EP0290864B1 - Internal axis rotary piston machine - Google Patents

Internal axis rotary piston machine Download PDF

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Publication number
EP0290864B1
EP0290864B1 EP88106729A EP88106729A EP0290864B1 EP 0290864 B1 EP0290864 B1 EP 0290864B1 EP 88106729 A EP88106729 A EP 88106729A EP 88106729 A EP88106729 A EP 88106729A EP 0290864 B1 EP0290864 B1 EP 0290864B1
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EP
European Patent Office
Prior art keywords
housing
rotary piston
outer rotor
valve body
rotor
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
EP88106729A
Other languages
German (de)
French (fr)
Other versions
EP0290864A2 (en
EP0290864A3 (en
Inventor
Arno Förster
Gerhard Oberholz
Christiane Römuss
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.)
Howden Turbo GmbH
Original Assignee
Siemens Turbomachinery Equipment GmbH
Kuehnle Kopp and Kausch 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 Siemens Turbomachinery Equipment GmbH, Kuehnle Kopp and Kausch AG filed Critical Siemens Turbomachinery Equipment GmbH
Priority to AT88106729T priority Critical patent/ATE68557T1/en
Publication of EP0290864A2 publication Critical patent/EP0290864A2/en
Publication of EP0290864A3 publication Critical patent/EP0290864A3/en
Application granted granted Critical
Publication of EP0290864B1 publication Critical patent/EP0290864B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/10—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F01C1/103—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C20/00—Control of, monitoring of, or safety arrangements for, machines or engines
    • F01C20/24—Control of, monitoring of, or safety arrangements for, machines or engines characterised by using valves for controlling pressure or flow rate, e.g. discharge valves
    • F01C20/26—Control of, monitoring of, or safety arrangements for, machines or engines characterised by using valves for controlling pressure or flow rate, e.g. discharge valves using bypass channels

