EP2613052B1 - Rotating piston compressor or rotating piston pump - Google Patents

Rotating piston compressor or rotating piston pump Download PDF

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Publication number
EP2613052B1
EP2613052B1 EP12000060.9A EP12000060A EP2613052B1 EP 2613052 B1 EP2613052 B1 EP 2613052B1 EP 12000060 A EP12000060 A EP 12000060A EP 2613052 B1 EP2613052 B1 EP 2613052B1
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EP
European Patent Office
Prior art keywords
piston
rotary piston
pistons
working
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.)
Active
Application number
EP12000060.9A
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German (de)
French (fr)
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EP2613052A1 (en
Inventor
Oleksandr Bezeliuk
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Noble Products International GmbH
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Noble Products International GmbH
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Publication of EP2613052A1 publication Critical patent/EP2613052A1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/084—Toothed wheels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • F04C11/001—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/123—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with radially or approximately radially from the rotor body extending tooth-like elements, co-operating with recesses in the other rotor, e.g. one tooth
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/24—Rotary-piston machines or pumps of counter-engagement type, i.e. the movement of co-operating members at the points of engagement being in opposite directions
    • F04C2/28—Rotary-piston machines or pumps of counter-engagement type, i.e. the movement of co-operating members at the points of engagement being in opposite directions of other than internal-axis type

