EP2655803B1 - Multi-stage or multi-channel pump, compressor or motor - Google Patents

Multi-stage or multi-channel pump, compressor or motor Download PDF

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Publication number
EP2655803B1
EP2655803B1 EP11767718.7A EP11767718A EP2655803B1 EP 2655803 B1 EP2655803 B1 EP 2655803B1 EP 11767718 A EP11767718 A EP 11767718A EP 2655803 B1 EP2655803 B1 EP 2655803B1
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EP
European Patent Office
Prior art keywords
rotor
toothing
counter
rotary piston
piston machine
Prior art date
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Active
Application number
EP11767718.7A
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German (de)
French (fr)
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EP2655803A2 (en
Inventor
Dieter Amesoeder
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP2655803A2 publication Critical patent/EP2655803A2/en
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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01CROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C3/00Rotary-piston machines or engines with non-parallel axes of movement of co-operating members
    • F01C3/06Rotary-piston machines or engines with non-parallel axes of movement of co-operating members the axes being arranged otherwise than at an angle of 90 degrees
    • F01C3/08Rotary-piston machines or engines with non-parallel axes of movement of co-operating members the axes being arranged otherwise than at an angle of 90 degrees of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F01C3/085Rotary-piston machines or engines with non-parallel axes of movement of co-operating members the axes being arranged otherwise than at an angle of 90 degrees of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing the axes of cooperating members being on the same plane
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01CROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00Rotary-piston machines or engines
    • F01C1/08Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/082Details specially related to intermeshing engagement type machines or engines
    • F01C1/084Toothed wheels
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01CROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C11/00Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type
    • F01C11/002Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of similar working principle
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01CROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10Outer members for co-operation with rotary pistons; Casings

Definitions

  • the present invention relates to a rotary piston machine which operates as a pump, compressor or motor, with a rotor, an intermediate rotor and a counter-rotor.
  • Such drive and driven parts run in a common housing, whose interior is spherical.
  • the housing is divided such that the separation plane contains the center of the spherical interior, so that a first housing part with a hemispherical interior with a first center and a second housing part with a hemispherical interior and a second center is formed.
  • special attention is to be paid to the design of the parting surfaces of the two housing parts in such a way that in the assembled state the first and the second center of the spherical interior spaces of the housing parts coincide.
  • Particular attention should be paid to the design of the housing separation surfaces with regard to the sealing technology to be used.
  • a rotary piston engine operating as a pump, compressor or motor includes a rotor, an intermediate rotor and a counter rotor with the intermediate rotor disposed between the rotor and the counter rotor.
  • the counter rotor has a first end face with a first toothing.
  • the intermediate rotor has a second end face with a second toothing and a third end face with a third toothing.
  • the rotor has a fourth end face with a fourth toothing.
  • Each toothing is formed from at least one tooth and one tooth gap.
  • the teeth are engaged with each other such that first working spaces are formed by meshing the teeth of the first teeth and the teeth of the second teeth, and that second working spaces are formed by meshing the teeth of the third teeth and the teeth of the fourth teeth, wherein the first and second work spaces formed volumes are changed by the combing of the teeth.
  • the rotors are rotatably guided in a housing accommodating the rotors. An inner wall of the housing is largely modeled on an outer contour of the rotors.
  • the counter rotor has a first axis of rotation, the intermediate rotor a second axis of rotation and the rotor has a third axis of rotation, wherein the first axis of rotation and the second axis of rotation include a first angle and the second axis of rotation and the third axis of rotation a second angle.
  • the first and the second angle is not equal to 0 °.
  • the rotor, the intermediate rotor and the counter rotor in a housing mounted position form a hemisphere stump.
  • the inner wall of the housing largely follows the outer contour of the rotor, the intermediate rotor and the counter rotor in the assembled state, the inner wall of the housing, the rotor, the intermediate rotor and the Opposite rotor surrounds, is formed as a hemisphere.
  • the housing can be made in one piece, wherein the processing for generating the inner wall can be made from one direction.
  • the assembly of rotor, intermediate rotor and counter rotor can be made from one direction.
  • any gap between the rotors and the inner wall can be maintained.
  • a gap between the individual rotors and the inner wall is circumferentially maintained so that rotors and inner wall do not touch.
  • Such contact could lead to damage to the rotors or inner wall or to overheating of the components due to friction.
  • the gap should be as small as possible, since it can form a leak for the medium to be pumped and thus can adversely affect the efficiency of the rotary piston engine.
  • hemispherical stump is understood herein to mean that a ball is cut through a first plane and a second plane parallel to the first plane, the first plane containing the center of the ball and the second plane cutting off a ball cap.
  • the term hemispherical stump should also be understood to mean a spherical segment in which the first plane does not contain the center of the sphere, but rather intersects the sphere at a point approximated to the second plane.
  • the second toothing of the intermediate rotor has one tooth less than the first toothing of the counter-rotor. Furthermore, the second toothing and the third toothing of the intermediate rotor have the same number of teeth. The fourth toothing of the rotor has one tooth less than the third toothing of the intermediate rotor.
  • the intermediate rotor is formed as a corrugated disk.
  • This wave-like formation is produced by a tooth gap of the third toothing protruding into a tooth root of the second toothing and vice versa.
  • the first working spaces formed between the first and second toothing have no connection to the second working spaces formed between the third and fourth toothing, so that the rotary piston machine can be operated in multiple stages and / or multiple-flow.
  • Multi-flow operation means that a medium to be transported is split into a first volume flow and a second volume flow, wherein the first volume flow is supplied to the first working spaces and the second volume flow to the second working spaces.
  • these two volume flows are brought together again after reaching the maximum pressure increase by the rotary piston engine at the outlet.
  • a multi-stage operation means that a volume flow is supplied to the first working spaces that control the pressure of the medium to be transported increase and then this pre-compressed medium to be transported is supplied to the second working spaces, which increase the pressure of the medium to be transported again.
  • the housing has an overflow chamber, which is set up in such a way that, during multistage operation, it receives the medium compressed by a first stage and supplies it to a second stage.
  • the compressed by the first working spaces to be transported medium is stored in an overflow chamber.
  • This overflow chamber may be attached to the housing as a separate chamber.
  • the compression of the medium through the first working spaces can also be referred to as the first stage.
  • the second work spaces remove the already pre-compressed medium to be transported and compress it again. This further compression can be referred to as a second stage, so to speak.
  • the overflow chamber is formed as a recess on the inner wall of the housing.
  • a drive device with a component from the group rotor, intermediate rotor and counter rotor and / or a driven device with another component from the group rotor, intermediate rotor and counter rotor is rotatably connected.
  • the rotary piston engine can be used as a transmission, so that the drive device and the output device have different speeds. Furthermore, it is possible to use in a coupling of a drive device, such as a motor, the group rotor, intermediate rotor and counter rotor as a pump or compressor. Also, the group rotor, intermediate rotor and counter rotor, if this with a medium is driven, drive a driven device and act as a motor. Furthermore, by connecting the drive device to the rotor, the intermediate rotor or the counter rotor, it is possible to correspondingly influence the rotational speed of the rotary piston machine at a constant rotational speed of the drive device. In the present embodiment, the drive device is rotatably connected to the counter rotor.
  • first angle and the second angle are oriented in the opposite direction.
  • the individual rotors are adjusted to each other so that when the first working space is minimal, the two of these first working space directly adjacent second working spaces are maximum.
  • This offers the advantage, in particular in multi-stage design, that the inflow and outflow channel can be arranged on the same side of the housing.
  • first angle and the second angle are oriented in the same direction.
  • This embodiment appears to be more suitable for multi-flow designs.
  • the first and second working spaces are at a maximum on a first side of the housing.
  • the inlet channels for the medium to be transported are arranged.
  • Diametrically opposite the inlet channels are on a second side of the housing outlet channels, since at this point the first and second working spaces are minimal and thus the medium to be transported has been subjected to the maximum pressure.
  • At least one component from the group housing, rotor, intermediate rotor (6) and counter rotor is integrally formed.
  • these parts are predestined to be manufactured as injection-molded parts.
  • the spray can be in both Plastic as well as metal take place.
  • these components can be produced inexpensively with complex surface designs.
  • At least two intermediate rotors can be arranged between the counter rotor and the rotor.
  • At least one of the toothings (14, 18, 22, 26) is designed as a trochoid toothing.
  • the first axis of rotation and the third axis of rotation enclose a third angle which is not equal to 0 °.
  • FIG. 1 shows a rotary piston machine 2 according to the invention in cross section, in particular for a multi-stage application.
  • a rotor 8 an intermediate rotor 6 and a counter rotor 4 is shown in working position.
  • the counter rotor 4 has on its first end face 12 a first toothing 14, which is formed from a first tooth 15.
  • the intermediate rotor 6 has a second end face 16 facing the counter rotor 4, on which a second toothing 18, consisting of at least one second tooth 19, is formed.
  • the intermediate rotor 6 has at a second end face 16 opposite the third end face 20, a third toothing 22, which is formed from a third tooth 23.
  • the rotor 8 has a fourth end face 24 facing the third end face 20, on which a fourth toothing 26, consisting of at least one fourth tooth 27, is formed. Furthermore, it can be seen that the teeth 15, 19, 23 and 27 of the respective teeth 14, 18, 22 and 26 are engaged with each other such that by meshing the teeth 15 of the first teeth 14 and the teeth 19 of the second teeth 18 first Work spaces 28 are formed. Furthermore, by combing the teeth 23 of the third toothing 22 and the teeth 27 of the fourth toothing 26 second working spaces 30 are formed. The volumes formed by the first 28 and second working spaces 30 are changed by the meshing of the teeth 15, 19, 23 and 27. This is evident in the characters 2 and 8th seen. An inner wall 34 of the housing 32 follows an outer contour 36 of the rotors 4, 6, 8.
  • the rotors 4, 6, 8 mounted in the housing 32 position form a half-cone stump.
  • This counter rotor shaft 40 is in a first bearing 42 which is fixedly connected to the housing 32, stored.
  • This first bearing 42 is a combined radial-axial bearing, on which axially the fifth end face 38 and radially of the counter rotor shaft 40 is supported.
  • the counter rotor shaft 40 has a receptacle 44, by means of which a drive and / or driven device, not shown here, can be connected in a rotationally fixed manner to the counter rotor 4.
  • a hemisphere 46 is concentrically arranged on the first end face 12 of the counter rotor 4. This hemisphere 46 is engaged with a spherical shaped support surface 48 disposed on the intermediate rotor 6. Further, the hemisphere 46 is engaged with a spherical shaped support surface 50 of the rotor 8.
  • the intermediate rotor 6 and the rotor 8 can be deflected relative to the counter rotor 4 with respect to a center M of the hemisphere 46.
  • the fourth end face 24 is located on the rotor 8, a circular sixth end face 52, which constitute in conjunction with the first end face 12, the hemisphere stump bounding flat surfaces.
  • a likewise cylindrical rotor shaft 54 is concentrically formed. This rotor shaft 54 in conjunction with the sixth end face 52 are supported on a combined axial-radial bearing 56.
  • the counter rotor 4 rotates about a first axis of rotation I, the intermediate rotor 6 about a second axis of rotation II and the rotor 8 about a third axis of rotation III.
  • the third axis of rotation III and the second axis of rotation II intersect at the center M of the hemisphere 46.
  • a first angle ⁇ 1 is included between the first axis of rotation I.
  • An angle ⁇ 2 is included between the second axis of rotation II and the third axis of rotation III. It can clearly be seen that the first angle ⁇ 1 and the second angle ⁇ 2 are oriented in the opposite direction. This is made clear by the two arrowheads 57. Furthermore, the first axis of rotation I and the third axis of rotation III enclose a third angle ⁇ 3, which is not equal to 0 °. As in FIG. 2 can be seen, results from this angular arrangement, a rotor assembly in which a first working space 28 with a maximum volume directly adjacent to two second work spaces 30 with a minimum volume. This is clearly visible in FIG. 2 ,
  • an inlet stub 58 is shown with an inlet control opening 64 formed in the inner wall 34 of the housing 32 as a recess.
  • the working spaces 28 are supplied with the gaseous or liquid medium to be transported and / or compressed.
  • the entirety of the first working spaces 28 is also referred to as the first stage.
  • an outlet port 60 is mounted, which is connected to a recess formed in the inner wall 34 of the housing 32 as a recess outlet control opening 66.
  • the second working spaces 30 formed by the third toothing 22 and fourth toothing 26 may also be referred to as the second stage.
  • inlet 58 and outlet port 60 diametrically opposite in the inner wall 34 of the housing 32, a formed as a recess overflow chamber 62 can be seen (see also FIG. 6 ). It should also be noted that the inlet control port 64, the outlet control port 66 and the overflow chamber 62 have no fluid-communicating connections.
  • the medium to be compressed which may be liquid or gaseous, is sucked in via the inlet stub 58 and the inlet control opening 64 by means of the opening first working chambers 28.
  • Ansch manend the medium is compressed by the closing work spaces 28 and stored in this compressed state in the overflow 62.
  • the medium in the overflow chamber thus has a higher pressure than at the inlet port 58 and has thus been compressed in a first stage.
  • the compressed medium from the overflow chamber 62 is received by opening second working chambers 30 and then further compressed by closing second working spaces 30 and fed via the outlet control opening 66 to the outlet port 60.
  • the voltage applied to the outlet port 60 of the medium to be compressed is higher than in the overflow chamber 62.
  • FIG. 3 shows the two-stage compressor described above in working position, with only the counter rotor 4, the intermediate rotor 6 and the rotor 8 are shown. It can clearly be seen that a maximally opened first working space 28 faces a maximally closed second working space 30.
  • FIG. 4 shows an exploded view of the rotors 4, 6, 8 from the rotor sight.
  • the first toothing 14 of the counter rotor 4 consists of eight first teeth 15.
  • the second toothing 18 and the third toothing 22 of the intermediate rotor 6 are each formed from seven teeth 19 and 23.
  • the fourth toothing 26 of the rotor 8 consists of six fourth teeth 27.
  • the intermediate rotor 6 has a tooth 19, 23 less than the counter rotor 4 and the rotor 8 a tooth 27 less than the intermediate rotor 6.
  • the intermediate rotor 6 is formed like a sheave, such in that a toothed space 10 of the third toothing 22 faces a second tooth 19 of the second toothing 18.
  • a toothed space 10 of the third toothing 22 faces a second tooth 19 of the second toothing 18.
  • FIG. 5 shows the representation of FIG. 4 , but seen from Schmidtrotorsicht. Clearly visible here are the support surface 48 of the intermediate rotor 6 and the support surface 50 of the rotor 8.
  • FIG. 6 shows the inner wall 34 of the housing 32. Clearly in the inner wall 34, the recesses of the overflow chamber 62, the inlet control port 64 and the outlet control opening 66 can be seen.
  • FIG. 7 is different from the representation of FIG. 1 merely in that the first angle ⁇ 1 and the second angle ⁇ 2 are oriented in the same direction. This is indicated by the position of the arrowheads 57. Again, the enclosed between the first axis of rotation I and the third axis of rotation III third angle ⁇ 3 not equal to 0 °. Thus, the axis of rotation III relative to the axis of rotation I is stronger and deflected in the opposite direction than in FIG. 1 shown. This has the consequence that the first working space 28 with the largest volume two second work spaces 30 are directly adjacent, which also have the largest volume. Such an embodiment of the invention is particularly suitable for a multi-flow application.
  • Another advantage of the present invention is that at least one component from the group housing 32, rotor 8, intermediate rotor 6 and counter rotor 4 is integrally formed, so that it is predestined to be executed as an injection molded part made of either metal or plastic.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Description