Definitions

  • the invention relates to a rotary piston machine according to the features specified in the preamble of patent claim 1.
  • the inner rotor is mounted eccentrically to the axis of rotation of the outer rotor and has three engagement parts which can engage in four recesses in the outer rotor in accordance with the current rotational position.
  • a high level of manufacturing effort is necessary and compression could previously only be achieved if the medium to be conveyed was itself suitable as a sealant.
  • an inner-axis rotary piston machine is known, the inner rotor of which has two engagement parts and the outer rotor of which has three recesses.
  • the inner surfaces, which delimit the recesses of the outer rotor, are designed as flat surfaces in order to enable simple manufacture.
  • the inner rotor In order to enable a rolling motion of the inner rotor on the aforementioned flat surfaces of the outer rotor, the inner rotor must have a special geometry, the production of which nevertheless requires a not inconsiderable effort.
  • the formation and arrangement of the bearings is particularly problematic of inner rotor and outer rotor. Very tight manufacturing tolerances have to be observed so that on the one hand excessive surface pressures are avoided and on the other hand no undesirably large gaps can occur between the inner rotor and outer rotor.
  • the invention has for its object to further develop the internal-axis rotary lobe machine of the type mentioned in such a way that a high level of functional reliability and a long service life can be achieved with a simple construction taking into account permissible manufacturing tolerances.
  • the proposed rotary lobe machine is characterized by an expedient construction and has a high level of functional reliability and a long service life.
  • the number of components to be coordinated with respect to the manufacturing tolerances is small and the manufacturing effort is limited.
  • Due to the one-piece molding of the base on the housing the bearings of the inner rotor and of the outer rotor are expediently integrated into the housing, as a result of which an exact geometric allocation of the inner rotor is both is guaranteed with respect to the outer rotor as well as with respect to the housing.
  • the bearing of the inner rotor is arranged on the extension which extends into the drive disk and can therefore be designed with a comparatively small diameter.
  • the machining surfaces and corresponding manufacturing tolerances that are required in the case of a multi-part construction of the housing and the bottom are eliminated. With little work and assembly effort, high accuracy is reliably ensured even when manufacturing in large quantities.
  • the arrangement of the gearbox in the housing cover, which closes the housing, enables a compact design with a few components to be coordinated in terms of their tolerances.
  • the gearbox is arranged in the housing cover, which closes the cup-shaped housing.
  • a line opening into the gear chamber which can be arranged externally outside the housing or can be integrated as a longitudinal bore in the housing, can expediently equalize the pressure to the suction nozzle and prevent lubricant from being pressed into the working spaces.
  • the gear is easily accessible for maintenance without having to remove the rotors.
  • the pinion of the gearbox expediently connected to the shaft of the inner rotor remains accessible in the assembled state of the rotors.
  • the housing cover or even rotor bearings do not have to be removed in order to change the rotational position of the pinion with respect to the inner rotor for the exact setting of the tooth flank play.
  • the pinion can easily be turned on the shaft to obtain the required angle of rotation setting.
  • the shaft can also be led out through the end cover, for example to couple an alternator or another unit to the shaft of the inner rotor.
  • a centrifugal plate is arranged in the gearbox on the inner rotor and / or on the outer rotor.
  • the lubricant is conveyed to the ring gear of the outer rotor or to the pinion.
  • a recirculation valve is arranged between the pressure port and the suction port, which, in certain operating states, enables regulation by returning the air from the pressure port to the suction port.
  • This valve can be used for boost pressure control and can also be advantageously used in combination for partial load control.
  • a valve of this type solves the task of reducing consumption in the part-load range by means of part-load control and, on the other hand, limiting the boost pressure in the full-load range by boost pressure control.
  • This valve is expediently provided in the above-described rotary piston machine according to the US Pat. No. 4,714,417 explained at the outset.
  • the suitably combined valve can also be provided for charging in other engines, in particular in automotive engines.
  • the air mass flow conveyed by the machine is fed wholly or in part to the suction side as required, the two valve components being expediently housed in a common housing.
  • the valve intended for partial load control When the engine to be charged with the rotary lobe engine is idling, the valve intended for partial load control is open and the engine is operating in suction mode. As the load increases, the partial load valve expediently closes continuously in a predeterminable range and the motor is charged in the required manner by means of the rotary piston machine. In the full load range, the valve provided for the boost pressure control opens when an adjustable maximum boost pressure is reached. When the load is reduced, these processes take place in reverse order.
  • the air recirculation valve is arranged in a cover which is tightly connected to the housing and advantageously has the valve guide and the return line. The proposed valve requires a small amount of space and weight, which is particularly important in motor vehicle engines.
  • Figure 1 shows an axial longitudinal section of the inner-axis rotary lobe machine with a cup-shaped housing 2, which has a bottom 4 and is closed at the other axial end with a single housing cover 6.
  • An inner rotor 8 is arranged in the interior of the housing 2 and is rotatably mounted about an axis 10 by means of a shaft 12 which is led out through the base 4.
  • a bearing 16 is arranged in a shoulder 14 of the base 4, which bearing is expediently designed as a combined axial / radial bearing.
  • a second bearing 18 is arranged in the housing cover 6, which is preferably designed as a needle bearing.
  • the bearing 16 provided in the projection 14 is surrounded by a pot-shaped pulley 20 which lies essentially in the same radial plane as the bearing 16 mentioned and is connected to the shaft 12 in a rotationally fixed manner.
  • the inner rotor 8 can be made of plastic or light metal and is connected directly to the shaft 12, in particular by composite casting. This one-piece construction ensures a not inconsiderable simplification of assembly.
  • the bearing 16 and the pulley 20 are fixed on the shaft 12 by means of a nut 22 screwed onto a thread at the shaft end, the support on the inner rotor 8 being carried out by means of a spacer sleeve 24.
  • an outer rotor 26 is arranged in the interior of the housing 2, work spaces being formed in a known manner with the inner rotor 8.
  • the relevant principles and the mode of operation result from the aforementioned US Pat. No. 4,714,417, to which reference is expressly made here.
  • the bottom 4 of the housing 2 has a ring 28 extending axially into the end of the outer rotor 26, on the outer surfaces of which the bearing 30 of the outer rotor 26 is arranged.
  • the outer rotor 26 has three engagement parts 34 distributed over the circumference, which are in one piece are formed with a rotor disk 36. Also important is the axially spaced arrangement of the bearing 30 in the ring 28 with respect to the bearing 16 from the inner rotor 8, so that the bearing 30 of the outer rotor 26 has a comparatively small diameter.
  • the outer rotor 26 has a ring 38 which is connected to the engaging parts 34 by means of screws 40.
  • the second bearing 32 for the outer rotor 26 is arranged according to the invention within the rotor ring 38 on the housing cover 6.
  • an internally toothed wheel 42 is expediently connected to the outer rotor 26.
  • the internally toothed wheel 42 meshes with a pinion 44 which is arranged on the shaft 12 of the inner rotor 8 in a frictionally engaged manner.
  • the pinion 44 is braced against a shaft collar 50 by means of a nut 46 via a bearing sleeve 48.
  • the backlash of the gear and the angular position of the inner rotor 8 and outer rotor 26 can be adjusted without difficulty due to this special arrangement.
  • the gear chamber 52 is closed off by means of an end cover 54 fastened in an opening 53 in the housing cover 6. By removing the end cover, the gear chamber 52 is easily accessible at any time in order to carry out maintenance or adjustment measures. It is important here that due to the proposed integration and arrangement of the transmission and the design of the housing cover 6 and end cover 54, good accessibility and ease of service with a simple construction is achieved.
  • centrifugal plate 56 connected to the inner rotor 8 and a centrifugal plate 58 connected to the outer rotor 26, by means of which the lubricant supply is reliably ensured. Additional fasteners are not necessary insofar as the centrifugal plate 56 is fixed on the inner rotor 8 or the outer rotor 26 by means of the nut 46 already mentioned and the centrifugal plate 58 is fixed by means of the screws 40.
  • a line 60 opens into the gear chamber 52 and leads into the intake port is guided and serves to equalize the pressure. In this way, pressure build-up is expediently prevented in the gear chamber 52, as a result of which lubricant could otherwise be pressed into the work spaces.
  • the shaft 12 is passed through the end cover 54, the gear chamber 52 being sealed by means of a shaft seal.
  • Another unit for example the alternator of a motor vehicle, can be connected to the shaft journal protruding beyond the end cover 54.
  • the outer rotor 26 has a piston ring 68 at each of its two ends, which bear against the cylindrical inner surface 70 of the housing 2. It is also essential that, as seen from the working spaces or the inner rotor 8, an annular groove 72 is arranged in each case in front of the piston rings 68 in the outer surface of the outer rotor 26. A non-uniform loading of the piston ring 68 is avoided by these two ring grooves 72. In this respect, the narrow annular gap between the outer rotor 26 and the inner surface 70 of the housing, which exists axially between the working spaces and the annular groove, is also important in order to avoid an impermissible pressure loss between the working spaces.
  • FIG. 2 shows a radial section along section line II according to FIG. 1, the suction nozzle 62 with the inlet opening 63 and the pressure nozzle 65 with the outlet opening 64 now being recognizable.
  • the above-described line 60 opens into the suction port 62.
  • the line 60 shown here externally outside the housing 2 can also be integrated directly into the housing 2 in the context of this invention and, for example, be formed by a bore in a correspondingly thickened wall of the housing is arranged.
  • the inner rotor 8 is connected directly to the shaft 12. This can be achieved in particular by composite casting, the inner rotor 8 being cast around the shaft 12 previously produced. This one-piece construction of inner rotor 8 and shaft 12 leads to a not inconsiderable simplification of assembly.
  • the three segments or engaging parts 34 and the three work spaces 66 are clearly visible here.
  • the rotor and engaging parts 34 are connected on the drive side to the rotor disk explained above in one piece.
  • the recesses located between the segments, which define the work spaces, are created by machining in one piece, which ensures exact dimensional accuracy.
  • the engagement parts 9 of the inner rotor 8 and also the segments of the outer rotor 26 are expediently designed as hollow bodies in order to reduce the mass.
  • FIG. 3 shows an enlarged view of the inner rotor 8, which has a profiling or longitudinal grooves 74 running in the axial direction on its surface.
  • the tips of this profiling projecting above the surface are removed or bent. An optimal seal between the inner rotor 8 and the outer rotor and consequently the working spaces is ensured.
  • FIG. 4 shows a section through an embodiment of the rotary piston machine in accordance with the section line IV, the suction port 62 and the pressure port 65 being cut and the housing 2 being partially visible in a top view.
  • a valve 76 and a return line 78 are provided between the pressure port 65 and the suction port 62 in order to enable a return from the pressure port to the suction port in certain operating states.
  • a valve body 82 is guided in a valve cover 80 and is pressed by means of a spring 84 onto the valve seat 86 which is advantageously provided on the housing 2.
  • the valve 76 is expediently integrated into this valve cover 80, which is firmly connected to the housing 2 via a seal 88.
  • the valve cover 80 also contains the return line 78, through which air can flow back into the suction port 62 if the pressure in the pressure port 65 is too high.
  • FIG. 5 shows a section through a special embodiment of the valve 76.
  • This valve is not only for the boost pressure limitation in the full-load range, as in the embodiment according to FIG. 4 but also trained for partial load control.
  • the valve housing 90 contains a pressure channel 92 and a suction channel 94, between which the return line 78 is present.
  • the pressure channel 92 leads to the pressure port 65 and the suction channel 94 leads to the suction port 62 of the housing 2 of the rotary piston machine explained above.
  • the housing 90 can be connected to the housing of the rotary lobe machine in accordance with the valve cover explained with reference to FIG. 4.
  • the valve contains the first valve body 82, which is provided for boost pressure control.
  • This first valve body 82 is arranged in a second valve body 96 so as to be displaceable in the direction of arrow 98.
  • the second valve body 96 is used for partial load control and is likewise arranged in the housing 90 so as to be displaceable in the direction of the arrow 98.
  • the first valve body 82 is supported by means of the spring 84, a plate 100 and an adjusting screw 102 and a cover 104 which is screwed to the second valve body 96.
  • the spring preload of the spring 84 is changed and thus the maximum boost pressure at which the valve body 82 can be moved against the spring force in the full-load range is set.
  • the second valve body 96 contains an inlet opening 106 and one or more lateral outlet openings 108. According to the invention, with the valve combined in this way, the inlet opening 106 can be blocked off with respect to the outlet opening 108 in accordance with the position of the first valve body 82 shown.
  • the second valve body 96 is shown in the position which it assumes when the engine to be charged is idling. Pressure channel 92 and suction channel 94 are connected to one another via the partial load opening 114 and the engine can operate in suction mode.
  • the partial load valve or the valve body 96 can be controlled according to the invention depending on the position of the accelerator pedal of the engine. As will be explained below, the partial load valve can be actuated mechanically, for example by means of a cable pull. Furthermore, the control can also be done pneumatically via the boost pressure, hydraulically or electrically.
  • a shaft 110 is provided, which is rotatably mounted about an axis perpendicular to the drawing plane in a manner not shown here.
  • a cable is guided on this shaft, which is connected directly to the accelerator cable or accelerator pedal for controlling the engine.
  • the partial load valve 96 is expediently controlled in such a way that the valve body 96 is not adjusted for an accelerator pedal travel in the range from 0 to 2/3.
  • the partial load opening 114 present between the valve seat 112 and the second valve body 96 is, as shown, opened in the area mentioned and the engine operates in suction mode.
  • the partial load opening 114 is expediently closed continuously.
  • the connection between the pressure channel 92 and the suction channel 94 is closed by means of the second valve body 96. If the boost pressure present in the pressure channel 92 then exceeds the maximum boost pressure set via the boost pressure spring 84 by means of the adjusting screw 102, the first valve body 82 is moved against the biasing force of the spring 84. The air can now flow from the pressure channel 92 through the inlet opening 106 to the outlet openings 108 and via the return line 78 into the suction channel 94.
  • the combination of partial load control and boost pressure control with valve 76 ensures on the one hand a reduction in consumption in the partial load range and an effective boost pressure limitation in the full load range of the engine.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Hydraulic Motors (AREA)
  • Reciprocating Pumps (AREA)
  • Compressor (AREA)
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  • Crushing And Pulverization Processes (AREA)

Abstract

An internal axis rotary piston machine containing in a housing (2), an outer rotor (26), with which an inner rotor (8) having n engagement parts (9) is in meshing engagement, there being n+1 recesses between engagement parts (34) of the outer rotor (26). The inner rotor (8) and outer rotor (26) rotate uniformly at a speed ratio of (n+1):n. There is contact of the tooth-flank type between inside faces of the outer rotor (26) and outside faces of the inner rotor (8) such that working spaces (66) are formed and move past inlet and outlet orifices (63, 64) of the housing (2). The rotary piston machine is designed in such a way that cost-effective production can be achieved while assuring a simple construction. To achieve this, it is proposed that the housing (2) should have, on the drive side, a bottom (4) formed in one piece and should be made pot-shaped. The bottom (4) has an outer face for a bearing (30) of the outer rotor (26), especially on a ring (28) extending axially into the end of the outer rotor (6).

Description

Die Erfindung bezieht sich auf eine Drehkolbenmaschine gemäß den im Oberbegriff des patentanspruchs 1 angegebenen Merkmalen.The invention relates to a rotary piston machine according to the features specified in the preamble of patent claim 1.