Definitions

  • the invention relates to a rotary piston compressor or rotary piston pump according to the preamble of claim 1.
  • Pump or compressor consist of a housing and two parallel, synchronized counter-rotating units, which are interconnected via a gearbox.
  • Each turntable consists of a shaft and a fixedly connected rotor with the function of a rotary piston.
  • Each rotary piston is a rotary body, which consists of two or three flat disc-shaped, integrally formed part discs, wherein two forming a pair of part discs intermesh.
  • By sequential arrangement of the individual part discs of each rotor creates a catchy gradation and by cycloid-shaped formation of the connecting surfaces between the lateral surface and the core surface of each disc a self-contained, dense working chamber.
  • this On the suction side, this has a control opening designed to control the gas filling and, on the pressure side, a control opening designed to control the gas compression.
  • Two multi-stage rotary pistons of one plane rotate in the opposite direction to each other in the ratio 1: 1 with the same speed.
  • Two pairs interlocking rotary pistons or their dividing discs suck the fluid in several stages via suction nozzle and a arranged in a housing suction-side control port and then displace it into the working chambers.
  • the medium is precompressed by the respective rotary pistons of both rotors and finally compressed in the respective delivery chamber.
  • a pressure-side control port the medium is transferred with the desired total compression in a pressure channel.
  • Another disadvantage is the mechanical surface contact of two intermeshing part discs of the rotary piston. Due to the friction become high demands placed on the material of the rotary piston. There is a risk that increased wear occurs with the result of leaks.
  • the NL 7 509 751 is considered to be the closest prior art and discloses the features of the preamble of claim 1.
  • the invention has for its object to provide a rotary piston compressor or a rotary piston pump, which is or is exposed in the operating state lower mechanical loads and is characterized by improved performance characteristics.
  • the attached to the shaft of the rotor units disc is circular in shape and has at least one piston, wherein a piston consists of two identical piston sections in the form of ring cut-outs, which are arranged mirror-symmetrically to each other, one on each end face of the disc.
  • a piston consists of two identical piston sections in the form of ring cut-outs, which are arranged mirror-symmetrically to each other, one on each end face of the disc.
  • Identical here means that the two piston sections of a piston in their geometry, the cross-sectional shape and in the mass are always the same.
  • the mirror-symmetrically arranged piston sections project beyond the outer edge of the associated disk, with respect to their radian length, with the same dimension.
  • the distance between two adjacent rotor units is dimensioned so that their piston lying in a plane in the operating state in a common overlap region non-contact mesh.
  • the width of the overlap region corresponds to the difference between the outer and inner radii of the respective pistons, which is the same for adjacent pistons.
  • the overlap area is located at the points where the circular path of the one piston of a rotor unit intersect with the circular path of the piston of the adjacent rotor unit.
  • the housing of the pump or of the compressor consists of at least two housing components with an annular cylinder chamber for receiving the piston sections.
  • the cylinder chamber is divided by a between two adjacent housing components arranged intermediate ring, which projects into the space between two mirror-symmetrically arranged piston sections.
  • the basic version as the simplest version consists of two identical rotor units, each with a disc and a piston, wherein the radian gauge length of the two pistons is in each case 180 °.
  • the pistons of both rotor units alternately suck the delivery medium through an inlet opening with their side face pointing in the suction direction and compress it with their other side face pointing in the compression direction against the lateral surface of the other adjacent piston which closes the overlap region.
  • an outlet opening the compressed fluid is transferred to a pressure channel.
  • the two pistons act alternately as a working piston and closing piston during a complete revolution. In all other embodiments, this is not the case, since in these at least one piston acts only as a closure piston and at least one other adjacent piston as a working piston.
  • the piston sections have the shape of a ring cutout or that of a partial ring.
  • the two narrow side surfaces of the piston sections preferably have a rectangular or square cross-sectional area.
  • Two mirror-symmetrically arranged piston sections functionally form a piston section pairing or are also referred to as pistons.
  • the outer radius of the pistons is always larger than the outer radius of the associated disc.
  • the extent to which the two annular piston sections project beyond the associated disk is the same for both piston sections, and e.g. dependent on the predetermined volume of the medium to be compressed.
  • the load on the rotor shaft is thus absorbed by two opposing forces.
  • the shaft, the disc and the Kolbenabroughproung or piston have a common axis of rotation and radial axis in single-stage and multi-stage designs.
  • a gear is arranged on each rotor unit, for synchronizing at least two rotor units.
  • a disc with one or more pairs of piston sections always represents a structure, e.g. produced by casting, or of several parts, which are assembled into a functional unit.
  • the discs otherwise have no special function.
  • Each piston can be balanced by one or more additionally arranged on the respective disc identical Kolbenabêtcrustation or by the arrangement of balancing weights on the disc.
  • Pump or compressor with two rotor units, each with a piston, which lie in one plane, can be made different in diameter and / or in the number of pistons.
  • the smaller diameter piston acts as a closure piston and the larger diameter piston acts as a working piston.
  • the rotor units are also referred to as a working rotor unit or shutter rotor unit and the associated disks as a working disk or closure disk.
  • non-identical rotor units acts a rotor unit, the winning bids sucks and compressed as Härotoriser and another as a shutter rotor unit, as this closes with the lateral surface of their pistons both working areas, suction and compression area, and releases again.
  • the radian length of the working piston is a maximum of 180 ° and the radian length of the closure piston is at least 180 °.
  • a piston (closure piston) always forms at least two common combing areas, each with a different piston (working piston).
  • Multi-stage pumps or compressors may be equipped with disks of different sizes in outer diameter and / or with a different large number of pistons.
  • the sum of the circular arc length of two intermeshing pistons corresponds to the circumference of a circle with the outer radius of the piston, which acts as a closure piston, or a radian length of 360 °.
  • a housing of several housing components is provided, for each stage two housing components.
  • the housing has at least two rotor units at least one suction opening with a suction channel for sucking the pumped medium and at least one pressure channel for the compressed medium.
  • the suction channel and the pressure channel are with the annular Cylinder chamber of the working rotor unit connected, which performs the suction and compression.