Stand der TechnikState of the art

Die vorliegende Erfindung betrifft eine Drehkolbenmaschine, die als Pumpe, Verdichter oder Motor arbeitet, mit einem Rotor, einem Zwischenrotor und einem Gegen rotor.The present invention relates to a rotary piston machine which operates as a pump, compressor or motor, with a rotor, an intermediate rotor and a counter-rotor.

Aus der DE 42 41 320 A1 ist eine Drehkolbenmaschine bekannt, die als Pumpe, Verdichter oder Motor arbeitet. Bei dieser laufen Kämme von Zähnen eines rotierenden Antriebsteils zur Begrenzung von Arbeitsräumen auf einer zykloiden Fläche eines ebenfalls verzahnten Abtriebteils und treiben dabei dieses Abtriebsteil an. Zwischen den Zähnen von Antriebsteil und Abtriebsteil werden die genannten Arbeitsräume gebildet, die während des Rotierens der Teile für ihre Arbeit vergrößert bzw. verkleinert werden, um die Förderwirkung auf ein gasförmiges oder flüssiges Medium zu erzeugen.From the DE 42 41 320 A1 is known a rotary piston machine, which works as a pump, compressor or motor. In this run combs of teeth of a rotating drive member for limiting work spaces on a cycloid surface of a likewise toothed output member and thereby drive this output member. Between the teeth of the driving part and the driven part, the said work spaces are formed, which are increased or reduced during the rotation of the parts for their work or to produce the conveying effect on a gaseous or liquid medium.

Aus den Dokumenten US 2002/0037228 , DE 10 2008 038 625 A1 und US 2,582,413 sind ähnliche Drehkolbenmaschinen bekannt. Bei der aus US 2,582,413 bekannten Drehkolbenmaschine ist jedoch die Anzahl der Zähne jeweils gleich, sodass sich das Arbeitsprinzip von der in der vorliegenden Anmeldung offenbarten Drehkolbenmaschine unterscheidet.From the documents US 2002/0037228 . DE 10 2008 038 625 A1 and US 2,582,413 Similar rotary engines are known. At the US 2,582,413 However, the known number of teeth is the same, so that the working principle differs from that disclosed in the present application rotary piston engine.