Aus dem Dokument DE-C-547 826 ist eine derartige innenachsige Drehkolbenmaschine bekannt, deren Außenrotor und Innenrotor miteinander in Kämmeingriff stehen. Der Außenrotor wird von dem Gehäuse umschlossen und ist ebenso wie der Innenrotor in dem topfförmig ausgebildeten Gehäuse drehbar gelagert. Auf der Antriebsseite enthält der Boden des Gehäuses einen Ring zur Aufnahme eines Lagers des Außenrotors, während auf der dem Boden abgewandten Seite in einem Getrieberaum ein Getriebe zur Antriebsverbindung von Innenrotor und Außenrotor vorgesehen ist. In dem genannten Dokument ist das Gehäuse nur schematisch in der Weise dargestellt, als ob es aus einem einzigen Stück bestehen würde. Zur praktisch realisierbaren Konstruktion des Gehäuses, um insbesondere die Rotoren und Lager einbauen zu können, kann dem Dokument kein weiterer Hinweis entnommen werden. Der Innenrotor ist exzentrisch zur Drehachse des Außenrotors gelagert und besitzt drei Eingriffsteile, welche in vier Ausnehmungen des Außenrotors entsprechend der momentanen Drehstellung eingreifen können. Um die Arbeitsräume, deren Volumen entsprechend der Drehstellung des Außenrotors und Innenrotors veränderbar ist, voneinander funktionssicher abzudichten, ist ein hoher Fertigungsaufwand notwendig und eine Verdichtung konnte früher nur dann erreicht werden, wenn das zu fördernde Medium selbst als Dichtungsmittel geeignet war.From document DE-C-547 826, such an inner-axis rotary lobe machine is known, the outer rotor and inner rotor of which mesh with one another. The outer rotor is enclosed by the housing and, like the inner rotor, is rotatably mounted in the cup-shaped housing. On the drive side, the bottom of the housing contains a ring for receiving a bearing of the outer rotor, while on the side facing away from the bottom, a gear is provided in a gear space for the drive connection of the inner rotor and outer rotor. In the cited document, the housing is shown only schematically, as if it were made of one piece. To the practically feasible construction of the housing in order In particular, to be able to install the rotors and bearings, no further information can be found in the document. The inner rotor is mounted eccentrically to the axis of rotation of the outer rotor and has three engagement parts which can engage in four recesses in the outer rotor in accordance with the current rotational position. In order to reliably seal the working spaces, the volume of which can be changed in accordance with the rotational position of the outer rotor and inner rotor, a high level of manufacturing effort is necessary and compression could previously only be achieved if the medium to be conveyed was itself suitable as a sealant.

Daher wurde aus dem Dokument US-A-4 714 417 eine innenachsige Drehkolbenmaschine bekannt, deren Innenrotor zwei Eingriffsteile und deren Außenrotor entsprechend drei Ausnehmungen aufweisen. Die Innenflächen, welche die Ausnehmungen des Außenrotors begrenzen, sind als plane Flächen ausgebildet, um eine einfache Fertigung zu ermöglichen. Um eine Abwälzbewegung des Innenrotors auf den genannten planen Flächen des Außenrotors zu ermöglichen, muß der Innenrotor eine besondere Geometrie aufweisen, deren Herstellung gleichwohl einen nicht unerheblichen Aufwand erfordert. Besonders problematisch ist darüberhinaus die Ausbildung und Anordnung der Lager von Innenrotor und Außenrotor. Es müssen sehr enge Fertigungstoleranzen eingehalten werden, damit einerseits zu hohe Flächenpressungen vermieden und andererseits keine unerwünscht große Spalte zwischen dem Innenrotor und Außenrotor auftreten können.Therefore, from the document US-A-4 714 417 an inner-axis rotary piston machine is known, the inner rotor of which has two engagement parts and the outer rotor of which has three recesses. The inner surfaces, which delimit the recesses of the outer rotor, are designed as flat surfaces in order to enable simple manufacture. In order to enable a rolling motion of the inner rotor on the aforementioned flat surfaces of the outer rotor, the inner rotor must have a special geometry, the production of which nevertheless requires a not inconsiderable effort. In addition, the formation and arrangement of the bearings is particularly problematic of inner rotor and outer rotor. Very tight manufacturing tolerances have to be observed so that on the one hand excessive surface pressures are avoided and on the other hand no undesirably large gaps can occur between the inner rotor and outer rotor.

Der Erfindung liegt die Aufgabe zugrunde, die innenachsige Drehkolbenmaschine der genannten Art dahingehend weiterzubilden, daß bei einfacher Konstruktion unter Berücksichtigung von zulässigen Fertigungstoleranzen eine hohe Funktionssicherheit und eine lange Lebensdauer erreicht werden.The invention has for its object to further develop the internal-axis rotary lobe machine of the type mentioned in such a way that a high level of functional reliability and a long service life can be achieved with a simple construction taking into account permissible manufacturing tolerances.

Diese Aufgabe erfolgt gemäß den im kennzeichnenden Teil des Patentanspruchs 1 angegebenen Merkmalen.This object is carried out according to the features specified in the characterizing part of patent claim 1.

Die vorgeschlagene Drehkolbenmaschine zeichnet sich durch eine zweckmäßige Konstruktion aus und weist eine hohe Funktionssicherheit und lange Lebensdauer auf. Die Anzahl der hinsichtlich der Fertigungstoleranzen aufeinander abzustimmenden Bauteile ist gering und der Fertigungsaufwand hält sich in Grenzen. Durch die einstückige Anformung des Bodens an das Gehäuse sind in zweckmäßiger Weise die Lager des Innenrotors und des Außenrotors in das Gehäuse integriert, wodurch eine exakte geometrische Zuornung des Innenrotors sowohl bezüglich des Außenrotors als auch bezüglich des Gehäuses gewährleistet wird. Das Lager des Innenrotors ist auf dem Ansatz angeordnet, welcher sich in die Antriebsscheibe hinein erstreckt und kann daher mit einem vergleichsweise geringen Durchmesser ausgebildet werden. Die bei mehrteiliger Ausbildung des Gehäuses und des Bodens erforderlichen Bearbeitungsflächen und entsprechende Fertigungstoleranzen entfallen. Mit geringem Arbeits- und Montageaufwand wird eine hohe Genauigkeit auch bei Fertigung in großen Stückzahlen zuverlässig sichergestellt. Die Anordnung des Getrieberaumes in dem Gehäusedeckel, der das Gehäuse abschließt, ermöglicht eine kompakte Bauweise mit wenigen in ihren Toleranzen aufeinander abzustimmenden Bauteilen. Das Getriebe ist in dem Gehäusedeckel angeordnet, welcher das topfförmige Gehäuse abschließt. Durch eine in den Getrieberaum mündenden Leitung, welche extern außerhalb des Gehäuses angeordnet oder als Längsbohrung in das Gehäuse integriert sein kann, kann in zweckmäßiger Weise ein Druckausgleich zum Saugstutzen erreicht und verhindert werden, daß Schmiermittel in die Arbeitsräume gedrückt wird. Durch die insbesondere mit einem Abschlußdeckel verschließbare Öffnung des Gehäuses hindurch ist das Getriebe zwecks Wartung leicht zugänglich ohne daß die Rotoren ausgebaut werden müssen. Ferner bleibt das mit der Welle des Innenrotors zweckmäßigerweise reibschlüssig verbundene Ritzel des Getriebes im montierten Zustand der Rotoren zugänglich. Der Gehäusedeckel oder gar Rotorlager müssen nicht entfernt werden, um zur exakten Einstellung des Zahnflankenspieles die Drehstellung des Ritzels bezüglich des Innenrotors zu verändern. Nach Abnahme des Abschlußdeckels und Lösen der Verbindung des Ritzels mit der Welle, kann das Ritzel ohne weiteres auf der Welle etwas verdreht werden, um die erforderliche Drehwinkeleinstellung zu erhalten. Bedarfsweise kann durch den Abschlußdeckel auch die Welle herausgeführt sein, um beispielsweise eine Lichtmaschine oder ein anderes Aggregat an die Welle des Innenrotors anzukoppeln. Um eine funktionssichere Schmierung zu gewährleisten ist im Getrieberaum am Innenrotor und/oder am Außenrotor ein Schleuderblech angeordnet. Mittels derartiger Schleuderbleche wird das Schmiermittel zu dem Zahnkranz des Außenrotors bzw. zum Ritzel gefördert.The proposed rotary lobe machine is characterized by an expedient construction and has a high level of functional reliability and a long service life. The number of components to be coordinated with respect to the manufacturing tolerances is small and the manufacturing effort is limited. Due to the one-piece molding of the base on the housing, the bearings of the inner rotor and of the outer rotor are expediently integrated into the housing, as a result of which an exact geometric allocation of the inner rotor is both is guaranteed with respect to the outer rotor as well as with respect to the housing. The bearing of the inner rotor is arranged on the extension which extends into the drive disk and can therefore be designed with a comparatively small diameter. The machining surfaces and corresponding manufacturing tolerances that are required in the case of a multi-part construction of the housing and the bottom are eliminated. With little work and assembly effort, high accuracy is reliably ensured even when manufacturing in large quantities. The arrangement of the gearbox in the housing cover, which closes the housing, enables a compact design with a few components to be coordinated in terms of their tolerances. The gearbox is arranged in the housing cover, which closes the cup-shaped housing. A line opening into the gear chamber, which can be arranged externally outside the housing or can be integrated as a longitudinal bore in the housing, can expediently equalize the pressure to the suction nozzle and prevent lubricant from being pressed into the working spaces. Through the opening of the housing, which can be closed in particular with an end cover, the gear is easily accessible for maintenance without having to remove the rotors. Furthermore, the pinion of the gearbox expediently connected to the shaft of the inner rotor remains accessible in the assembled state of the rotors. The housing cover or even rotor bearings do not have to be removed in order to change the rotational position of the pinion with respect to the inner rotor for the exact setting of the tooth flank play. After removing the end cover and loosening the connection of the pinion with the shaft, the pinion can easily be turned on the shaft to obtain the required angle of rotation setting. If necessary, the shaft can also be led out through the end cover, for example to couple an alternator or another unit to the shaft of the inner rotor. To ensure reliable lubrication, a centrifugal plate is arranged in the gearbox on the inner rotor and / or on the outer rotor. By means of such centrifugal sheets, the lubricant is conveyed to the ring gear of the outer rotor or to the pinion.