  • two identical rotor units both have a common suction and pressure channel.
  • each working rotor unit has its own suction and its own pressure channel.
  • a suction cup for sucking in conveying medium and opposite to this a pressure channel for compressed medium are provided.
  • the annular cylinder chamber in the housing components serves to receive the piston sections and is formed by at least two intersecting circular grooves extending in the housing components.
  • the single-stage pumps or compressors are designed for low pressure ranges of up to approx. 20 bar.
  • multiple suction channels and pressure channels may be present, with multiple pressure channels can be combined in a pressure accumulator.
  • Multi-stage pumps or compressors are designed for high-pressure ranges of up to approx. 500 bar.
  • the compression of the pumped liquid takes place by pre-compression of the pumped medium in at least one additional level.
  • the final compression takes place in the main or last level. Between all levels connecting channels are placed in the housing for the transmission of precompressed fluid from one to the other level.
  • a multi-stage design is advantageous that several standardized components of single-stage versions can be used.
  • the pumps or compressors according to the invention are characterized by a simple and compact design and enable operation without lubrication.
  • FIGS. 1 to 4 a first embodiment of a compressor is shown, which consists of two centrally mounted and axially parallel to each other in opposite directions rotatable rotor units 8, 12, which are identical and arranged in a housing, consisting of two housing components 1, 2, in a plane.
  • Each rotor unit 8, 12 consists of a rotor shaft 9, 13, each with a rotationally fixed circular disc 10, 14th
  • each disc 10, 14 On both end faces of each disc 10, 14, an annular piston portion 10b, 14b is arranged.
  • the two piston sections 10b or 14b each of a disc 10, 14 are identical and arranged mirror-symmetrically. This applies to all embodiments according to the invention.
  • Identical here means the same geometry, mass and cross-sectional shape.
  • the cross-sectional shape is rectangular in the examples shown.
  • the piston portions 10b, 14b are arranged so that they project beyond the associated disc 10, 14 in the radial direction uniformly. As a result, the piston sections project beyond the outer edge of the associated disc, with respect to their radian length, to the same extent.
  • the supernatant or extent to which the annular piston portions project beyond the associated disc is e.g. depending on the given work volume.
  • balancing weights 10c, 14c are arranged on each end face of the discs 10, 14 ( Fig. 2 ).
  • Each piston section is assigned, if necessary, a balance weight to the required in the operating state To ensure concentricity.
  • the disc, the associated piston sections and the balance weights form a compact unit.
  • the distance between the two adjacent disks 10 and 14 is dimensioned so that their piston lying in a plane in the operating state in a common overlap region non-contact mesh. This region is located at the points where the circular path of the one piston of a rotor unit intersects with the circular path of the piston of the adjacent rotor unit ( Fig. 4 ).
  • the overlap area corresponds to the difference between the outer and inner radius of the respective pistons, which is the same for adjacent pistons.
  • the radian length of both adjacent pistons is 180 °. If the radian measurement length of the working piston is less than 180 °, the radian length of the closure piston is 180 ° greater than 180 ° by the difference. As a result, the required compression volume can be realized.
  • two housing components 1, 2 are in a plane annular grooves, in the first housing member 1 annular grooves 4a and in the second housing member 2 annular grooves 4b, which adjoin one another directly and form the cylinder chamber 4.
  • the groove-shaped section 4.1 is intended for receiving the working piston 10a and the groove-shaped section 4.2 for receiving the closure piston 14a.
  • the annular piston sections rotate in the grooves, which are tuned in their geometry to the cross-sectional shape of the piston sections.
  • the rectangular shape is preferred as a cross-sectional shape. Also suitable, however, are other cross-sectional shapes, such as round or oval.
  • a common circumferential annular cylinder chamber 4 as a curved extending eight. As in Fig. 4 can be seen, the cylinder chamber 4 by two overlapping circular extending, mirror-inverted arranged grooves 4a, 4b of the adjacent housing components 1, 2 is formed.
  • the housing components 1, 2 are structurally designed so that the balancing weights 10c, 14c arranged on the working disk 10 and on the closure disk 14 are separated from the piston portions by a circumferential housing inner wall ( Fig. 2 ).
  • a suction opening 5a which open into a suction channel 5 ( Fig. 4 ).
  • a pressure port 6a is provided, which is in communication with a pressure channel 6 for the compressed medium.
  • a Arranged intermediate ring 3 which extends to directly to the counter-rotating disks of a plane and the annular space between two mirror-symmetrically arranged piston portions 10b and 14b fills, taking into account a sufficient clearance for a frictionless rotation of the discs 10 and 14th
  • a gear is fixed to the working rotor shaft 9, the gear 11 and the shutter rotor shaft 13, the gear 15.
  • the two gears 11, 15 engage each other and form a gear via which the rotational movements of the two shafts 9, 13 are synchronized.
  • the gear transmission is designed in this embodiment so that the working rotor shaft 9 rotates to the shutter rotor shaft 13 in the ratio 1: 1.
  • the two shafts 9, 13 are mounted in corresponding cylindrical roller bearings 7 of the housing components 1, 2, wherein two bearings are provided for each shaft.
  • the working disk and shutter disk and the gears are fastened, for example by means of splined connections on the respective shaft and secured by means known per se against rotation.
  • suction side suction chamber S and suction channel 5
  • compression side compression chamber K and compression channel 6
  • the piston 14a of the second rotor unit 12 acts as a closure piston.
  • the piston 10a of the first rotor unit separates and closes the suction side and the compression side region of the cylinder chamber, thereby fulfilling the function of a shutter piston. Both processes "sucking” and “compressing” occur at each 180 ° rotation of the two pistons 10a, 14a simultaneously. Thus assume the piston of the first rotor unit 8 and the second rotor unit 12 during a complete revolution alternately successively after each 180 ° rotation, the function as a working or closure piston.
  • a second embodiment variant is shown as a cross-sectional view, in the direction of the lower housing component 2.
  • This embodiment differs from the previous embodiment according to FIGS. 1 to 4 in that the two rotor units 22, 25 have discs 27, 24 and pistons 27a, 24a of different diameter or outer radius, the piston 27a having the smaller outer radius being a closure piston and cooperating with three working pistons 24a, 24b, 24c in one plane.
  • the interlocking of the closure piston 27a with each working piston 24a, 24b, 24c always takes place successively during a 360 ° rotation of the working rotor unit 22.
  • the closure piston 27a is associated with three identical working pistons 24a, 24b, 24c with the same radian length, which are each offset by 120 ° to each other ,
  • a working piston 24a, 24b, 24c meshes with the closure piston 27a without contact.