Derartige Antriebs- und Abtriebsteile laufen in einem gemeinsamen Gehäuse, dessen Innenraum kugelförmig ausgebildet ist. Zur Montage dieser Teile ist das Gehäuse derart geteilt, dass die Trennungsebene den Mittelpunkt des kugelförmigen Innenraums enthält, so dass ein erstes Gehäuseteil mit einem halbkugelförmigen Innenraum mit einem ersten Mittelpunkt und ein zweites Gehäuseteil mit einem halbkugelförmigen Innenraum und einem zweiten Mittelpunkt entsteht. Dadurch ist ein besonderes Augenmerk auf die Gestaltung der Trennflächen der beiden Gehäuseteile dergestalt zu richten, dass in montiertem Zustand sich der erste und der zweite Mittelpunkt der kugelförmigen Innenräume der Gehäuseteile decken. Auch ist besonderes Augenmerk auf die Gestaltung der Gehäusetrennflächen im Hinblick auf die zu verwendende Dichtungstechnologie zu richten.Such drive and driven parts run in a common housing, whose interior is spherical. For mounting these parts, the housing is divided such that the separation plane contains the center of the spherical interior, so that a first housing part with a hemispherical interior with a first center and a second housing part with a hemispherical interior and a second center is formed. As a result, special attention is to be paid to the design of the parting surfaces of the two housing parts in such a way that in the assembled state the first and the second center of the spherical interior spaces of the housing parts coincide. Particular attention should be paid to the design of the housing separation surfaces with regard to the sealing technology to be used.

Zusammenfassung der ErfindungSummary of the invention

Es kann daher ein Bedürfnis bestehen, ein Gehäuse mit einem einfach zu fertigenden Innenraum anzugeben.There may therefore be a need to provide a housing with an easy-to-manufacture interior.

Dieses Bedürfnis kann durch einen Gegenstand des unabhängigen Anspruchs gelöst werden. Vorteilhafte Ausgestaltungen sind in den abhängigen Ansprüchen angegeben.This need can be solved by an article of the independent claim. Advantageous embodiments are specified in the dependent claims.

Eine Drehkolbenmaschine, die als Pumpe, Verdichter oder Motor arbeitet, weist einen Rotor, einen Zwischenrotor und einen Gegenrotor auf, wobei der Zwischenrotor zwischen dem Rotor und dem Gegenrotor angeordnet ist. Der Gegenrotor weist eine erste Stirnfläche mit einer ersten Verzahnung auf. Der Zwischenrotor weist eine zweite Stirnfläche mit einer zweiten Verzahnung und eine dritte Stirnfläche mit einer dritten Verzahnung auf. Der Rotor weist eine vierte Stirnfläche mit einer vierten Verzahnung auf. Jede Verzahnung ist aus zumindest einem Zahn und einer Zahnlücke gebildet. Die Verzahnungen stehen miteinander derart in Eingriff, dass durch Kämmen der Zähne der ersten Verzahnung und der Zähne der zweiten Verzahnung erste Arbeitsräume ausgebildet werden und dass durch Kämmen der Zähne der dritten Verzahnung und der Zähne der vierten Verzahnung zweite Arbeitsräume ausgebildet werden, wobei durch die ersten und zweiten Arbeitsräume gebildete Volumina durch das Kämmen der Zähne verändert werden. Die Rotoren sind in einem die Rotoren aufnehmenden Gehäuse drehbar geführt. Eine Innenwandung des Gehäuses ist weitgehend einer Außenkontur der Rotoren nachgebildet. Der Gegenrotor weist eine erste Drehachse, der Zwischenrotor eine zweite Drehachse und der Rotor eine dritte Drehachse auf, wobei die erste Drehachse und die zweite Drehachse einen ersten Winkel und die zweite Drehachse und die dritte Drehachse einen zweiten Winkel einschließen. Hierbei ist der erste und der zweite Winkel ungleich 0°. Weiterhin bilden der Rotor, der Zwischenrotor und der Gegenrotor in im Gehäuse montierter Lage einen Halbkugelstumpf aus.A rotary piston engine operating as a pump, compressor or motor includes a rotor, an intermediate rotor and a counter rotor with the intermediate rotor disposed between the rotor and the counter rotor. The counter rotor has a first end face with a first toothing. The intermediate rotor has a second end face with a second toothing and a third end face with a third toothing. The rotor has a fourth end face with a fourth toothing. Each toothing is formed from at least one tooth and one tooth gap. The teeth are engaged with each other such that first working spaces are formed by meshing the teeth of the first teeth and the teeth of the second teeth, and that second working spaces are formed by meshing the teeth of the third teeth and the teeth of the fourth teeth, wherein the first and second work spaces formed volumes are changed by the combing of the teeth. The rotors are rotatably guided in a housing accommodating the rotors. An inner wall of the housing is largely modeled on an outer contour of the rotors. The counter rotor has a first axis of rotation, the intermediate rotor a second axis of rotation and the rotor has a third axis of rotation, wherein the first axis of rotation and the second axis of rotation include a first angle and the second axis of rotation and the third axis of rotation a second angle. Here, the first and the second angle is not equal to 0 °. Furthermore, the rotor, the intermediate rotor and the counter rotor in a housing mounted position form a hemisphere stump.

Somit kann es als ein Vorteil der Erfindung angesehen werden, dass, da die Innenwandung des Gehäuses weitestgehend der Außenkontur des Rotors, des Zwischenrotors und des Gegenrotors in montiertem Zustand folgt, die Innenwandung des Gehäuses, die den Rotor, den Zwischenrotor und den Gegenrotor umgibt, als Halbkugel ausgeformt ist. Somit lässt sich das Gehäuse einstückig gestalten, wobei die Bearbeitung zur Erzeugung der Innenwandung aus einer Richtung erfolgen kann. Auch kann die Montage von Rotor, Zwischenrotor und Gegenrotor aus einer Richtung erfolgen. Durch diese Maßnahmen entfällt zum einen ein geteiltes Gehäuse mit sich der daran anschließenden Dichtungsproblematik bezüglich der Trennflächen. Andererseits kann durch die Bearbeitung des Innenraums aus nur einer Bearbeitungsrichtung präzise ein etwaiges Spaltmaß zwischen den Rotoren und der Innenwandung eingehalten werden. Insbesondere bei der Verwendung von schnell laufenden Rotoren in Verbindung mit einer Förderung von nicht schmierenden Medien ist ein solcher Spalt zwischen den einzelnen Rotoren und der Innenwandung umlaufend einzuhalten, damit sich Rotoren und Innenwandung nicht berühren. Eine solche Berührung könnte zu einer Beschädigung der Rotoren oder Innenwandung führen oder auch zu einem Überhitzen der Bauteile aufgrund der Reibung. Der Spalt sollte jedoch so gering als möglich sein, da er eine Leckage für das zu fördernde Medium bilden und damit den Wirkungsgrad der Drehkolbenmaschine negativ beeinflussen kann.Thus, it can be considered as an advantage of the invention that, since the inner wall of the housing largely follows the outer contour of the rotor, the intermediate rotor and the counter rotor in the assembled state, the inner wall of the housing, the rotor, the intermediate rotor and the Opposite rotor surrounds, is formed as a hemisphere. Thus, the housing can be made in one piece, wherein the processing for generating the inner wall can be made from one direction. Also, the assembly of rotor, intermediate rotor and counter rotor can be made from one direction. By these measures, on the one hand eliminates a split housing with the subsequent sealing problem with respect to the parting surfaces. On the other hand, by machining the interior from only one machining direction, precisely any gap between the rotors and the inner wall can be maintained. In particular, when using fast-running rotors in conjunction with a promotion of non-lubricating media, such a gap between the individual rotors and the inner wall is circumferentially maintained so that rotors and inner wall do not touch. Such contact could lead to damage to the rotors or inner wall or to overheating of the components due to friction. However, the gap should be as small as possible, since it can form a leak for the medium to be pumped and thus can adversely affect the efficiency of the rotary piston engine.

Unter dem Begriff Halbkugelstumpf wird hierin verstanden, dass eine Kugel durch eine erste Ebene und eine zu der ersten Ebene parallele zweite Ebene geschnitten wird, wobei die erste Ebene den Mittelpunkt der Kugel enthält und die zweite Ebene eine Kugelkappe abschneidet. Unter dem Begriff Halbkugelstumpf soll auch ein Kugelabschnitt verstanden werden, bei dem die erste Ebene nicht den Mittelpunkt der Kugel enthält, sondern die Kugel an einer der zweiten Ebene angenäherten Stelle schneidet.The term hemispherical stump is understood herein to mean that a ball is cut through a first plane and a second plane parallel to the first plane, the first plane containing the center of the ball and the second plane cutting off a ball cap. The term hemispherical stump should also be understood to mean a spherical segment in which the first plane does not contain the center of the sphere, but rather intersects the sphere at a point approximated to the second plane.

