gebildeten und von Stirnwänden begrenzten Arbeitsraum eines Gehäuses ange­ordnet sind, wobei das Gehäuse je einen in den Arbeits­raum mündenden Niederdruckstutzen und Hochdruckstutzen sowie einen parallel zu den Rotorachsen verschiebbar gelagerten Schieber aufweist, der einen Teil der Umfangs­wand des Arbeitsraums auf der dem Niederdruckstutzen zugeordneten Seite bildet und je nach seiner Stellung den Strömungsweg vom Niederdruckstutzen in den Arbeits­raum mehr oder weniger freigibt , dadurch gekenn­zeichnet, daß die Verbindung vom Niederdruck­stutzen (7) zum Arbeitsraum durch den Schieber (4) voll­ständig verschließbar ist.2. Slider-controlled screw rotor machine, in particular for use as a loader in an internal combustion engine according to claim 1, with at least two interlocking with their screw ribs and grooves screw rotors, which are arranged in the axially parallel and penetrating cylinder bores and delimited by end walls working space of a housing, wherein the housing each has a low-pressure nozzle and a high-pressure nozzle opening into the work space and a slide which is displaceably mounted parallel to the rotor axes and forms part of the circumferential wall of the work space on the side assigned to the low-pressure nozzle and, depending on its position, the flow path from the low-pressure nozzle to the work space more or less releases, characterized in that the connection from the low-pressure nozzle (7) to the work space can be completely closed by the slide (4). 3. Schraubenrotormaschine nach Anspruch 2 , dadurch gekennzeichnet, daß der Schieber (4) auf seiner in Schließrichtung vorne liegenden Stirnseite eine Kontur (4a) hat, die dem Verlauf der Kopflinien der ineinandergreifenden Rotorzähne im Bereich der Schieber­ öffnung entspricht, und daß der Schieber (4) durch eine Ausnehmung in der niederdruckseitigen Stirnwand (12) so weit über diese hinausbewegbar ist, bis die durch den Zwickel der Schieberkontur gebildete Öffnung zwischen Niederdruckstutzen (7) und Arbeitsraum geschlossen ist.3. Screw rotor machine according to claim 2, characterized in that the slide (4) on its front end in the closing direction has a contour (4a) that the course of the top lines of the interlocking rotor teeth in the region of the slide opening corresponds, and that the slide (4) through a recess in the low-pressure side end wall (12) can be moved so far beyond this until the opening formed by the gusset of the slide contour between the low-pressure nozzle (7) and the working space is closed. 4. Schraubenrotormaschine nach Anspruch 2 , dadurch gekennzeichnet, daß die Schraubenrippen und Schraubennuten der beiden Rotoren (2, 3) jeweils symmetrische Profilformen mit gleich ausgebildeter vor­und nachlaufender Flanke aufweisen.4. Screw rotor machine according to claim 2, characterized in that the screw ribs and screw grooves of the two rotors (2, 3) each have symmetrical profile shapes with the same trained leading and trailing flank. 5. Schraubenrotormaschine nach Anspruch 2 , dadurch gekennzeichnet, daß der Schieber (4) durch eine Rückstelleinrichtung (5) in seiner Schließstellung gehalten und mittels einer Stellvorrichtung (6) entgegen der Rückstellkraft in Öffnungsrichtung bewegbar ist.5. Screw rotor machine according to claim 2, characterized in that the slide (4) is held in its closed position by a restoring device (5) and can be moved in the opening direction against the restoring force by means of an adjusting device (6).
EP88118719A 1988-02-02 1988-11-10 Slide-controlled screw rotor machine and supercharged internal-combustion engine equipped therewith Expired - Lifetime EP0326663B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3803044 1988-02-02
DE3803044A DE3803044A1 (en) 1988-02-02 1988-02-02 SLIDER-CONTROLLED SCREW-ROTOR MACHINE AND CHARGED COMBUSTION ENGINE

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

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EP (1) EP0326663B1 (en)
JP (1) JPH0654092B2 (en)
KR (1) KR930005961B1 (en)
DE (2) DE3803044A1 (en)
ES (1) ES2035220T3 (en)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0484884A2 (en) * 1990-11-06 1992-05-13 Honda Giken Kogyo Kabushiki Kaisha Method for controlling the supercharge pressure in internal combustion engine
WO1994024426A1 (en) * 1993-04-21 1994-10-27 Opcon Autorotor Ab Supercharged internal combustion engine
US20110083432A1 (en) * 2009-10-14 2011-04-14 Hansen Craig N Internal combustion engine and supercharger
WO2011046591A1 (en) 2009-10-14 2011-04-21 Hansen Craig N Internal combustion engine and supercharger