  • the processes "suction” and “compression” are carried out simultaneously by the respective working piston. While the working piston 24a sucks in the conveying medium, the working piston 24c compresses the conveying medium against the lateral surface of the closing piston 27a. Between the working piston 24a and 24b and between the working piston 24b and 24c conveying medium is transported without compressing in the cylinder chamber 4.
  • suction opening 5a, suction channel 5, pressure channel opening 6a and pressure channel 6 are provided and a suction chamber S and a pressure chamber K.
  • the rotor units 22 and 25 are equipped in conventional construction with rotor shafts 23 and 26.
  • FIG. 6 shown third embodiment in contrast to the first embodiment not two but three identical rotor units 8, 12, 16, each having a rotor shaft 9, 13, 17 with a circular disc 10, 14, 18, each circular disc at their end faces respectively an annular piston portion 10b, 14b, 18b has.
  • the pistons 10a, 14a and 18a are analogous to those in the FIGS. 1 to 4 shown execution. With three or more rotor units connected in a row, the shutter rotor unit 12 is always arranged between two working rotor units 8, 16.
  • the working piston 18a of the third rotor unit 16 forms the first rotor unit 8 with the adjacent piston 14a of the second rotor unit 12 Overlapping area, where each two adjacent pistons mesh with a time delay.
  • the rotor unit 12, which is arranged centrally between two rotor units 8, 16, is always a shutter rotor unit due to its function, since the closing piston 14a closes the suction or compression area of both adjacent working rotor units 8, 16.
  • the closure piston 14a closes with its lateral surface the suction S and compression regions K of the cylinder chamber (in section 4.1) of the first working rotor unit 8 and then the cylinder chamber (in section 4.3) of the second working rotor unit 16th
  • the first working rotor unit 8 and the second working rotor unit 16 each have their own suction channel 5 connected to the respective cylinder chamber 4.1, 4.3 with respective suction opening 5a as well as a separate pressure channel 6 also connected to the respective cylinder chamber with respective pressure channel opening 6a.
  • suction and pressure channels of both rotor units are designated identically.
  • the suction channels and the pressure channels of the first working rotor unit 8 and the second working rotor units 16 are arranged offset by 180 ° in the housing.
  • the closure piston 14a of the closure rotor unit 12 always has the function of closing the suction-side regions as well as the compression-side regions of the cylinder chamber 4.1, 4.3.
  • the working piston 10 a sucks from the suction channel 5 during a 180 ° rotation conveying medium with the suction side seen rectangular side surface of the piston by rotation in a clockwise direction and compresses the medium with its opposite, rectangular side surface against the lateral surface of the closure piston 14 a.
  • the clockwise rotating second working piston 18a closes with its lateral surface the adjacent suction 5 and pressure channel 6 and thus the connection to the annular cylinder chamber (Section 4.2).
  • the second working piston 18a draws from its suction channel 5 conveying medium with its suction side seen rectangular side surface by its rotational movement and compresses it with its opposite rectangular side surface against the lateral surface of the closure piston 14a.
  • the closure piston 14a closes with its lateral surface during a rotation through 180 °, the annular cylinder chamber (section 4.1) of the first working rotor unit 8 and after another rotation through 180 °, the annular cylinder chamber (section 4.3) of the second working rotor unit 16, so within a complete revolution to 360 ° both working rotor units the suction and the compression process offset by 180 ° in succession.
  • a star-shaped connection of three working rotor units 8, 16, 19 to a centrally or centrally arranged shutter rotor unit 12 is shown.
  • the angle between the axis of rotation of the shutter rotor unit to the axis of rotation of each working rotor unit depends on the number of working rotor units and is, for example, with the arrangement of three working rotor units 120 ° and with the arrangement of four working rotor units 90 °.
  • the closure piston 14a of the centrally arranged shutter rotor unit 12 always meshes successively with the respective power pistons 10a, 18a, 21a. In each case, an equally large overlap area arises with each working piston of the respective working rotor units. On a work disk and several working piston can be arranged.
  • the work rotor units 8, 16 and 19 are analogous to those in Fig. 6 executed units executed.
  • the closure piston 14a of the centrally arranged shutter rotor unit 12 is smaller in diameter than the pistons of the working rotor units.
  • a fifth embodiment can also be several working rotor units and a plurality of shutter rotor units axially parallel circular verbun-related, the number of working and shutter rotor units is the same and a shutter rotor unit must always be arranged between two working rotor units.
  • the individual working rotor units are equipped with two identical working pistons 10a, each working piston 10a having a radian length of 80 °.
  • the smaller diameter shutter rotor units are equipped only with a shutter piston 14a with a radian length of 170 °.
  • Previously mentioned components are identified by the same reference numerals.
  • Each work rotor unit may have two separate, connected to each other at the respective cylinder chamber suction channels and two own also offset to each other connected to the cylinder chamber pressure channels.
  • each work rotor unit each has a working disk on which two identical working piston are arranged symmetrically to each other and each shutter rotor unit each have a shutter disc, on each of which a shutter piston is arranged.
  • two rotor units are equipped with pistons, which are arranged in several working planes and connected to each other, each level can be arbitrarily constructed in different variants or modular.
  • pistons which are arranged in several working planes and connected to each other, each level can be arbitrarily constructed in different variants or modular.
  • all previously described single-stage designs in floor-type design can be used for the construction of multi-stage designs. In principle, there are no differences in the mode of operation either.
  • Fig. 9 shows a simplified schematic representation of two rotor units 8, 12 with four levels or four stages.
  • working or VerMitschelben are fixed with working or closure piston, which correspond in their execution to the components already described.
  • the fluid is sucked and compressed.
  • the difference to the single-stage design consists only in that in at least one additional level, the feeder medium is sucked through a suction channel and precompressed.
  • the precompressed medium is passed through a connection channel to an adjacent level, this level having an additional suction channel. At this level, precompressed medium is finally compressed and transferred via a pressure line into a pressure vessel.
  • Each connection channel is equipped with a cooler.
  • the shutter rotor units and the working rotor units rotate in a speed ratio which depends on the number of working pistons.
  • the speed ratio of shutter rotor unit to working rotor unit is 1: 1.
  • the speed ratio is proportional to the ratio of the number of pistons of one rotor unit to the number of pistons of the other rotor unit.
  • the performance parameters can be increased by joining several pressure channels in a pressure vessel.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Description