In der Erfindung weist die zweite Verzahnung des Zwischenrotors einen Zahn weniger auf als die erste Verzahnung des Gegenrotors. Weiterhin weisen die zweite Verzahnung und die dritte Verzahnung des Zwischenrotors die gleiche Anzahl an Zähnen auf. Die vierte Verzahnung des Rotors weist einen Zahn weniger auf als die dritte Verzahnung des Zwischenrotors.In the invention, the second toothing of the intermediate rotor has one tooth less than the first toothing of the counter-rotor. Furthermore, the second toothing and the third toothing of the intermediate rotor have the same number of teeth. The fourth toothing of the rotor has one tooth less than the third toothing of the intermediate rotor.

Durch diese Wahl der Verzahnung kann sichergestellt werden, dass zum einen die Außenkontur von Rotor, Zwischenrotor und Gegenrotor in Form eines Halbkugelstumpfes gewahrt ist und zum anderen, dass die ersten und zweiten Arbeitsräume möglichst groß sind. Durch die möglichst große Ausgestaltung der Arbeitsräume kann mit der Drehkolbenmaschine ein hoher Durchsatz des zu transportierenden Mediums erreicht werden. Es soll noch darauf hingewiesen werden, dass in dem vorliegenden Ausführungsbeispiel die Teilung der einzelnen Verzahnungen gleich ist. Durch die unterschiedliche Anzahl an Zähnen der jeweiligen Verzahnungen drehen sich der Gegenrotor langsamer und der Rotor schneller als der Zwischenrotor. Daher kann diese Ausgestaltung der Drehkolbenmaschine auch als ein Getriebe genutzt werden.By this choice of teeth can be ensured that, on the one hand, the outer contour of the rotor, intermediate rotor and counter rotor is preserved in the form of a hemisphere stump and, secondly, that the first and second work spaces are as large as possible. Due to the largest possible design of the work spaces, a high throughput of the medium to be transported can be achieved with the rotary piston machine. It should also be noted that in the present embodiment, the pitch of the individual gears is the same. Due to the different number of teeth of the respective gears, the counter rotor rotate slower and the rotor faster than the intermediate rotor. Therefore, this embodiment of the rotary piston engine can also be used as a transmission.

In einer weiteren Ausgestaltung der Erfindung ist der Zwischenrotor wellscheibenartig ausgebildet.In a further embodiment of the invention, the intermediate rotor is formed as a corrugated disk.

Diese wellscheibenartige Ausbildung wird dadurch erzeugt, dass in einem Zahnfuß der zweiten Verzahnung eine Zahnlücke der dritten Verzahnung hineinragt und umgekehrt. Durch diese Ausgestaltung werden zum einen innerhalb des Zwischenrotors Materialanhäufungen vermieden und zum anderen die Größe der Arbeitsräume maximiert.This wave-like formation is produced by a tooth gap of the third toothing protruding into a tooth root of the second toothing and vice versa. By this configuration, on the one hand material accumulations are avoided within the intermediate rotor and, on the other hand, the size of the work spaces is maximized.

In einer weiteren Ausgestaltung der Erfindung weisen die zwischen der ersten und zweiten Verzahnung gebildeten ersten Arbeitsräume keine Verbindung zu den zwischen der dritten und vierten Verzahnung gebildeten zweiten Arbeitsräumen auf, so dass die Drehkolbenmaschine mehrstufig und/oder mehrflutig betreibbar ist.In a further embodiment of the invention, the first working spaces formed between the first and second toothing have no connection to the second working spaces formed between the third and fourth toothing, so that the rotary piston machine can be operated in multiple stages and / or multiple-flow.

Ein mehrflutiger Betrieb bedeutet, dass ein zu transportierendes Medium in einen ersten Volumenstrom und einen zweiten Volumenstrom aufgespalten wird, wobei der erste Volumenstrom den ersten Arbeitsräumen und der zweite Volumenstrom den zweiten Arbeitsräumen zugeführt wird. In der Regel werden diese beiden Volumenströme nach Erreichung der maximalen Druckerhöhung durch die Drehkolbenmaschine am Auslass wieder zusammengeführt.Multi-flow operation means that a medium to be transported is split into a first volume flow and a second volume flow, wherein the first volume flow is supplied to the first working spaces and the second volume flow to the second working spaces. As a rule, these two volume flows are brought together again after reaching the maximum pressure increase by the rotary piston engine at the outlet.

Ein mehrstufiger Betrieb bedeutet, dass ein Volumenstrom den ersten Arbeitsräumen zugeführt wird, die den Druck des zu transportierenden Mediums erhöhen und anschließend dieses vorverdichtete zu transportierende Medium den zweiten Arbeitsräumen zugeführt wird, die den Druck des zu transportierenden Mediums nochmals erhöhen.A multi-stage operation means that a volume flow is supplied to the first working spaces that control the pressure of the medium to be transported increase and then this pre-compressed medium to be transported is supplied to the second working spaces, which increase the pressure of the medium to be transported again.

In einer weiteren Ausgestaltung der Erfindung weist das Gehäuse eine Überströmkammer auf, die derart eingerichtet ist, beim mehrstufigen Betrieb das durch eine erste Stufe verdichtete Medium aufzunehmen und einer zweiten Stufe zuzuführen.In a further embodiment of the invention, the housing has an overflow chamber, which is set up in such a way that, during multistage operation, it receives the medium compressed by a first stage and supplies it to a second stage.

Hierbei wird das durch die ersten Arbeitsräume verdichtete zu transportierende Medium in einer Überströmkammer abgelegt. Diese Überströmkammer kann als separate Kammer an dem Gehäuse angebracht sein. Die Verdichtung des Mediums durch die ersten Arbeitsräume kann auch als erste Stufe bezeichnet werden. Aus der Überströmkammer entnehmen die zweiten Arbeitsräume das zu transportierende, bereits vorverdichtete Medium und verdichten dieses nochmals. Diese weitere Verdichtung kann sozusagen als zweite Stufe bezeichnet werden. Durch ein Hinzufügen von weiteren Zwischenrotoren ist es möglich, das zu transportierende Medium weiter zu verdichten.Here, the compressed by the first working spaces to be transported medium is stored in an overflow chamber. This overflow chamber may be attached to the housing as a separate chamber. The compression of the medium through the first working spaces can also be referred to as the first stage. From the overflow chamber, the second work spaces remove the already pre-compressed medium to be transported and compress it again. This further compression can be referred to as a second stage, so to speak. By adding further intermediate rotors, it is possible to further compress the medium to be transported.

In einer weiteren Ausgestaltung der Erfindung ist die Überströmkammer als eine Vertiefung an der Innenwandung des Gehäuses ausgebildet.In a further embodiment of the invention, the overflow chamber is formed as a recess on the inner wall of the housing.

Hierdurch kann auf eine separate Kammer, die an der Außenseite des Gehäuses angebracht sein kann, verzichtet werden.This makes it possible to dispense with a separate chamber, which can be attached to the outside of the housing.

In einer weiteren Ausgestaltung der Erfindung ist eine Antriebsvorrichtung mit einer Komponente aus der Gruppe Rotor, Zwischenrotor und Gegenrotor und/oder eine Abtriebsvorrichtung mit einer anderen Komponente aus der Gruppe Rotor, Zwischenrotor und Gegenrotor drehfest verbunden.In a further embodiment of the invention, a drive device with a component from the group rotor, intermediate rotor and counter rotor and / or a driven device with another component from the group rotor, intermediate rotor and counter rotor is rotatably connected.

In einer solchen Konstellation kann die Drehkolbenmaschine als Getriebe genutzt werden, so dass die Antriebsvorrichtung und die Abtriebsvorrichtung unterschiedliche Drehzahlen aufweisen. Weiterhin ist es möglich, bei einer Kopplung einer Antriebsvorrichtung, beispielsweise eines Motors, die Gruppe Rotor, Zwischenrotor und Gegenrotor als Pumpe oder Verdichter zu nutzen. Auch kann die Gruppe Rotor, Zwischenrotor und Gegenrotor, wenn diese mit einem Medium angetrieben wird, eine Abtriebsvorrichtung betreiben und selbst als Motor fungieren. Weiterhin ist es möglich, durch Verbinden der Antriebsvorrichtung mit dem Rotor, dem Zwischenrotor oder dem Gegenrotor die Drehzahl der Drehkolbenmaschine bei konstanter Drehzahl der Antriebsvorrichtung entsprechend zu beeinflussen. In dem hier vorliegenden Ausführungsbeispiel ist die Antriebsvorrichtung mit dem Gegenrotor drehfest verbunden.In such a constellation, the rotary piston engine can be used as a transmission, so that the drive device and the output device have different speeds. Furthermore, it is possible to use in a coupling of a drive device, such as a motor, the group rotor, intermediate rotor and counter rotor as a pump or compressor. Also, the group rotor, intermediate rotor and counter rotor, if this with a medium is driven, drive a driven device and act as a motor. Furthermore, by connecting the drive device to the rotor, the intermediate rotor or the counter rotor, it is possible to correspondingly influence the rotational speed of the rotary piston machine at a constant rotational speed of the drive device. In the present embodiment, the drive device is rotatably connected to the counter rotor.