Schließlich ist in einer besonderen Ausgestaltung der Erfindung zwischen dem Druckstutzen und dem Saugstutzen ein Umluftventil angeordnet, das in bestimmten Betriebszuständen eine Regelung durch Rückführung der Luft vom Druckstutzen zum Saugstutzen ermöglicht. Dieses Ventil kann zur Ladedruckregelung dienen und zweckmäßig in Kombination ferner zur Teillastregelung vorgesehen sein. Ein derartiges Ventil löst die Aufgabe einerseits eine Verbrauchsreduzierung im Teillastbereich durch eine Teillastregelung und andererseits eine Ladedruckbegrenzung im Vollastbereich durch Ladedruckregelung zu erhalten. Dieses Ventil wird zweckmäßig bei der vorstehend beschriebenen Drehkolbenmaschine gemäß der eingangs erläuterten US-PS 47 14 417 vorgesehen. Ferner kann das in zweckmäßiger Weise kombinierte Ventil auch bei anderen Motoren, und zwar insbesondere bei Kraftfahrzeugmotoren zur Aufladung vorgesehen werden. Der von der Maschine geförderte Luftmassenstrom wird bedarfsweise ganz oder teilweise der Saugseite zugeführt, wobei die beiden Ventilkomponenten zweckmäigerweise in einem gemeinsamen Gehäuse untergebracht werden.Finally, in a special embodiment of the invention, a recirculation valve is arranged between the pressure port and the suction port, which, in certain operating states, enables regulation by returning the air from the pressure port to the suction port. This valve can be used for boost pressure control and can also be advantageously used in combination for partial load control. A valve of this type solves the task of reducing consumption in the part-load range by means of part-load control and, on the other hand, limiting the boost pressure in the full-load range by boost pressure control. This valve is expediently provided in the above-described rotary piston machine according to the US Pat. No. 4,714,417 explained at the outset. Furthermore, the suitably combined valve can also be provided for charging in other engines, in particular in automotive engines. The air mass flow conveyed by the machine is fed wholly or in part to the suction side as required, the two valve components being expediently housed in a common housing.

Im Leerlaufbetrieb das mit der Drehkolbenmaschine aufzuladenden Motors ist das zur Teillastregelung vorgesehene Ventil geöffnet und der Motor arbeitet im Saugbetrieb. Mit zunehmender Belastung erfolgt in einem vorgebbaren Bereich ein zweckmäßig kontinuierliches Schließen des Teillastventils und der Motor wird mittels der Drehkolbenmaschine in der erforderlichen Weise aufgeladen. Im Vollastbereich öffnet bei Erreichen eines einstellbaren maximalen Ladedrucks das für die Ladedruckregelung vorgesehene Ventil. Bei Reduzierung der Belastung laufen diese Vorgänge in umgekehrter Reihenfolge ab. Durch Integration des Ventilgehäuses in das Gehäuse wird eine funktionssichere Konstruktion gewährleistet sowie der benötigte Einbauraum unwesentlich vergrößert, wobei der Bearbeitungsaufwand verringert wird. Das Umluftventil ist in einem Deckel angeordnet, der mit dem Gehäuse dicht verbunden ist und vorteilhaft die Ventilführung sowie die Rückführleitung aufweist. Das vorgeschlagene Ventil erfordert einen geringen Platz- und Gewichtsbedarf, was vor allem bei Kraftfahrzeugmotoren von besonderer Bedeutung ist.When the engine to be charged with the rotary lobe engine is idling, the valve intended for partial load control is open and the engine is operating in suction mode. As the load increases, the partial load valve expediently closes continuously in a predeterminable range and the motor is charged in the required manner by means of the rotary piston machine. In the full load range, the valve provided for the boost pressure control opens when an adjustable maximum boost pressure is reached. When the load is reduced, these processes take place in reverse order. By integrating the valve housing into the housing, a functionally reliable construction is ensured and the installation space required is increased insignificantly, the processing effort being reduced. The air recirculation valve is arranged in a cover which is tightly connected to the housing and advantageously has the valve guide and the return line. The proposed valve requires a small amount of space and weight, which is particularly important in motor vehicle engines.

Die Erfindung wird nachfolgend anhand der in der Zeichnung dargestellten Ausführungsbeispiele näher erläutert. Es zeigen:

Fig. 1
Einen axialen Schnitt durch die Drehkolbenmaschine mit topfförmigem Gehäuse,
Fig. 2
einen Schnitt entlang Schnittlinie II,
Fig. 3
vergrößert den Ausschnitt III gemäß Fig. 2,
Fig. 4
einen Schnitt entsprechend Schnittlinie IV gemäß Figur 1 durch eine besondere Ausgestaltung mit einem Ventil zwischen Saug- und Druckkanal,
Fig. 5
einen Schnitt durch ein im Prinzip dargestelltes Ventil, das sowohl zur Teillast- als auch Ladedruckregelung ausgebildet ist.
The invention is explained in more detail below with reference to the exemplary embodiments shown in the drawing. Show it:
Fig. 1
An axial section through the rotary lobe machine with a pot-shaped housing,
Fig. 2
a section along section line II,
Fig. 3
enlarges section III according to FIG. 2,
Fig. 4
2 shows a section according to section line IV according to FIG. 1 through a special configuration with a valve between the suction and pressure channels,
Fig. 5
a section through a valve shown in principle, which is designed for both partial load and boost pressure control.

Figur 1 zeigt in einem axialen Längsschnitt die innenachsige Drehkolbenmaschine mit einem topfförmigen Gehäuse 2, das einen Boden 4 aufweist und am anderen axialen Ende mit einem einzigen Gehäusedeckel 6 abgeschlossen ist. Im Inneren des Gehäuses 2 ist ein Innenrotor 8 angeordnet, der um eine Achse 10 mittels einer Welle 12 drehbar gelagert ist, die durch den Boden 4 herausgeführt ist. Zur Lagerung des Innenrotors 8 ist in einem Ansatz 14 des Bodens 4 ein Lager 16 angeordnet, das zweckmäßig als ein kombiniertes Axial-Radiallager ausgebildet ist. Auf der anderen Seite des Innenrotors 8 ist im Gehäusedeckel 6 ein zweites Lager 18 angeordnet, welches bevorzugt als ein Nadellager ausgebildet ist. Das im Ansatz 14 vorgesehene Lager 16 ist von einer topfartig ausgebildeten Riemenscheibe 20 umgeben, die im wesentlichen in der gleichen Radialebene wie das genannte Lager 16 liegt und mit der Welle 12 drehfest verbunden ist. Beim Antrieb des Innenrotors 8 mittels eines Riemenzuges wird folglich ein auf die Welle 12 und das Lager 16 einwirkendes Biegemoment praktisch vermieden. Der Innenrotor 8 kann aus Kunststoff oder aus Leichtmetall bestehen und ist, insbesondere durch Verbundguß, direkt mit der Welle 12 verbunden. Diese einstückige Bauweise gewährleistet eine nicht unerhebliche Montagevereinfachung. Die Festlegung des Lagers 16 und der Riemenscheibe 20 auf der Welle 12 erfolgt mittels einer auf einem Gewinde am Wellenende aufgeschraubten Mutter 22, wobei mittels einer Distanzhülse 24 die Abstützung am Innenrotor 8 erfolgt.Figure 1 shows an axial longitudinal section of the inner-axis rotary lobe machine with a cup-shaped housing 2, which has a bottom 4 and is closed at the other axial end with a single housing cover 6. An inner rotor 8 is arranged in the interior of the housing 2 and is rotatably mounted about an axis 10 by means of a shaft 12 which is led out through the base 4. To mount the inner rotor 8, a bearing 16 is arranged in a shoulder 14 of the base 4, which bearing is expediently designed as a combined axial / radial bearing. On the other side of the inner rotor 8, a second bearing 18 is arranged in the housing cover 6, which is preferably designed as a needle bearing. The bearing 16 provided in the projection 14 is surrounded by a pot-shaped pulley 20 which lies essentially in the same radial plane as the bearing 16 mentioned and is connected to the shaft 12 in a rotationally fixed manner. When the inner rotor 8 is driven by means of a belt tension, a bending moment acting on the shaft 12 and the bearing 16 is consequently practically avoided. The inner rotor 8 can be made of plastic or light metal and is connected directly to the shaft 12, in particular by composite casting. This one-piece construction ensures a not inconsiderable simplification of assembly. The bearing 16 and the pulley 20 are fixed on the shaft 12 by means of a nut 22 screwed onto a thread at the shaft end, the support on the inner rotor 8 being carried out by means of a spacer sleeve 24.