Die Erfindung bezieht sich auf einen Rotationskolbenverdichter bzw. Rotationskolbenpumpe gemäß dem Oberbegriff des Anspruchs 1.The invention relates to a rotary piston compressor or rotary piston pump according to the preamble of claim 1.

Auf dem Gebiet der Rotationskolbenverdichter bzw. Rotationskolbenpumpen gibt es bereits eine Vielzahl an Veröffentlichungen.There are already a large number of publications in the field of rotary piston compressors and rotary piston pumps.

Aus der WO20091024262 A1 sind eine mehrstufige Drehkolbenvakuumpumpe bzw. -verdichter bekannt. Pumpe oder Verdichter bestehen aus einem Gehäuse und zwei parallel angeordneten, synchronisiert gegenläufigen Dreheinheiten, die über ein Getriebe miteinander verbunden sind.From the WO20091024262 A1 are a multi-stage rotary piston vacuum pump or compressor known. Pump or compressor consist of a housing and two parallel, synchronized counter-rotating units, which are interconnected via a gearbox.

Jede Dreheinheit besteht aus einer Welle und einem mit dieser fest verbundenen Rotor mit der Funktion eines Drehkolbens. Jeder Drehkolben ist ein Rotationskörper, der aus zwei oder drei flachen scheibenförmigen, einstückig ausgebildeten Teilscheiben besteht, wobei zwei ein Paar bildende Teilscheiben ineinandergreifen. Durch Hintereinanderreihung der einzelnen Teilscheiben jedes Rotors entsteht eine eingängige Schraubenstufung sowie durch zykloidenförmige Ausbildung der Verbindungsflächen zwischen Mantelfläche und Kemfläche jeder Teilscheibe eine in sich geschlossene, dichte Arbeitskammer. Diese weist saugseitig eine zur Steuerung der Gasfüllung ausgebildete Steueröffnung sowie druckseitig eine zur Steuerung der Gaskompression ausgebildete Steueröffnung auf.Each turntable consists of a shaft and a fixedly connected rotor with the function of a rotary piston. Each rotary piston is a rotary body, which consists of two or three flat disc-shaped, integrally formed part discs, wherein two forming a pair of part discs intermesh. By sequential arrangement of the individual part discs of each rotor creates a catchy gradation and by cycloid-shaped formation of the connecting surfaces between the lateral surface and the core surface of each disc a self-contained, dense working chamber. On the suction side, this has a control opening designed to control the gas filling and, on the pressure side, a control opening designed to control the gas compression.

Zwei mehrstufige Drehkolben einer Ebene drehen sich in entgegengesetzter Richtung zueinander im Verhältnis 1:1 mit gleicher Geschwindigkeit. Zwei paarweise ineinandergreifende Drehkolben bzw. deren Teilscheiben saugen das Fördermedium in mehreren Stufen über Saugstutzen sowie über eine in einem Gehäuse angeordnete saugseitige Steueröffnung an und verdrängen es anschließend in die Arbeitskammern. Das Medium wird durch die jeweiligen Drehkolben beider Rotoren vorverdichtet und in der jeweiligen Förderkammer endverdichtet. Durch eine druckseitige Steueröffnung wird das Medium mit der gewünschten Gesamtkompression in einen Druckkanal übergeben.Two multi-stage rotary pistons of one plane rotate in the opposite direction to each other in the ratio 1: 1 with the same speed. Two pairs interlocking rotary pistons or their dividing discs suck the fluid in several stages via suction nozzle and a arranged in a housing suction-side control port and then displace it into the working chambers. The medium is precompressed by the respective rotary pistons of both rotors and finally compressed in the respective delivery chamber. By a pressure-side control port, the medium is transferred with the desired total compression in a pressure channel.