In einem weiteren Ausführungsbeispiel der Erfindung ist der erste Winkel und der zweite Winkel in entgegengesetzter Richtung orientiert.In a further embodiment of the invention, the first angle and the second angle are oriented in the opposite direction.

Durch eine derartige Anordnung der beiden Winkel werden die einzelnen Rotoren zueinander so eingestellt, dass, wenn der erste Arbeitsraum minimal ist, die beiden diesem ersten Arbeitsraum direkt benachbarten zweiten Arbeitsräume maximal sind. Dies bietet den Vorteil, insbesondere bei mehrstufiger Ausführung, dass der Einström- und Ausströmkanal auf der gleichen Seite des Gehäuses anordenbar sind.By such an arrangement of the two angles, the individual rotors are adjusted to each other so that when the first working space is minimal, the two of these first working space directly adjacent second working spaces are maximum. This offers the advantage, in particular in multi-stage design, that the inflow and outflow channel can be arranged on the same side of the housing.

In einem weiteren Ausführungsbeispiel der Erfindung sind der erste Winkel und der zweite Winkel in gleicher Richtung orientiert.In a further embodiment of the invention, the first angle and the second angle are oriented in the same direction.

Diese Ausführungsform erscheint für mehrflutige Ausführungen geeigneter zu sein. Bei einer derartigen Winkelkonstellation sind an einer ersten Gehäuseseite die ersten und zweiten Arbeitsräume maximal. An dieser ersten Gehäuseseite sind die Eintrittskanäle für das zu transportierende Medium angeordnet. Diametral den Eintrittskanälen gegenüber liegen an einer zweiten Gehäuseseite die Auslasskanäle, da an dieser Stelle die ersten und zweiten Arbeitsräume minimal sind und damit das zu transportierende Medium mit dem maximalen Druck beaufschlagt worden ist.This embodiment appears to be more suitable for multi-flow designs. With such an angle configuration, the first and second working spaces are at a maximum on a first side of the housing. At this first side of the housing, the inlet channels for the medium to be transported are arranged. Diametrically opposite the inlet channels are on a second side of the housing outlet channels, since at this point the first and second working spaces are minimal and thus the medium to be transported has been subjected to the maximum pressure.

In einem weiteren Ausführungsbeispiel der Erfindung ist wenigstens eine Komponente aus der Gruppe Gehäuse, Rotor, Zwischenrotor (6) und Gegenrotor einstückig ausgebildet.In a further embodiment of the invention, at least one component from the group housing, rotor, intermediate rotor (6) and counter rotor is integrally formed.

Durch die einstückige Ausbildung sind diese Teile prädestiniert dafür, als Spritzgussteile gefertigt zu werden. Hierbei kann die Abspritzung sowohl in Kunststoff als auch Metall erfolgen. Damit lassen sich diese Komponenten mit komplexen Oberflächengestaltungen kostengünstig herstellen.Due to the one-piece design, these parts are predestined to be manufactured as injection-molded parts. Here, the spray can be in both Plastic as well as metal take place. Thus, these components can be produced inexpensively with complex surface designs.

In einem weiteren Ausführungsbeispiel der Erfindung sind zwischen dem Gegenrotor und dem Rotor wenigstens zwei Zwischenrotoren anordenbar.In a further embodiment of the invention at least two intermediate rotors can be arranged between the counter rotor and the rotor.

Hierdurch können zusätzliche Arbeitsräume geschaffen werden, so dass eine derartig gestaltete Drehkolbenmaschine entweder ein zu verdichtendes Medium noch höher verdichten kann als dies bei einer zweistufigen Verdichtung möglich ist. Auch können beim mehrflutigen Betrieb ein höherer Volumenstrom durchgesetzt werden als dies mit nur einem Zwischenrotor möglich wäre. Zusätzlich kann eine derartig gestaltete Drehkolbenmaschine sowohl mehrflutig als auch mehrstufig betrieben werden,As a result, additional working spaces can be created, so that such a rotary engine designed can either compress a medium to be compressed even higher than is possible with a two-stage compression. Also in multi-flow operation, a higher volume flow can be enforced than would be possible with only one intermediate rotor. In addition, such a designed rotary piston machine can be operated both multi-flood and multi-stage,

In einem weiteren Ausführungsbeispiel der Erfindung ist wenigstens eine der Verzahnungen (14, 18, 22, 26) als trochoide Verzahnung ausgestaltet.In a further embodiment of the invention, at least one of the toothings (14, 18, 22, 26) is designed as a trochoid toothing.

In einem weiteren Ausführungsbeispiel der Erfindung schließen die erste Drehachse und die dritte Drehachse einen dritten Winkel ein, der ungleich 0° ist.In a further embodiment of the invention, the first axis of rotation and the third axis of rotation enclose a third angle which is not equal to 0 °.

Es wird angemerkt, dass Gedanken zu der Erfindung hierin im Zusammenhang mit einer Drehkolbenmaschine mit einem Rotor, einem Zwischenrotor und einem Gegenrotor beschrieben sind. Einem Fachmann ist hierbei klar, dass die einzelnen beschriebenen Merkmale auf verschiedene Weise miteinander kombiniert werden können, um so auch zu anderen Ausgestaltungen der Erfindung zu gelangen.It is noted that thoughts on the invention herein are described in the context of a rotary engine having a rotor, an intermediate rotor, and a counter rotor. It will be clear to a person skilled in the art that the individual features described can be combined with one another in various ways so as to arrive at other embodiments of the invention.

Ausführungsformen der Erfindung werden nachfolgend mit Bezug auf die beigefügten Figuren beschrieben. Die Figuren sind lediglich schematisch und nicht maßstabsgetreu.Embodiments of the invention will be described below with reference to the accompanying drawings. The figures are only schematic and not to scale.

Kurze Beschreibung der Zeichnungen

Figur 1
zeigt eine erfindungsgemäße Drehkolbenmaschine im Querschnitt mit einer ersten Winkelanordnung der Rotorendrehachsen,
Figur 2
zeigt eine 3D-Ansicht von Rotorseite aus im Röntgenblick,
Figur 3
zeigt eine 3D-Ansciht der Rotoren im Arbeitsmodus für insbesondere mehrstufige Anwendung,
Figur 4
zeigt eine Explosionszeichnung der Rotoren aus Rotoransicht,
Figur 5
zeigt eine Explosionszeichnung der Rotoren aus Gegenrotorsicht,
Figur 6
zeigt eine Innenwandung eines Gehäuses für insbesondere mehrflutigen Betrieb und
Figur 7
zeigt eine erfindungsgemäße Drehkolbenmaschine im Querschnitt mit einer zweiten Winkelanordnung der Rotorendrehachsen.
Brief description of the drawings
FIG. 1
shows a rotary piston engine according to the invention in cross section with a first angular arrangement of the rotor rotational axes,
FIG. 2
shows a 3D view from the rotor side in the X-ray view,
FIG. 3
shows a 3D-Ansciht the rotors in the working mode for particular multi-stage application,
FIG. 4
shows an exploded view of the rotors from rotor view,
FIG. 5
shows an exploded view of the rotors from Gegenrotorsicht,
FIG. 6
shows an inner wall of a housing for in particular multi-flow operation and
FIG. 7
shows a rotary piston engine according to the invention in cross section with a second angular arrangement of the rotor axes of rotation.

Detaillierte Beschreibung beispielhafter AusführungsformenDetailed description of exemplary embodiments

An dieser Stelle soll vorausgeschickt werden, dass gleiche Teile in den einzelnen Figuren gleiche Bezugszeichen aufweisen.It should be said at this point that the same parts in the individual figures have the same reference numerals.