Im Inneren des Gehäuses 2 ist ferner ein Außenrotor 26 angeordnet, wobei mit dem Innenrotor 8 in bekannter Weise Arbeitsräume gebildet werden. Die insoweit maßgebenden Prinzipien und die Funktionsweise ergeben sich aus der eingangs genannten US-PS 47 14 417, auf welche hier ausdrücklich Bezug genommen wird. Der Boden 4 des Gehäuses 2 weist einen sich axial in das Ende des Außenrotors 26 erstreckenden Ring 28 auf, auf dessen Außenflächen das Lager 30 des Außenrotors 26 angeordnet ist. Bei dieser Ausführungsform weist der Außenrotor 26 drei über den Umfang verteilte Eingriffsteile 34 auf, welche einstückig mit einer Rotorscheibe 36 ausgebildet sind. Wesentlich ist ferner die axial beabstandete Anordnung des Lagers 30 in dem Ring 28 bezüglich des Lagers 16 vom Innenrotor 8, so daß das Lager 30 des Außenrotors 26 einen vergleichsweise geringen Durchmesser aufweist.In addition, an outer rotor 26 is arranged in the interior of the housing 2, work spaces being formed in a known manner with the inner rotor 8. The relevant principles and the mode of operation result from the aforementioned US Pat. No. 4,714,417, to which reference is expressly made here. The bottom 4 of the housing 2 has a ring 28 extending axially into the end of the outer rotor 26, on the outer surfaces of which the bearing 30 of the outer rotor 26 is arranged. In this embodiment, the outer rotor 26 has three engagement parts 34 distributed over the circumference, which are in one piece are formed with a rotor disk 36. Also important is the axially spaced arrangement of the bearing 30 in the ring 28 with respect to the bearing 16 from the inner rotor 8, so that the bearing 30 of the outer rotor 26 has a comparatively small diameter.

Am anderen axialen Ende weist der Außenrotor 26 einen Ring 38 auf, welcher mit den Eingriffsteilen 34 mittels Schrauben 40 verbunden ist. Das zweite Lager 32 für den Außenrotor 26 ist erfindungsgemäß innerhalb des Rotorringes 38 auf dem Gehäusedeckel 6 angeordnet. Mittels der gleichen Schrauben 40 ist zweckmäßig ein innenverzahntes Rad 42 mit dem Außenrotor 26 verbunden. Das innenverzahnte Rad 42 kämmt mit einem auf der Welle 12 des Innenrotors 8 reibschlüssig angeordneten Ritzel 44. Das Ritzel 44 ist mittels einer Mutter 46 über eine Lagerhülse 48 gegen einen Wellenbund 50 verspannt. Das Flankenspiel des Getriebes und die Drehwinkellage von Innenrotor 8 und Außenrotor 26 können aufgrund dieser besonderen Anordnung ohne Schwiergkeiten eingestellt werden. Der Getrieberaum 52 ist mittels eines in einer Öffnung 53 im Gehäusedeckel 6 befestigten Abschlußdeckels 54 abgeschlossen. Durch Abnahme des Abschlußdeckels ist der Getrieberaum 52 jederzeit ohne weiteres zugänglich, um Wartungs- oder Einstellmaßnahmen durchzuführen. Wesentlich ist hierbei, daß aufgrund der vorgeschlagenen Integration und Anordnung des Getriebes sowie Ausbildung von Gehäusedeckel 6 und Abschlußdeckel 54 eine gute Zugänglichkeit und Servicefreundlichkeit bei einfacher Konstruktion erreicht wird.At the other axial end, the outer rotor 26 has a ring 38 which is connected to the engaging parts 34 by means of screws 40. The second bearing 32 for the outer rotor 26 is arranged according to the invention within the rotor ring 38 on the housing cover 6. By means of the same screws 40, an internally toothed wheel 42 is expediently connected to the outer rotor 26. The internally toothed wheel 42 meshes with a pinion 44 which is arranged on the shaft 12 of the inner rotor 8 in a frictionally engaged manner. The pinion 44 is braced against a shaft collar 50 by means of a nut 46 via a bearing sleeve 48. The backlash of the gear and the angular position of the inner rotor 8 and outer rotor 26 can be adjusted without difficulty due to this special arrangement. The gear chamber 52 is closed off by means of an end cover 54 fastened in an opening 53 in the housing cover 6. By removing the end cover, the gear chamber 52 is easily accessible at any time in order to carry out maintenance or adjustment measures. It is important here that due to the proposed integration and arrangement of the transmission and the design of the housing cover 6 and end cover 54, good accessibility and ease of service with a simple construction is achieved.

Im Getrieberaum 52 sind ein mit dem Innenrotor 8 verbundenes Schleuderblech 56 sowie ein mit dem Außenrotor 26 verbundenes Schleuderblech 58 vorgesehen, mittels welchen die Schmiermittelversorgung in zuverlässiger Weise gewährleistet wird. Zusätzliche Befestigungsmittel sind insoweit nicht erforderlich, da daß Schleuderblech 56 mittels der bereits genannten Mutter 46 und das Schleuderblech 58 mittels den Schrauben 40 auf dem Innenrotor 8 bzw. dem Außenrotor 26 festgelegt sind. In den Getrieberaum 52 mündet eine Leitung 60, die in den Saugstutzen geführt ist und zum Druckausgleich dient. Hierdurch wird in zweckmäßiger Weise im Getrieberaum 52 ein Druckaufbau verhindert, aufgrund denen ansonsten Schmiermittel in die Arbeitsräume gedrückt werden könnte. Die Welle 12 ist durch den Abschlußdeckel 54 durchgeführt, wobei mittels einer Wellendichtung der Getrieberaum 52 abgedichtet wird. An dem, über dem Abschlußdeckels 54 hinausragenden Wellenzapfen kann ein anderes Aggregat, beispielsweise die Lichtmaschine eines Kraftfahrzeuges, angeschlossen werden.Provided in the gear chamber 52 are a centrifugal plate 56 connected to the inner rotor 8 and a centrifugal plate 58 connected to the outer rotor 26, by means of which the lubricant supply is reliably ensured. Additional fasteners are not necessary insofar as the centrifugal plate 56 is fixed on the inner rotor 8 or the outer rotor 26 by means of the nut 46 already mentioned and the centrifugal plate 58 is fixed by means of the screws 40. A line 60 opens into the gear chamber 52 and leads into the intake port is guided and serves to equalize the pressure. In this way, pressure build-up is expediently prevented in the gear chamber 52, as a result of which lubricant could otherwise be pressed into the work spaces. The shaft 12 is passed through the end cover 54, the gear chamber 52 being sealed by means of a shaft seal. Another unit, for example the alternator of a motor vehicle, can be connected to the shaft journal protruding beyond the end cover 54.