Bei dieser Lösung ist von Nachteil, dass während der Rotation der Rotoren starke einseitige radiale Belastungen auf die Wellen bzw. Lagerungen wirken, die auch auf die Getriebe übertragen werden. Die Belastungen auf die Rotorwelle entlang der Drehachse wirken sich nachteilig auf den Betrieb und die Lebensdauer von Pumpe oder Verdichter aus und begrenzen deren Einsatzmöglichkeiten.In this solution, it is disadvantageous that during the rotation of the rotors strong unilateral radial loads act on the shafts or bearings, which are also transmitted to the transmission. The loads on the rotor shaft along the axis of rotation have an adverse effect on the operation and the life of the pump or compressor and limit their applications.

Ein weiterer Nachteil besteht in dem mechanischen Flächenkontakt zweier ineinandergreifender Teilscheiben des Drehkolbens. Aufgrund der Reibung werden hohe Anforderungen an das Material der Drehkolben gestellt. Es besteht Gefahr, dass erhöhter Verschleiß auftritt mit der Folge von Dichtigkeitsverlusten.Another disadvantage is the mechanical surface contact of two intermeshing part discs of the rotary piston. Due to the friction become high demands placed on the material of the rotary piston. There is a risk that increased wear occurs with the result of leaks.

Die NL 7 509 751 wird als nächst liegender Stand der Technik angesehen und offenbart die Merkmale des Oberbegriffs des Anspruchs 1.The NL 7 509 751 is considered to be the closest prior art and discloses the features of the preamble of claim 1.

Der Erfindung liegt die Aufgabe zugrunde, einen Rotationskolbenverdichter bzw. eine Rotationskolbenpumpe zu schaffen, der bzw. die im Betriebszustand geringeren mechanischen Belastungen ausgesetzt ist und sich durch verbesserte anwendungstechnische Eigenschaften auszeichnet.The invention has for its object to provide a rotary piston compressor or a rotary piston pump, which is or is exposed in the operating state lower mechanical loads and is characterized by improved performance characteristics.

Erfindungsgemäß wird die Aufgabe durch die im Anspruch 1 angegebenen Merkmale gelöst. Vorteilhafte Ausgestaltungen und Weiterbildungen sind Gegenstand der Ansprüche 2 bis 15.According to the invention the object is achieved by the features specified in claim 1. Advantageous embodiments and further developments are subject matter of claims 2 to 15.

Die auf der Welle der Rotoreinheiten befestigte Scheibe ist kreisrund ausgebildet und besitzt mindestens einen Kolben, wobei ein Kolben aus zwei identischen Kolbenabschnitten in Form von Ringausschnitten besteht, die spiegelsymmetrisch zueinander, jeweils einer auf jeder Stirnseite der Scheibe, angeordnet sind. Identisch bedeutet hier, dass die beiden Kolbenabschnitte eines Kolbens in ihrer Geometrie, der Querschnittsform und In der Masse immer gleich sind. Die spiegelsymmetrisch angeordneten Kolbenabschnitte überragen die äußere Kante der zugehörigen Scheibe, bezogen auf ihre Bogenmaßlänge, mit dem gleichen Maß.The attached to the shaft of the rotor units disc is circular in shape and has at least one piston, wherein a piston consists of two identical piston sections in the form of ring cut-outs, which are arranged mirror-symmetrically to each other, one on each end face of the disc. Identical here means that the two piston sections of a piston in their geometry, the cross-sectional shape and in the mass are always the same. The mirror-symmetrically arranged piston sections project beyond the outer edge of the associated disk, with respect to their radian length, with the same dimension.

Der Abstand zwischen zwei benachbarten Rotoreinheiten ist so bemessen, dass deren in einer Ebene liegende Kolben im Betriebszustand in einem gemeinsamen Überschneidungsbereich berührungslos ineinanderkämmen.The distance between two adjacent rotor units is dimensioned so that their piston lying in a plane in the operating state in a common overlap region non-contact mesh.

Die Breite des Überschneidungsbereiches entspricht der Differenz zwischen Außen- und Innenradius der jeweiligen Kolben, die bei benachbarten Kolben gleich ist.The width of the overlap region corresponds to the difference between the outer and inner radii of the respective pistons, which is the same for adjacent pistons.

Der Überschneidungsbereich befindet sich an den Stellen wo sich die Kreisbahn des einen Kolbens der einen Rotoreinheit mit der Kreisbahn des Kolbens der benachbarten Rotoreinheit schneiden. Durch das berührungslose Ineinanderkämmen der benachbarten Kolben treten im Betriebszustand so gut wie keine Reibungsverluste auf, was von großem Vorteil ist.The overlap area is located at the points where the circular path of the one piston of a rotor unit intersect with the circular path of the piston of the adjacent rotor unit. As a result of the non-contact meshing of the adjacent pistons, practically no friction losses occur in the operating state, which is of great advantage.