Figur 1 zeigt eine erfindungsgemäße Drehkolbenmaschine 2 im Querschnitt insbesondere für eine mehrstufige Anwendung. Hierbei ist ein Rotor 8, ein Zwischenrotor 6 und ein Gegenrotor 4 in Arbeitsstellung dargestellt. Hierbei weist der Gegenrotor 4 an seiner ersten Stirnfläche 12 eine erste Verzahnung 14 auf, die aus einem ersten Zahn 15 gebildet ist. Weiterhin weist der Zwischenrotor 6 eine dem Gegenrotor 4 zugewandte zweite Stirnfläche 16 auf, an der eine zweite Verzahnung 18, bestehend aus mindestens einem zweiten Zahn 19, ausgebildet ist. Weiterhin besitzt der Zwischenrotor 6 an einer der zweiten Stirnfläche 16 gegenüber liegenden dritten Stirnfläche 20 eine dritte Verzahnung 22, die aus einem dritten Zahn 23 gebildet ist. Ferner weist der Rotor 8 eine der dritten Stirnfläche 20 zugewandte vierte Stirnfläche 24 auf, an der eine vierte Verzahnung 26, bestehend aus mindestens einem vierten Zahn 27, ausgebildet ist. Weiterhin ist sichtbar, dass die Zähne 15, 19, 23 und 27 der jeweiligen Verzahnungen 14, 18, 22 und 26 miteinander derart in Eingriff stehen, dass durch ein Kämmen der Zähne 15 der ersten Verzahnung 14 und der Zähne 19 der zweiten Verzahnung 18 erste Arbeitsräume 28 ausgebildet werden. Weiterhin werden durch Kämmen der Zähne 23 der dritten Verzahnung 22 und der Zähne 27 der vierten Verzahnung 26 zweite Arbeitsräume 30 ausgebildet. Die durch die ersten 28 und zweiten Arbeitsräume 30 gebildeten Volumina werden durch das Kämmen der Zähne 15, 19, 23 und 27 verändert. Deutlich ist dies in den Figuren 2 und 8 ersichtlich. Angeordnet sind die Rotoren 4, 6 und 8 in einem Gehäuse 32. Eine Innenwandung 34 des Gehäuses 32 folgt hierbei einer Außenkontur 36 der Rotoren 4, 6, 8. Deutlich sichtbar ist, dass die Rotoren4, 6, 8 in im Gehäuse 32 montierter Lage einen Halbkegelstumpf ausbilden. An einer der ersten Stirnfläche 12 des Gegenrotors 4 gegenüberliegenden fünften Stirnfläche 38 ist konzentrisch ein zylinderförmiger Gegenrotorschaft 40 angeformt. Dieser Gegenrotorschaft 40 ist in einem ersten Lager 42, welches mit dem Gehäuse 32 fest verbunden ist, gelagert. Dieses erste Lager 42 ist ein kombiniertes Radial-Axial-Lager, an dem sich axial die fünfte Stirnfläche 38 und radial der Gegenrotorschaft 40 abstützt. Der Gegenrotorschaft 40 weist eine Aufnahme 44 auf, mittels derer eine hier nicht dargestellte Antriebs- und/oder Abtriebsvorrichtung drehfest mit dem Gegenrotor 4 verbunden werden kann. Weiterhin ist an der ersten Stirnfläche 12 des Gegenrotors 4 konzentrisch eine Halbkugel 46 angeordnet. Diese Halbkugel 46 steht in Eingriff mit einer am Zwischenrotor 6 angeordneten kugelförmig ausgeformten Stützfläche 48. Weiterhin ist die Halbkugel 46 mit einer kugelförmig ausgeformten Stützfläche 50 des Rotors 8 in Eingriff. Somit können der Zwischenrotor 6 und der Rotor 8 gegenüber dem Gegenrotor 4 bezogen auf einen Mittelpunkt M der Halbkugel 46 ausgelenkt werden. FIG. 1 shows a rotary piston machine 2 according to the invention in cross section, in particular for a multi-stage application. Here, a rotor 8, an intermediate rotor 6 and a counter rotor 4 is shown in working position. Here, the counter rotor 4 has on its first end face 12 a first toothing 14, which is formed from a first tooth 15. Furthermore, the intermediate rotor 6 has a second end face 16 facing the counter rotor 4, on which a second toothing 18, consisting of at least one second tooth 19, is formed. Furthermore, the intermediate rotor 6 has at a second end face 16 opposite the third end face 20, a third toothing 22, which is formed from a third tooth 23. Furthermore, the rotor 8 has a fourth end face 24 facing the third end face 20, on which a fourth toothing 26, consisting of at least one fourth tooth 27, is formed. Furthermore, it can be seen that the teeth 15, 19, 23 and 27 of the respective teeth 14, 18, 22 and 26 are engaged with each other such that by meshing the teeth 15 of the first teeth 14 and the teeth 19 of the second teeth 18 first Work spaces 28 are formed. Furthermore, by combing the teeth 23 of the third toothing 22 and the teeth 27 of the fourth toothing 26 second working spaces 30 are formed. The volumes formed by the first 28 and second working spaces 30 are changed by the meshing of the teeth 15, 19, 23 and 27. This is evident in the characters 2 and 8th seen. An inner wall 34 of the housing 32 follows an outer contour 36 of the rotors 4, 6, 8. It is clearly visible that the rotors 4, 6, 8 mounted in the housing 32 position form a half-cone stump. On one of the first end face 12 of the counter-rotor 4 opposite fifth end face 38 concentric with a cylindrical counter-rotor shaft 40 is formed. This counter rotor shaft 40 is in a first bearing 42 which is fixedly connected to the housing 32, stored. This first bearing 42 is a combined radial-axial bearing, on which axially the fifth end face 38 and radially of the counter rotor shaft 40 is supported. The counter rotor shaft 40 has a receptacle 44, by means of which a drive and / or driven device, not shown here, can be connected in a rotationally fixed manner to the counter rotor 4. Furthermore, a hemisphere 46 is concentrically arranged on the first end face 12 of the counter rotor 4. This hemisphere 46 is engaged with a spherical shaped support surface 48 disposed on the intermediate rotor 6. Further, the hemisphere 46 is engaged with a spherical shaped support surface 50 of the rotor 8. Thus, the intermediate rotor 6 and the rotor 8 can be deflected relative to the counter rotor 4 with respect to a center M of the hemisphere 46.

Gegenüber der vierten Stirnfläche 24 befindet sich am Rotor 8 eine kreisförmige sechste Stirnfläche 52, die in Verbindung mit der ersten Stirnfläche 12 die den Halbkugelstumpf begrenzenden ebenen Flächen darstellen. An der sechsten Stirnfläche 52 ist konzentrisch ein ebenfalls zylinderförmiger Rotorschaft 54 angeformt. Dieser Rotorschaft 54 in Verbindung mit der sechsten Stirnfläche 52 stützen sich an einem kombinierten Axial-Radial-Lager 56 ab. In dem vorliegenden Ausführungsbeispiel rotiert der Gegenrotor 4 um eine erste Drehachse I, der Zwischenrotor 6 um eine zweite Drehachse II und der Rotor 8 um eine dritte Drehachse III. Die dritte Drehachse III und die zweite Drehachse II schneiden sich in dem Mittelpunkt M der Halbkugel 46. Zwischen der ersten Drehachse I wird ein erster Winkel ϕ1 eingeschlossen. Zwischen der zweiten Drehachse II und der dritten Drehachse III wird ein Winkel ϕ2 eingeschlossen. Deutlich zu sehen ist, dass der erste Winkel ϕ1 und der zweite Winkel ϕ2 in entgegengesetzter Richtung orientiert sind. Dies ist sichtlich gemacht durch die beiden Pfeilspitzen 57. Ferner schließen die erste Drehachse I und die dritte Drehachse III einen dritten Winkel ϕ3 ein, der ungleich 0° ist. Wie in Figur 2 ersichtlich, ergibt sich durch diese Winkelanordnung eine Rotoranordnung, bei der einem ersten Arbeitsraum 28 mit einem maximalen Volumen direkt benachbart zwei zweite Arbeitsräume 30 mit einem minimalen Volumen gegenüberstehen. Gut sichtbar ist dies in Figur 2.Opposite the fourth end face 24 is located on the rotor 8, a circular sixth end face 52, which constitute in conjunction with the first end face 12, the hemisphere stump bounding flat surfaces. At the sixth end face 52, a likewise cylindrical rotor shaft 54 is concentrically formed. This rotor shaft 54 in conjunction with the sixth end face 52 are supported on a combined axial-radial bearing 56. In the present embodiment, the counter rotor 4 rotates about a first axis of rotation I, the intermediate rotor 6 about a second axis of rotation II and the rotor 8 about a third axis of rotation III. The third axis of rotation III and the second axis of rotation II intersect at the center M of the hemisphere 46. A first angle φ1 is included between the first axis of rotation I. An angle φ2 is included between the second axis of rotation II and the third axis of rotation III. It can clearly be seen that the first angle φ1 and the second angle φ2 are oriented in the opposite direction. This is made clear by the two arrowheads 57. Furthermore, the first axis of rotation I and the third axis of rotation III enclose a third angle φ3, which is not equal to 0 °. As in FIG. 2 can be seen, results from this angular arrangement, a rotor assembly in which a first working space 28 with a maximum volume directly adjacent to two second work spaces 30 with a minimum volume. This is clearly visible in FIG. 2 ,