Zur stirnseitigen Dichtung der Arbeitsräume weist der Außenrotor 26 an seinen beiden Enden jeweils einen Kolbenring 68 auf, welche an der zylindrichen Innenfläche 70 des Gehäuses 2 anliegen. Wesentlich ist ferner, daß, von den Arbeitsräumen bzw. dem Innenrotor 8 gesehen, vor den Kolbenringen 68 jeweils eine Ringnut 72 in der Außenfläche des Außenrotors 26 angeordnet ist. Durch diese beiden Ringnuten 72 wird eine ungleichförmige Belastung des Kolbenringes 68 vermieden. Wesentlich ist insoweit auch der axial zwischen den Arbeitsräumen und der Ringnut vorhandene schmale Ringspalt zwischen Außenrotor 26 und Innenfläche 70 des Gehäuses, um einen unzulässigen Druckverlust zwischen den Arbeitsräumen zu vermeiden.To seal the working spaces on the front side, the outer rotor 26 has a piston ring 68 at each of its two ends, which bear against the cylindrical inner surface 70 of the housing 2. It is also essential that, as seen from the working spaces or the inner rotor 8, an annular groove 72 is arranged in each case in front of the piston rings 68 in the outer surface of the outer rotor 26. A non-uniform loading of the piston ring 68 is avoided by these two ring grooves 72. In this respect, the narrow annular gap between the outer rotor 26 and the inner surface 70 of the housing, which exists axially between the working spaces and the annular groove, is also important in order to avoid an impermissible pressure loss between the working spaces.

Figur 2 zeigt einen radialen Schnitt entlang Schnittlinie II gemäß der Figur 1, wobei nunmehr der Saugstutzen 62 mit der Einlaßöffnung 63 und der Druckstutzen 65 mit der Auslaßöffnung 64 zu erkennen sind. Die oben beschriebene Leitung 60 mündet in den Saugstutzen 62. Die hier extern außerhalb des Gehäuses 2 dargestellte Leitung 60 kann im Rahmen dieser Erfindung auch direkt in das Gehäuse 2 integriert sein und beispielsweise durch eine Bohrung gebildet werden, die in einer entsprechend verdickten Wand des Gehäuses angeordnet ist. Der Innenrotor 8 ist mit der Welle 12 direkt verbunden. Dies kann insbesondere durch Verbundguß realisiert sein, wobei der Innenrotor 8 um die zuvor gefertigte Welle 12 gegossen wird. Diese einstückige Bauweise von Innenrotor 8 und Welle 12 führt zu einer nicht unwesentlichen Montagevereinfachung. Die drei Segmente bzw. Eingriffsteile 34 sowie die drei Arbeitsräume 66 sind hier gut zu erkennen. Die Rotor- und Eingriffsteile 34 sind auf der Antriebsseite mit der oben erläuterten Rotorscheibe zu einem Stück verbunden. Die zwischen den Segmenten befindlichen Ausnehmungen, welche die Arbeitsräume definieren, werden durch Bearbeitung an einem Stück erzeugt, wodurch eine exakte Maßhaltigkeit gewährleistet wird. Die Eingriffsteile 9 des Innenrotosr 8 und ebenso die Segmente des Außenrotors 26 sind zwecks Reduzierung der Masse zweckmäßig als Hohlkörper ausgebildet.FIG. 2 shows a radial section along section line II according to FIG. 1, the suction nozzle 62 with the inlet opening 63 and the pressure nozzle 65 with the outlet opening 64 now being recognizable. The above-described line 60 opens into the suction port 62. The line 60 shown here externally outside the housing 2 can also be integrated directly into the housing 2 in the context of this invention and, for example, be formed by a bore in a correspondingly thickened wall of the housing is arranged. The inner rotor 8 is connected directly to the shaft 12. This can be achieved in particular by composite casting, the inner rotor 8 being cast around the shaft 12 previously produced. This one-piece construction of inner rotor 8 and shaft 12 leads to a not inconsiderable simplification of assembly. The three segments or engaging parts 34 and the three work spaces 66 are clearly visible here. The rotor and engaging parts 34 are connected on the drive side to the rotor disk explained above in one piece. The recesses located between the segments, which define the work spaces, are created by machining in one piece, which ensures exact dimensional accuracy. The engagement parts 9 of the inner rotor 8 and also the segments of the outer rotor 26 are expediently designed as hollow bodies in order to reduce the mass.

In Figur 3 ist vergrößert der Innenrotor 8 dargestellt, welcher auf seiner Oberfläche eine in axialer Richtung verlaufende Profilierung bzw. Längsriefen 74 aufweist. Beim Einlaufen mit dem Außenrotor werden die über die Oberfläche vorstehenden Spitzen dieser Profilierung abgetragen oder auch umgebogen. Eine optimale Abdichtung zwischen dem Innenrotor 8 und dem Außenrotor und folglich der Arbeitsräume wird sichergestellt.FIG. 3 shows an enlarged view of the inner rotor 8, which has a profiling or longitudinal grooves 74 running in the axial direction on its surface. When running in with the outer rotor, the tips of this profiling projecting above the surface are removed or bent. An optimal seal between the inner rotor 8 and the outer rotor and consequently the working spaces is ensured.

Figur 4 zeigt entsprechend der Schnittlinie IV einen Schnitt durch eine Ausführungsform der Drehkolbenmaschine, wobei der Saugstutzen 62 und der Druckstutzen 65 geschnitten sind und das Gehäuse 2 zum Teil in einer Aufsicht zu sehen ist. Zwischen dem Druckstutzen 65 und dem Saugstutzen 62 sind im Rahmen dieser Erfindung ein Ventil 76 und eine Rückführleitung 78 vorgesehen, um bei bestimmten Betriebszuständen eine Rückführung vom Druckstutzen zum Saugstutzen zu ermöglichen. In einem Ventildeckel 80 ist ein Ventilkörper 82 geführt, welcher mittels einer Feder 84 auf den vorteilhaft am Gehäuse 2 vorgesehenen Ventilsitz 86 gedrückt wird. Das Ventil 76 ist zweckmäßig in diesen Ventildeckel 80 integriert, welcher über eine Dichtung 88 fest mit dem Gehäuse 2 verbunden ist. Der Ventildeckel 80 enthält ferner die Rückführleitung 78, durch welche bei einem zu hohen Druck im Druckstutzen 65 Luft in den Saugstutzen 62 zurückströmen kann.FIG. 4 shows a section through an embodiment of the rotary piston machine in accordance with the section line IV, the suction port 62 and the pressure port 65 being cut and the housing 2 being partially visible in a top view. Within the scope of this invention, a valve 76 and a return line 78 are provided between the pressure port 65 and the suction port 62 in order to enable a return from the pressure port to the suction port in certain operating states. A valve body 82 is guided in a valve cover 80 and is pressed by means of a spring 84 onto the valve seat 86 which is advantageously provided on the housing 2. The valve 76 is expediently integrated into this valve cover 80, which is firmly connected to the housing 2 via a seal 88. The valve cover 80 also contains the return line 78, through which air can flow back into the suction port 62 if the pressure in the pressure port 65 is too high.

Fig. 5 zeigt einen Schnitt durch eine besondere Ausgestaltung des Ventils 76. Dieses Ventil ist nicht nur wie bei der Ausführungsform gemäß Fig. 4 zur Ladedruckbegrenzung im Vollastbereich sondern auch für eine Teillastregelung ausgebildet. Das Ventilgehäuse 90 enthält einen Druckkanal 92 und einen Saugkanal 94, zwischen welchen die Rückführleitung 78 vorhanden ist. Der Druckkanal 92 führt zu dem Druckstutzen 65 und der Saugkanal 94 führt zu dem Saugstutzen 62 des vorstehend erläuterten Gehäuses 2 der Drehkolbenmaschine. Im Rahmen der Erfindung kann das Gehäuse 90 entsprechend dem anhand der Fig. 4 erläuterten Ventildeckel mit dem Gehäuse der Drehkolbenmaschine verbunden sein. Das Ventil enthält den ersten Ventilkörper 82, der zur Ladedruckregelung vorgesehen ist. Dieser erste Ventilkörper 82 ist in einem zweiten Ventilkörper 96 in Richtung des Pfeiles 98 verschiebbar angeordnet. Der zweite Ventilkörper 96 dient zur Teillastregelung und ist im Gehäuse 90 gleichfalls in Richtung des Pfeiles 98 verschiebbar angeordnet. Der erste Ventilkörper 82 ist mittels der Feder 84, einer Platte 100 und eine Stellschraube 102 und einem Deckel 104 abgestützt, der mit dem zweiten Ventilkörper 96 verschraubt ist. Mittels der Stellschraube 102 wird die Federvorspannung der Feder 84 verändert und damit der maximale Ladedruck, bei welchem im Vollastbereich der Ventilkörper 82 entgegen der Federkraft bewegt werden kann, eingestellt. Der zweite Ventilkörper 96 enthält eine Eintrittsöffnung 106 und eine oder mehrere seitliche Austrittsöffnungen 108. Erfindungsgemäß kann mit dem derart kombinierten Ventil gemäß der dargestellten Position des ersten Ventilkörpers 82 die Eintrittsöffnung 106 bezüglich der Austrittsöffnung 108 abgesperrt werden.FIG. 5 shows a section through a special embodiment of the valve 76. This valve is not only for the boost pressure limitation in the full-load range, as in the embodiment according to FIG. 4 but also trained for partial load control. The valve housing 90 contains a pressure channel 92 and a suction channel 94, between which the return line 78 is present. The pressure channel 92 leads to the pressure port 65 and the suction channel 94 leads to the suction port 62 of the housing 2 of the rotary piston machine explained above. In the context of the invention, the housing 90 can be connected to the housing of the rotary lobe machine in accordance with the valve cover explained with reference to FIG. 4. The valve contains the first valve body 82, which is provided for boost pressure control. This first valve body 82 is arranged in a second valve body 96 so as to be displaceable in the direction of arrow 98. The second valve body 96 is used for partial load control and is likewise arranged in the housing 90 so as to be displaceable in the direction of the arrow 98. The first valve body 82 is supported by means of the spring 84, a plate 100 and an adjusting screw 102 and a cover 104 which is screwed to the second valve body 96. By means of the adjusting screw 102, the spring preload of the spring 84 is changed and thus the maximum boost pressure at which the valve body 82 can be moved against the spring force in the full-load range is set. The second valve body 96 contains an inlet opening 106 and one or more lateral outlet openings 108. According to the invention, with the valve combined in this way, the inlet opening 106 can be blocked off with respect to the outlet opening 108 in accordance with the position of the first valve body 82 shown.