Das Gehäuse der Pumpe bzw. des Verdichters besteht aus mindestens zwei Gehäusebauteilen mit einer ringförmigen Zylinderkammer zur Aufnahme der Kolbenabschnitte. Die Zylinderkammer ist durch einen zwischen zwei benachbarten Gehäusebauteilen angeordneten Zwischenring, der bis in den Zwischenraum zwischen zwei spiegelsymmetrisch angeordneten Kolbenabschnitten ragt, unterteilt.The housing of the pump or of the compressor consists of at least two housing components with an annular cylinder chamber for receiving the piston sections. The cylinder chamber is divided by a between two adjacent housing components arranged intermediate ring, which projects into the space between two mirror-symmetrically arranged piston sections.

Durch die Anbindung weiterer einzelner Rotoreinheiten besteht die Möglichkeit, Pumpe bzw. Verdichter nach Art eines Baukastenprinzips als einstufige oder mehrstufige Ausführung zu erweitern. Bei einer einstufigen Ausführung erfolgen "Saugen" und "Komprimieren" mittels mehrerer auf einer Ebene rotierender ineinanderkämmender Kolben. Im Gegensatz dazu erfolgen bei mehrstufigen Ausführungen die Arbeitsschritte "Saugen" und "Komprimieren" auf mehreren Ebenen gleichzeitig. Die einstufigen Einheiten sind für Niederdrücke und die mehrstufigen Einheiten für hohe Drücke vorgesehen.By connecting further individual rotor units, it is possible to expand the pump or compressor in the manner of a modular principle as a single-stage or multi-stage design. In a single-stage embodiment, "sucking" and "compressing" are accomplished by a plurality of interlocking pistons rotating on a plane. In contrast, the steps "sucking" and "multi-stage" are carried out "Compress" on several levels at the same time. The single-stage units are intended for low pressures and the multi-stage units for high pressures.

Die Basisvariante als einfachste Ausführung besteht aus zwei identischen Rotoreinheiten mit jeweils einer Scheibe und einem Kolben, wobei die Bogenmaßlänge der beiden Kolben jeweils 180° beträgt. Im Betriebszustand saugen die Kolben beider Rotoreinheiten abwechselnd mit ihrer in Saugrichtung zeigenden Seitenfläche das Fördermedium durch eine Einlassöffnung an und verdichten es mit ihrer anderen, in Kompressionsrichtung zeigenden Seitenfläche jeweils gegen die Mantelfläche des anderen benachbarten Kolbens, der den Überschneidungsbereich verschließt. Durch eine Auslassöffnung wird das verdichtete Fördermedium an einen Druckkanal übergeben.The basic version as the simplest version consists of two identical rotor units, each with a disc and a piston, wherein the radian gauge length of the two pistons is in each case 180 °. In the operating state, the pistons of both rotor units alternately suck the delivery medium through an inlet opening with their side face pointing in the suction direction and compress it with their other side face pointing in the compression direction against the lateral surface of the other adjacent piston which closes the overlap region. Through an outlet opening, the compressed fluid is transferred to a pressure channel.

Im Betriebszustand wirken während einer vollständigen Umdrehung die beiden Kolben abwechselnd als Arbeitskolben und Verschlusskolben. Bei allen anderen Ausführungsvarianten ist dies nicht der Fall, da bei diesen mindestens ein Kolben nur als Verschlusskolben wirkt und mindestens ein anderer benachbarter Kolben als Arbeitskolben.In the operating state, the two pistons act alternately as a working piston and closing piston during a complete revolution. In all other embodiments, this is not the case, since in these at least one piston acts only as a closure piston and at least one other adjacent piston as a working piston.

Die Kolbenabschnitte haben die Form eines Ringausschnittes oder die eines Teilringes. Die beiden schmalen Seitenflächen der Kolbenabschnitte besitzen vorzugsweise eine rechteckförmige oder quadratische Querschnittsfläche.The piston sections have the shape of a ring cutout or that of a partial ring. The two narrow side surfaces of the piston sections preferably have a rectangular or square cross-sectional area.

Zwei spiegelsymmetrisch angeordnete Kolbenabschnitte bilden funktionsgemäß eine Kolbenabschnittpaarung bzw. werden auch als Kolben bezeichnet. Der Außenradius der Kolben ist immer größer als der Außenradius der zugehörigen Scheibe. Das Maß, um das die beiden ringförmigen Kolbenabschnitte die zugehörige Scheibe überragen, ist für beide Kolbenabschnitte gleich und z.B. vom vorgegebenen Volumen des zu komprimierenden Mediums abhängig.Two mirror-symmetrically arranged piston sections functionally form a piston section pairing or are also referred to as pistons. The outer radius of the pistons is always larger than the outer radius of the associated disc. The extent to which the two annular piston sections project beyond the associated disk is the same for both piston sections, and e.g. dependent on the predetermined volume of the medium to be compressed.