Wie weiterhin in Figur 2 ersichtlich ist, ist an dem Gehäuse 32 ein Einlassstutzen 58 mit einer in der Innenwandung 34 des Gehäuses 32 als Vertiefung ausgebildeten Einlasssteueröffnung 64 dargestellt. Mittels des Einlassstutzens 58 werden die Arbeitsräume 28 mit dem zu transportierenden und/oder zu verdichtenden gasförmigen oder flüssigen Medium versorgt. Die Gesamtheit der ersten Arbeitsräume 28 wird auch als erste Stufe bezeichnet. Auf der gleichen Seite des Gehäuses 32 ist ein Auslassstutzen 60 angebracht, der mit einer als Vertiefung in der Innenwandung 34 des Gehäuses 32 als Vertiefung ausgebildeten Auslasssteueröffnung 66 verbunden ist. Die durch die dritte Verzahnung 22 und vierte Verzahnung 26 gebildeten zweiten Arbeitsräume 30 können auch als zweite Stufe bezeichnet werden. Weiterhin ist dem Einlass- 58 und Auslassstutzen 60 diametral gegenüberliegend in der Innenwandung 34 des Gehäuses 32 eine als Vertiefung ausgebildete Überströmkammer 62 ersichtlich (siehe hierzu auch Figur 6). Zu bemerken ist noch, dass die Einlasssteueröffnung 64, die Auslasssteueröffnung 66 sowie die Überströmkammer 62 keine fluidkommunizierende Verbindungen aufweisen.As continues in FIG. 2 it can be seen, on the housing 32, an inlet stub 58 is shown with an inlet control opening 64 formed in the inner wall 34 of the housing 32 as a recess. By means of the inlet stub 58, the working spaces 28 are supplied with the gaseous or liquid medium to be transported and / or compressed. The entirety of the first working spaces 28 is also referred to as the first stage. On the same side of the housing 32, an outlet port 60 is mounted, which is connected to a recess formed in the inner wall 34 of the housing 32 as a recess outlet control opening 66. The second working spaces 30 formed by the third toothing 22 and fourth toothing 26 may also be referred to as the second stage. Furthermore, the inlet 58 and outlet port 60 diametrically opposite in the inner wall 34 of the housing 32, a formed as a recess overflow chamber 62 can be seen (see also FIG. 6 ). It should also be noted that the inlet control port 64, the outlet control port 66 and the overflow chamber 62 have no fluid-communicating connections.

Durch ein Rotieren des Gegenrotors 4, des Zwischenrotors 6 und des Rotors 8 wird das zu verdichtende Medium, welches flüssig oder gasförmig sein kann, über den Einlassstutzen 58 sowie die Einlasssteueröffnung 64 mittels der sich öffnenden ersten Arbeitsräume 28 angesaugt. Anschießend wird das Medium durch die sich schließenden Arbeitsräume 28 verdichtet und in diesem verdichteten Zustand in der Überströmkammer 62 abgelegt. Das Medium in der Überströmkammer hat somit einen höheren Druck als am Einlassstutzen 58 und ist somit in einer ersten Stufe verdichtet worden. Das verdichtete Medium aus der Überströmkammer 62 wird durch sich öffnende zweite Arbeitsräume 30 aufgenommen und anschließend durch sich schließende zweite Arbeitsräume 30 weiter verdichtet und über die Auslasssteueröffnung 66 dem Auslassstutzen 60 zugeführt. Hierbei ist der am Auslassstutzen 60 anliegende Druck des zu verdichtenden Mediums höher als in der Überströmkammer 62. Somit ist das zu verdichtende Medium zwischen Einlassstutzen 58 und Auslassstutzen 60 zweistufig verdichtet worden.By rotating the counter-rotor 4, the intermediate rotor 6 and the rotor 8, the medium to be compressed, which may be liquid or gaseous, is sucked in via the inlet stub 58 and the inlet control opening 64 by means of the opening first working chambers 28. Anschießend the medium is compressed by the closing work spaces 28 and stored in this compressed state in the overflow 62. The medium in the overflow chamber thus has a higher pressure than at the inlet port 58 and has thus been compressed in a first stage. The compressed medium from the overflow chamber 62 is received by opening second working chambers 30 and then further compressed by closing second working spaces 30 and fed via the outlet control opening 66 to the outlet port 60. Here, the voltage applied to the outlet port 60 of the medium to be compressed is higher than in the overflow chamber 62. Thus, that is too compacting medium between inlet port 58 and outlet port 60 has been compressed two-stage.

Figur 3 zeigt den oben beschriebenen zweistufigen Verdichter in Arbeitsstellung, wobei lediglich der Gegenrotor 4, der Zwischenrotor 6 und der Rotor 8 dargestellt sind. Deutlich zu sehen ist, dass einem maximal geöffnetem ersten Arbeitsraum 28 ein maximal geschlossener zweiter Arbeitsraum 30 gegenübersteht. FIG. 3 shows the two-stage compressor described above in working position, with only the counter rotor 4, the intermediate rotor 6 and the rotor 8 are shown. It can clearly be seen that a maximally opened first working space 28 faces a maximally closed second working space 30.

Figur 4 zeigt eine Explosionszeichnung der Rotoren 4, 6, 8 aus Rotorsicht. Deutlich sichtbar ist die in dem Gegenrotor 4 angebrachte Halbkugel 46 ersichtlich, an der sich der Gegenrotor 4 und der Zwischenrotor 8 abstützen. Weiterhin ist ersichtlich, dass die erste Verzahnung 14 des Gegenrotors 4 aus acht ersten Zähnen 15 besteht. Die zweite Verzahnung 18 und die dritte Verzahnung 22 des Zwischenrotors 6 werden jeweils aus sieben Zähnen 19 und 23 gebildet. Die vierte Verzahnung 26 des Rotors 8 besteht aus sechs vierten Zähnen 27. Somit besitzt der Zwischenrotor 6 einen Zahn 19, 23 weniger als der Gegenrotor 4 und der Rotor 8 einen Zahn 27 weniger als der Zwischenrotor 6. Der Zwischenrotor 6 ist wellscheibenartig ausgebildet, dergestalt, als dass einem zweiten Zahn 19 der zweiten Verzahnung 18 eine Zahnlücke 10 der dritten Verzahnung 22 gegenübersteht. Somit entstehen keine Materialanhäufungen, wie dies passieren würde, wenn sich die zweiten Zähne 19 der zweiten Verzahnung 18 den dritten Zähnen 23 der dritten Verzahnung 22 gegenüberstehen würden. FIG. 4 shows an exploded view of the rotors 4, 6, 8 from the rotor sight. Clearly visible in the counter rotor 4 mounted hemisphere 46 can be seen on which the counter rotor 4 and the intermediate rotor 8 are supported. Furthermore, it can be seen that the first toothing 14 of the counter rotor 4 consists of eight first teeth 15. The second toothing 18 and the third toothing 22 of the intermediate rotor 6 are each formed from seven teeth 19 and 23. The fourth toothing 26 of the rotor 8 consists of six fourth teeth 27. Thus, the intermediate rotor 6 has a tooth 19, 23 less than the counter rotor 4 and the rotor 8 a tooth 27 less than the intermediate rotor 6. The intermediate rotor 6 is formed like a sheave, such in that a toothed space 10 of the third toothing 22 faces a second tooth 19 of the second toothing 18. Thus, no accumulations of material arise, as would happen if the second teeth 19 of the second toothing 18 would oppose the third teeth 23 of the third toothing 22.

Figur 5 zeigt die Darstellung der Figur 4, jedoch gesehen aus Gegenrotorsicht. Deutlich zu sehen sind hier die Stützfläche 48 des Zwischenrotors 6 sowie die Stützfläche 50 des Rotors 8. FIG. 5 shows the representation of FIG. 4 , but seen from Gegenrotorsicht. Clearly visible here are the support surface 48 of the intermediate rotor 6 and the support surface 50 of the rotor 8.

Figur 6 zeigt die Innenwandung 34 des Gehäuses 32. Deutlich sind in der Innenwandung 34 die Vertiefungen der Überströmkammer 62, der Einlasssteueröffnung 64 sowie der Auslasssteueröffnung 66 zu erkennen. FIG. 6 shows the inner wall 34 of the housing 32. Clearly in the inner wall 34, the recesses of the overflow chamber 62, the inlet control port 64 and the outlet control opening 66 can be seen.

Figur 7 unterscheidet sich von der Darstellung der Figur 1 lediglich dadurch, dass der erste Winkel ϕ1 und der zweite Winkel ϕ2 in gleicher Richtung orientiert sind. Dies ist durch die Position der Pfeilspitzen 57 angedeutet. Auch hier ist der zwischen der ersten Drehachse I und der dritten Drehachse III eingeschlossene dritte Winkel ϕ3 ungleich 0°. Damit ist die Drehachse III gegenüber der Drehachse I stärker und in entgegengesetzter Richtung ausgelenkt als in Figur 1 dargestellt. Dies hat zur Folge, dass dem ersten Arbeitsraum 28 mit dem größten Volumen zwei zweite Arbeitsräume 30 direkt benachbart sind, die ebenfalls das größte Volumen besitzen. Eine derartige Ausgestaltung der Erfindung eignet sich insbesondere für eine mehrflutige Anwendung. FIG. 7 is different from the representation of FIG. 1 merely in that the first angle φ1 and the second angle φ2 are oriented in the same direction. This is indicated by the position of the arrowheads 57. Again, the enclosed between the first axis of rotation I and the third axis of rotation III third angle φ3 not equal to 0 °. Thus, the axis of rotation III relative to the axis of rotation I is stronger and deflected in the opposite direction than in FIG. 1 shown. This has the consequence that the first working space 28 with the largest volume two second work spaces 30 are directly adjacent, which also have the largest volume. Such an embodiment of the invention is particularly suitable for a multi-flow application.