Der zweite Ventilkörper 96 ist in der Position dargestellt, die er im Leerlaufbetrieb des aufzuladenden Motors einnimmt. Druckkanal 92 und Saugkanal 94 stehen über die Teillastöffnung 114 miteinander in Verbindung und der Motor kann im Saugbetrieb arbeiten. Das Teillastventil bzw. der Ventilkörper 96 kann erfindungsgemäß in Abhängigkeit der Stellung des Gaspedales des Motors gesteuert werden. Die Ansteuerung des Teillastventils kann, wie nachfolgend zu erläutern ist, mechanisch, beispielsweise über einen Seilzug erfolgen. Desweiteren kann die Ansteuerung auch pneumatisch über den Ladedruck, hydraulisch oder elektrisch erfolgen. Zur mechanischen Ansteuerung ist eine Welle 110 vorgesehen, die in hier nicht weiter dargestellter Weise um eine zur Zeichenebene senkrechte Achse drehbar gelagert ist. Auf diese Welle ist ein Seilzug geführt, der direkt mit dem Gaszug bzw. dem Gaspedal zur Steuerung des Motors verbunden ist. Die Steuerung des Teillastventiles 96 erfolgt zweckmäßig in der Weise, daß für einen Gaspedalweg im Bereich von 0 bis 2/3 keine Verstellung des Ventilkörpers 96 erfolgt. Die zwischen dem Ventilsitz 112 und dem zweiten Ventilkörper 96 vorhandene Teillastöffnung 114 ist, wie dargestellt, in dem genannten Bereich geöffnet und der Motor arbeitet im Saugbetrieb. Bei einer weiteren Betätigung des Gaspedales und damit des Seilzuges erfolgt eine Drehung der Welle 110 und des mit dieser drehfest verbundenen Hebels 116 in Richtung des Pfeiles 118. Über das freie Ende 120 des Hebels 116, der zweckmäßig über eine hier nicht dargestellte Rolle am Deckel 104 anliegt, wird der zweite Ventilkörper 96 nunmehr in Richtung auf den Ventilsitz 112 bewegt. In dem Bereich von zwei Drittel bis drei Drittel des Gaspedalweges erfolgt zweckmäßig ein kontinuierliches Schließen der Teillastöffnung 114. Die Verbindung zwischen dem Druckkanal 92 und dem Saugkanal 94 wird mittels des zweiten Ventilkörpers 96 geschlossen. Überschreitet dann im Vollastbetrieb der im Druckkanal 92 anstehende Ladedruck den über die Ladedruckfeder 84 mittels der Stellschraube 102 eingestellten maximalen Ladedruck, so wird der erste Ventilkörper 82 entgegen der Vorspannkraft der Feder 84 bewegt. Die Luft kann nunmehr vom Druckkanal 92 durch die Eintrittsöffnung 106 zu den Austrittsöffnungen 108 und über die Rückführleitung 78 in den Saugkanal 94 strömen. Durch die erfindungsgemäße Kombination von Teillastregelung und Ladedruckregelung mit dem Ventil 76 wird einerseits im Teillastbereich eine Verbrauchsreduzierung und im Vollastbereich des Motors eine effektive Ladedruckbegrenzung gewährleistet.The second valve body 96 is shown in the position which it assumes when the engine to be charged is idling. Pressure channel 92 and suction channel 94 are connected to one another via the partial load opening 114 and the engine can operate in suction mode. The partial load valve or the valve body 96 can be controlled according to the invention depending on the position of the accelerator pedal of the engine. As will be explained below, the partial load valve can be actuated mechanically, for example by means of a cable pull. Furthermore, the control can also be done pneumatically via the boost pressure, hydraulically or electrically. For mechanical control, a shaft 110 is provided, which is rotatably mounted about an axis perpendicular to the drawing plane in a manner not shown here. A cable is guided on this shaft, which is connected directly to the accelerator cable or accelerator pedal for controlling the engine. The partial load valve 96 is expediently controlled in such a way that the valve body 96 is not adjusted for an accelerator pedal travel in the range from 0 to 2/3. The partial load opening 114 present between the valve seat 112 and the second valve body 96 is, as shown, opened in the area mentioned and the engine operates in suction mode. When the accelerator pedal and thus the cable pull are actuated further, the shaft 110 and the lever 116 connected to it in a rotationally fixed manner are rotated in the direction of the arrow 118 is applied, the second valve body 96 is now moved in the direction of the valve seat 112. In the range from two thirds to three thirds of the accelerator pedal travel, the partial load opening 114 is expediently closed continuously. The connection between the pressure channel 92 and the suction channel 94 is closed by means of the second valve body 96. If the boost pressure present in the pressure channel 92 then exceeds the maximum boost pressure set via the boost pressure spring 84 by means of the adjusting screw 102, the first valve body 82 is moved against the biasing force of the spring 84. The air can now flow from the pressure channel 92 through the inlet opening 106 to the outlet openings 108 and via the return line 78 into the suction channel 94. The combination of partial load control and boost pressure control with valve 76 according to the invention ensures on the one hand a reduction in consumption in the partial load range and an effective boost pressure limitation in the full load range of the engine.

BezugszeichenlisteReference symbol list

22nd
Gehäusecasing
44th
Bodenground
66
GehäusedeckelHousing cover
88th
InnenrotorInner rotor
99
Eingriffsteil von 8Engagement part of 8
1010th
Achse von 8Axis of 8
1212
Wellewave
1414
Ansatz in 4Approach in 4
16, 1816, 18
Lager von 8Stock of 8
2020th
RiemenscheibePulley
2222
Muttermother
2424th
DistanzhülseSpacer sleeve
2626
AußenrotorOuter rotor
2828
Ringring
30, 3230, 32
Lager für 26Bearings for 26
3333
Achse von 26Axis of 26
3434
Eingriffsteil von 26Engagement part of 26
3636
RotorscheibeRotor disc
3838
RotorringRotor ring
4040
Schraubescrew
4242
innenverzahntes Radinternally toothed wheel
4444
Ritzelpinion
4646
Muttermother
4848
LagerhülseBearing sleeve
5050
WellenbundWave collar
5252
GetrieberaumGearbox
5353
Öffnungopening
5454
AbschlußdeckelEnd cover
56, 5856, 58
SchleuderblechSlingshot
6060
Leitungmanagement
6262
SaugstutzenSuction port
6363
EinlaßöffnungInlet opening
6464
AuslaßöffnungOutlet opening
6565
DruckstutzenDischarge nozzle
6666
Arbeitsraumworking space
6868
KolbenringPiston ring
7070
InnenflächeInner surface
7272
RingnutRing groove
7474
ProfilierungProfiling
7676
VentilValve
7878
RückführleitungReturn line
8080
VentildeckelValve cover
8282
erster Ventilkörperfirst valve body
8484
Federfeather
8686
VentilsitzValve seat
8888
Dichtungpoetry
9090
VentilgehäuseValve body
9292
DruckkanalPressure channel
9494
SaugkanalSuction channel
9696
zweiter Ventilkörpersecond valve body
9898
Pfeilarrow
100100
Platteplate
102102
StellschraubeSet screw
104104
Deckelcover
106106
EintrittsöffnungEntrance opening
108108
AustrittsöffnungOutlet opening
110110
Wellewave
112112
VentilsitzValve seat
114114
TeillastöffnungPartial load opening
116116
Hebellever
118118
Pfeilarrow
120120
EndeThe End

Claims (11)