Families Citing this family (5)

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Publication number Priority date Publication date Assignee Title
JPH0669993U (en) * 1993-03-09 1994-09-30 清 秋生 Toy whistle
GB9912645D0 (en) * 1999-05-28 1999-07-28 Seneca Tech Ltd Super-charger for i.c. engine
JP2007085174A (en) * 2004-01-08 2007-04-05 Koichi Hatamura Displacement compressor and supercharger using the same
DE102015007552A1 (en) 2015-06-16 2016-12-22 Man Diesel & Turbo Se Screw machine and method of operating the same
DE102021134652B3 (en) 2021-12-23 2023-05-11 Man Energy Solutions Se screw compressor

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DE8415188U1 (en) * 1984-05-18 1985-08-22 Pierburg Gmbh & Co Kg, 4040 Neuss Device for controlling the inlet opening of a rotary vane or vane compressor
WO1987002417A1 (en) * 1985-10-14 1987-04-23 Svenska Rotor Maskiner Ab An arrangement in an internal combustion engine provided with a supercharger

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GB959831A (en) * 1959-06-04 1964-06-03 Svenska Rotor Maskiner Ab Improvements in or relating to screw rotor machines

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FR1258650A (en) * 1960-06-01 1961-04-14 Svenska Rotor Maskiner Ab Axial displacement sliders for helical rotor machines
DE8415188U1 (en) * 1984-05-18 1985-08-22 Pierburg Gmbh & Co Kg, 4040 Neuss Device for controlling the inlet opening of a rotary vane or vane compressor
WO1987002417A1 (en) * 1985-10-14 1987-04-23 Svenska Rotor Maskiner Ab An arrangement in an internal combustion engine provided with a supercharger

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0484884A2 (en) * 1990-11-06 1992-05-13 Honda Giken Kogyo Kabushiki Kaisha Method for controlling the supercharge pressure in internal combustion engine
EP0484884A3 (en) * 1990-11-06 1993-06-16 Honda Giken Kogyo Kabushiki Kaisha Method for controlling the supercharge pressure in internal combustion engine
WO1994024426A1 (en) * 1993-04-21 1994-10-27 Opcon Autorotor Ab Supercharged internal combustion engine
US20110083432A1 (en) * 2009-10-14 2011-04-14 Hansen Craig N Internal combustion engine and supercharger
WO2011046591A1 (en) 2009-10-14 2011-04-21 Hansen Craig N Internal combustion engine and supercharger
WO2011046584A1 (en) 2009-10-14 2011-04-21 Hansen Craig N Internal combustion engine and supercharger
EP2488724A1 (en) * 2009-10-14 2012-08-22 Craig N. Hansen Internal combustion engine and supercharger
EP2488738A1 (en) * 2009-10-14 2012-08-22 Craig N. Hansen Internal combustion engine and supercharger
CN102667061A (en) * 2009-10-14 2012-09-12 克雷格·N·海山 Internal combustion engine and supercharger
EP2488724A4 (en) * 2009-10-14 2013-07-17 Craig N Hansen Internal combustion engine and supercharger
EP2488738A4 (en) * 2009-10-14 2013-07-17 Craig N Hansen Internal combustion engine and supercharger
US8813492B2 (en) 2009-10-14 2014-08-26 Hansen Engine Corporation Internal combustion engine and supercharger
CN102667061B (en) * 2009-10-14 2015-09-16 海山引擎公司 Be assembled with the internal-combustion engine of pressurized machine

Also Published As

Publication number Publication date
JPH01310119A (en) 1989-12-14
EP0326663B1 (en) 1992-10-21
KR930005961B1 (en) 1993-06-30
EP0326663A3 (en) 1990-03-14
DE3875471D1 (en) 1992-11-26
ES2035220T3 (en) 1993-04-16
DE3803044A1 (en) 1989-08-10
JPH0654092B2 (en) 1994-07-20
KR890013321A (en) 1989-09-22

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