Wie in Figur 8 sichtbar, wird mittels der durch die ersten Arbeitsräume 28 gebildeten ersten Stufe durch die Einlassstutzen 58 das zu transportierende flüssige oder gasförmige Medium angesaugt und unter Druckerhöhung dem dem Einlassstutzen 58 gegenüberliegenden Auslassstutzen 60 zugeführt. Auf der gleichen Seite des Gehäuses 32, benachbart zu den Einlassstutzen 58, befindet sich ein weiterer Einlassstutzen 68, durch welchen das zu transportierende Medium in die zweiten Arbeitsräume 30 gelangt. Auch hier wird das zu transportierende Medium unter Druckerhöhung einem an derselben Gehäuseseite wie der Auslassstutzen 60 sitzende weitere Auslassstutzen 70 übergeben. Somit wird ein erster Volumenstrom eines zu transportierenden Mediums zwischen dem Einlassstutzen 58 und dem Auslassstutzen 60 verdichtet und ein zweiter Volumenstrom zwischen dem weiteren Einlassstutzen 68 und dem weiteren Auslassstutzen 70.As in FIG. 8 Visible, by means of the first stage formed by the first working space 28 through the inlet port 58, the liquid or gaseous medium to be transported is sucked in and fed to the inlet port 58 opposite outlet port 60 with pressure increase. On the same side of the housing 32, adjacent to the inlet port 58, there is another inlet port 68, through which the medium to be transported enters the second working spaces 30. Here, too, the medium to be transported is passed under pressure increase to a seated on the same side of the housing as the outlet 60 further outlet 70. Thus, a first volume flow of a medium to be transported between the inlet port 58 and the outlet port 60 is compressed and a second volume flow between the further inlet port 68 and the other outlet port 70th

Ein weiterer Vorteil der vorliegenden Erfindung besteht darin, dass wenigstens eine Komponente aus der Gruppe Gehäuse 32, Rotor 8, Zwischenrotor 6 und Gegenrotor 4 einstückig ausgebildet ist, so dass diese prädestiniert ist, als Spritzgussteil entweder aus Metall oder aus Kunststoff ausgeführt zu werden.Another advantage of the present invention is that at least one component from the group housing 32, rotor 8, intermediate rotor 6 and counter rotor 4 is integrally formed, so that it is predestined to be executed as an injection molded part made of either metal or plastic.

Claims (12)

  1. Rotary piston machine which operates as a pump, compressor or motor,
    - having a rotor (8), having an intermediate rotor (6) and having a counter rotor (4), wherein the intermediate rotor (6) is arranged between the rotor (8) and the counter rotor (4),
    - wherein the counter rotor (4) has a first end face (12) with a first toothing (14), wherein the intermediate rotor (6) has a second end face (16) with a second toothing (18) and has a third end face (20) with a third toothing (22), and wherein the rotor (8) has a fourth end face (24) with a fourth toothing (26), and each toothing (14, 18, 22, 26) is formed from at least one tooth (15, 19, 23, 27) and one tooth space (10),
    - wherein the toothings (14, 18, 22, 26) engage with one another such that meshing of the teeth (15) of the first toothing (14) and of the teeth (19) of the second toothing (18) causes first working chambers (28) to be formed, and such that meshing of the teeth (23) of the third toothing (22) and of the teeth (27) of the fourth toothing (26) causes second working chambers (30) to be formed, wherein volumes formed by the first (28) and second working chambers (30) are varied by the meshing of the teeth (15, 19, 23, 27),
    - having a housing (32) with an inner wall (34), which housing accommodates the rotor (8), intermediate rotor (6) and counter rotor (4), wherein the rotor (8), intermediate rotor (6) and counter rotor (4) are guided rotatably in the housing (32), and the inner wall (34) largely follows an outer contour (36) of the rotor (8), intermediate rotor (6) and counter rotor (4),
    - wherein the counter rotor (4) has a first axis of rotation (I), wherein the intermediate rotor (6) has a second axis of rotation (II), wherein the rotor (8) has a third axis of rotation (III), wherein the first axis of rotation (I) and the second axis of rotation (II) enclose a first angle (ϕ1), wherein the second axis of rotation (II) and the third axis of rotation (III) enclose a second angle (ϕ2), and wherein the first (ϕ1) and the second angle (ϕ2) are not equal to 0°,
    characterized in that
    - the rotor (8), the intermediate rotor (6) and the counter rotor (4) form, in the position in which they are assembled in the housing, a hemispherical stump (36), wherein "hemispherical stump" is to be understood as meaning that a sphere is cut by a first plane and by a second plane which is parallel to the first plane, wherein the first plane contains the centre point and the second plane cuts away a spherical cap, or wherein the second plane cuts away a spherical cap and the first plane does not contain the centre point but rather cuts the sphere at a location closer to the second plane, and wherein an inner wall of the housing (32) substantially follows the outer contour of the rotor (8), the intermediate rotor (6) and the counter rotor (4) in the assembled state, and
    in that
    - the second toothing (18) has one tooth (19) fewer than the first toothing (14), in that the second toothing (18) and the third toothing (22) have the same number of teeth (19, 23), and in that the fourth toothing (26) has one tooth (27) fewer than the third toothing (22).
  2. Rotary piston machine according to Claim 1, characterized in that the intermediate rotor (6) is in the form of an undulating disc.
  3. Rotary piston machine according to one of the preceding claims, characterized in that the first working chambers (28) formed between the first (14) and second toothing (18) have no connection to the second working chambers (30) formed between the third (22) and fourth toothing (26), and so the rotary piston machine (2) is able to be operated in multi-stage and/or multi-channel configuration.
  4. Rotary piston machine according to Claim 3, characterized in that the housing (32) has an overflow chamber (62) which is designed such that, during multi-stage operation, it receives the medium compressed by a first stage and supplies said medium to a second stage.
  5. Rotary piston machine according to Claim 4, characterized in that the overflow chamber (62) is formed as a depression at the inner wall (34) of the housing (32).
  6. Rotary piston machine according to one of the preceding claims, characterized in that a drive device is connected rotationally conjointly to a component from the group of rotor (8), intermediate rotor (6) and counter rotor (4), and/or an output device is connected rotationally conjointly to some other component from the group of rotor (8), intermediate rotor (6) and counter rotor (4).
  7. Rotary piston machine according to one of the preceding claims, characterized in that the first angle (ϕ1) and the second angle (ϕ2) are oriented in opposite directions.
  8. Rotary piston machine according to one of Claims 1 to 6, characterized in that the first angle (ϕ1) and the second angle (ϕ2) are oriented in the same direction.
  9. Rotary piston machine according to one of the preceding claims, characterized in that at least one component from the group of housing (32), rotor (8), intermediate rotor (6) and counter rotor (4) is formed in one piece.
  10. Rotary piston machine according to one of the preceding claims, characterized in that at least two intermediate rotors (6) are able to be arranged between the counter rotor (4) and the rotor (8).
  11. Rotary piston machine according to one of the preceding claims, characterized in that at least one of the toothings (14, 18, 22, 26) is formed as a trochoidal toothing.
  12. Rotary piston machine according to one of the preceding claims, characterized in that the first axis of rotation (I) and the third axis of rotation (III) enclose a third angle (ϕ3) which is not equal to 0°.
EP11767718.7A 2010-12-20 2011-10-12 Multi-stage or multi-channel pump, compressor or motor Active EP2655803B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010063506A DE102010063506A1 (en) 2010-12-20 2010-12-20 Pump, compressor or motor multi-stage or multi-flow
PCT/EP2011/067786 WO2012084290A2 (en) 2010-12-20 2011-10-12 Multi-stage or multi-channel pump, compressor or motor

Publications (2)

Publication Number Publication Date
EP2655803A2 EP2655803A2 (en) 2013-10-30
EP2655803B1 true EP2655803B1 (en) 2018-02-28

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Country Link
EP (1) EP2655803B1 (en)
DE (1) DE102010063506A1 (en)
WO (1) WO2012084290A2 (en)

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2582413A (en) * 1945-07-20 1952-01-15 James M Clark Expansible chamber rotary fluid displacement device
DE4241320C2 (en) 1991-12-09 2002-01-17 Arnold Felix Rotary engine
US6494698B2 (en) * 1997-08-21 2002-12-17 Felix Michael Arnold Rotary piston machine having cycloid teeth
DE102008038625A1 (en) * 2008-08-12 2010-02-18 Cor Pumps + Compressors Ag Spur gear pump

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WO2012084290A2 (en) 2012-06-28
WO2012084290A3 (en) 2013-05-02
DE102010063506A1 (en) 2012-06-21
EP2655803A2 (en) 2013-10-30

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