  1. An internal-axis rotary piston engine with meshing engagement between an outer rotor (26) surrounded by a housing (2) and having N+1 recesses arranged between engaging parts (34) and an inner rotor (8) having n engaging parts which rotate uniformly at a speed ratio of (N+1):n when there is tooth-flanked contact between inner side faces of the outer rotor (26) and side faces of the inner rotor (8) mounted on bearings, so that working spaces (66) are formed in the recesses of the outer rotor (26) and move past an inlet orifice (63) and an outlet orifice (64) in the housing, wherein the housing (2) is of a pot-shaped construction and has a base (4) at the drive side having a ring (28) for accommodating a bearing (30) of the outer rotor (26), whilst, moreover, outside the housing (2) is a drive pulley (20) for the inner rotor (8) and, on the side remote from the base (4), in a gear space (52), a gear is provided for forming a driving connection between the inner rotor (8) and outer rotor (26), characterised in that the base (4) is integrally formed on the housing (2), in that the base (4) has an extension (14), projecting into the drive pulley (20), for accommodating a bearing (16) of the inner rotor (8), in that the gear space (52) is contained in a housing cover (6) which closes off the housing, and in that the housing cover (6) has a closable opening (53) through which the gear space (52) is accessible from the outside.
  2. Rotary piston engine according to claim 1, characterised in that a line (60) is provided between the gear space (52) and a suction connection (62) of the housing (2).
  3. Rotary piston engine according to claim 1 or 2, characterised in that the inner rotor (8) is directly connected to a shaft (12), particularly by composite casting.
  4. Rotary piston engine according to one of claims 1 to 3, characterised in that the outer rotor (26) has a piston ring (68) on each of its axial ends and that an annular groove (72) is provided axially between the working spaces and the piston ring (68).
  5. Rotary piston engine according to one of claims 1 to 4, characterised in that the opening (53) is closable by means of a closing cover (54).
  6. Rotary piston engine according to claim 5, characterised in that the shaft (12) of the inner rotor (8) passes through the closing cover (54).
  7. Rotary piston engine according to one of claims 2 to 6, characterised in that, between the suction connection (62) and a pressure connection (65) there is a valve (76) by means of which a connection can be established between the pressure connection (65) and the intake connection (62) or closed off.
  8. Rotary piston engine according to claim 7, characterised in that, connected to the housing (2), is a valve housing (80,90) in which the valve (76) is integrated.
  9. Rotary piston engine according to claim 7 or 8, characterised in that the valve (76) has a first valve body (82) for boost control and a second valve body (96) for partial-load control, the first valve body (82) being displaceably mounted, preferably inside the second valve body (96), in order to close off an inlet opening (106) of the second valve body (96) with respect to its outlet opening (108), or if a desired maximum pressure is exceeded, to open said inlet opening.
  10. Rotary piston engine according to claim 9, characterised in that the first valve body (82) is supported inside the second valve body (96) by means of a spring (84) and a plate (100) which is arranged to be displaceable by means of a set screw (102) in order to adjust the spring tension, and more particularly is supported in a cover (104) which is fixedly connected to the valve body (96).
  11. Rotary piston engine according to claim 9 or 10, characterised in that the second valve body (96) is movable, in the partial load range, more particularly for the range of adjustment of the accelerator pedal of an engine from two thirds to three thirds, in order to close off or, conversely, open up a partial-load opening (114) continuously.
EP88106729A 1987-05-14 1988-04-27 Internal axis rotary piston machine Expired - Lifetime EP0290864B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT88106729T ATE68557T1 (en) 1987-05-14 1988-04-27 INBOARD ROTARY LOBE MACHINE.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3716083 1987-05-14
DE19873716083 DE3716083A1 (en) 1987-05-14 1987-05-14 INNER AXIS ROTARY PISTON

Publications (3)

Publication Number Publication Date
EP0290864A2 EP0290864A2 (en) 1988-11-17
EP0290864A3 EP0290864A3 (en) 1989-07-12
EP0290864B1 true EP0290864B1 (en) 1991-10-16

Family

ID=6327508

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88106729A Expired - Lifetime EP0290864B1 (en) 1987-05-14 1988-04-27 Internal axis rotary piston machine

Country Status (8)

Country Link
US (1) US4943213A (en)
EP (1) EP0290864B1 (en)
CN (1) CN1010793B (en)
AT (1) ATE68557T1 (en)
BR (1) BR8802326A (en)
CS (1) CS324988A3 (en)
DE (2) DE3716083A1 (en)
YU (1) YU92188A (en)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3911540C1 (en) * 1989-04-08 1990-03-29 Aktiengesellschaft Kuehnle, Kopp & Kausch, 6710 Frankenthal, De
DE3911541C1 (en) * 1989-04-08 1990-03-29 Aktiengesellschaft Kuehnle, Kopp & Kausch, 6710 Frankenthal, De
CH685450A5 (en) * 1992-04-01 1995-07-14 Lindau Tech Forsch & Entw Gmbh Internal-axis rotary piston engine.
DE19800002A1 (en) * 1998-01-02 1999-07-08 Linde Ag Hydrostatic unit to drive work machine e.g. for fork lift truck
JP2003269329A (en) * 2002-03-15 2003-09-25 Sanden Corp Compressor for vehicle
ITTV20030089A1 (en) * 2003-06-19 2003-09-17 Orlando Canal MECHANISM FOR GAS-DYNAMICS ROTARY 60 DEGREE VOLUMETRIC ACTION, "GAVARA-60", FOR GENERAL USE AND PARTICULARLY FOR ENDOTERMIC ENGINES
SK6803Y1 (en) 2013-01-06 2014-06-03 Kujovic Jozef Workspace with rotary moving piston
CN105108485A (en) * 2015-09-08 2015-12-02 连云港市天意消防器材有限公司 Fire extinguisher conduit assembly machine

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Publication number Priority date Publication date Assignee Title
EP0178392A1 (en) * 1984-08-21 1986-04-23 Robert Bosch Gmbh Gear machine
WO1987001760A1 (en) * 1985-09-23 1987-03-26 Sundstrand Corporation Hydraulic displacement unit and method of assembly thereof

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DE547826C (en) * 1928-07-27 1932-04-07 Expl Des Procedes Maurice Lebl Gear compressor
US1955799A (en) * 1931-08-24 1934-04-24 Gen Motors Corp Pressure control system for blower-fed two-cycle engines
US2177976A (en) * 1935-08-19 1939-10-31 Brauer Walter Motor
US3139835A (en) * 1962-08-15 1964-07-07 Davey Compressor Co Rotary pump or motor
US4017221A (en) * 1976-02-27 1977-04-12 Caterpillar Tractor Co. Combined unloading and relief valve for pump unloading circuit
DE2844019A1 (en) * 1978-10-09 1980-04-17 Leybold Heraeus Gmbh & Co Kg VACUUM PUMP, ESPECIALLY RUBBER VACUUM PUMP
US4466414A (en) * 1981-07-07 1984-08-21 Nippondenso Co., Ltd. Supercharged internal combustion engine
EP0083491A1 (en) * 1981-12-24 1983-07-13 Concentric Pumps Limited Gerotor pumps
US4502283A (en) * 1982-09-24 1985-03-05 General Motors Corporation Turbocharged engine driven positive displacement blower having a bypass passage
US4722672A (en) * 1983-02-17 1988-02-02 Rinneer Arthur E Hydraulic energy-conversion device
JPS59213984A (en) * 1983-05-20 1984-12-03 Nippon Piston Ring Co Ltd Bearing device in vane type rotary compressor
CH664423A5 (en) * 1984-06-12 1988-02-29 Wankel Felix INNER AXIS ROTARY PISTON.
JPS61223290A (en) * 1985-03-27 1986-10-03 Honda Motor Co Ltd Rotor seal structure in vane pump
US4750867A (en) * 1985-05-09 1988-06-14 Siegfried Hertell Regulating pump
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Publication number Priority date Publication date Assignee Title
EP0178392A1 (en) * 1984-08-21 1986-04-23 Robert Bosch Gmbh Gear machine
WO1987001760A1 (en) * 1985-09-23 1987-03-26 Sundstrand Corporation Hydraulic displacement unit and method of assembly thereof

Also Published As

Publication number Publication date
EP0290864A2 (en) 1988-11-17
EP0290864A3 (en) 1989-07-12
US4943213A (en) 1990-07-24
JPS64303A (en) 1989-01-05
CN1010793B (en) 1990-12-12
DE3716083A1 (en) 1988-11-24
YU92188A (en) 1990-12-31
BR8802326A (en) 1988-12-13
CS324988A3 (en) 1992-08-12
ATE68557T1 (en) 1991-11-15
DE3865516D1 (en) 1991-11-21
CN1030961A (en) 1989-02-08

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