Die spiegelsymmetrisch angeordneten, identischen Kolbenabschnitte, die die Scheibe der Rotorwelle in radialer Richtung überragen, führen zur Kompensierung einer einseitigen radialen Belastung entlang der radialen Achse, bzw. der Achse, die senkrecht zur Drehachse der Welle des Rotors ausgerichtet ist. Beide Kräfte kompensieren sich auf den Stirnseiten der jeweiligen Scheibe. Als Stirnseiten werden die Ober- und Unterseite bzw. Vorder- und Rückseite einer Scheibe bezeichnet.The mirror-symmetrically arranged, identical piston sections, which project beyond the disk of the rotor shaft in the radial direction, lead to the compensation of a one-sided radial load along the radial axis, or the axis which is aligned perpendicular to the axis of rotation of the shaft of the rotor. Both forces compensate each other on the front sides of the respective disc. As end faces the top and bottom or front and back of a disc are called.

Die Belastung auf der Rotorwelle wird somit durch zwei gegeneinander wirkende Kräfte aufgenommen.The load on the rotor shaft is thus absorbed by two opposing forces.

Dadurch werden im Vergleich zu herkömmlichen Drehkolbensystemen die Rotorwellen wesentlich geringeren Belastungen ausgesetzt. Somit können kostengünstigere Lager, wie z.B. Zylinderrollenlager, eingesetzt werden, ohne nachteilige Auswirkungen auf die Lebensdauer.As a result, the rotor shafts are exposed to much lower loads compared to conventional rotary piston systems. Thus, cheaper bearings, such as e.g. Cylindrical roller bearings are used without adversely affecting the life.

Die Welle, die Scheibe und die Kolbenabschnittpaarung bzw. Kolben haben bei einstufigen und mehrstufigen Ausführungen eine gemeinsame Drehachse und Radialachse. Außerdem ist auf jeder Rotoreinheit jeweils ein Zahnrad angeordnet, zur Synchronisierung mindestens zweier Rotoreinheiten.The shaft, the disc and the Kolbenabschnittpaarung or piston have a common axis of rotation and radial axis in single-stage and multi-stage designs. In addition, a gear is arranged on each rotor unit, for synchronizing at least two rotor units.

Eine Scheibe mit einer oder mehreren Kolbenabschnittpaarungen stellt immer einen Baukörper dar, der z.B. durch Gießen hergestellt wird, oder aus mehreren Teilen, die zu einer Funktionseinheit zusammengefügt werden. Die Scheiben haben ansonsten keine besondere Funktion.A disc with one or more pairs of piston sections always represents a structure, e.g. produced by casting, or of several parts, which are assembled into a functional unit. The discs otherwise have no special function.

Jeder Kolben kann durch eine oder mehrere zusätzlich auf der jeweiligen Scheibe angeordnete identische Kolbenabschnittpaarungen oder durch die Anordnung von Ausgleichsgewichten auf der Scheibe ausgewuchtet werden.Each piston can be balanced by one or more additionally arranged on the respective disc identical Kolbenabschnittpaarungen or by the arrangement of balancing weights on the disc.

Pumpe oder Verdichter mit zwei Rotoreinheiten mit je einem Kolben, die in einer Ebene liegen, können im Durchmesser und/oder in der Anzahl an Kolben unterschiedlich ausgeführt werden. Der Kolben mit dem kleineren Durchmesser wirkt als Verschlusskolben und der Kolben mit dem größeren Durchmesser als Arbeitskolben. In Analogie zur Funktionsweise der Kolben werden die Rotoreinheiten auch als Arbeitsrotoreinheit bzw. Verschlussrotoreinheit bezeichnet und die zugehörigen Scheiben als Arbeitsscheibe bzw. Verschlussseheibe.Pump or compressor with two rotor units, each with a piston, which lie in one plane, can be made different in diameter and / or in the number of pistons. The smaller diameter piston acts as a closure piston and the larger diameter piston acts as a working piston. In analogy to the mode of operation of the pistons, the rotor units are also referred to as a working rotor unit or shutter rotor unit and the associated disks as a working disk or closure disk.

Bei mindestens zwei nicht identischen Rotoreinheiten wirkt eine Rotoreinheit, die Fördermedlum ansaugt und komprimiert als Arbeitsrotoreinheit und eine andere als Verschlussrotoreinheit, da diese mit der Mantelfläche ihrer Kolben beide Arbeitsbereiche, Saugbereich und Kompressionsbereich, verschließt und wieder freigibt.In at least two non-identical rotor units acts a rotor unit, the Fördermedlabs sucks and compressed as Arbeitsrotoreinheit and another as a shutter rotor unit, as this closes with the lateral surface of their pistons both working areas, suction and compression area, and releases again.

Bei aus zwei Rotoreinheiten bestehenden Ausführungen beträgt die Bogenmaßlänge des Arbeitskolbens maximal 180° und die Bogenmaßlänge des Verschlusskolbens mindestens 180°.In versions consisting of two rotor units, the radian length of the working piston is a maximum of 180 ° and the radian length of the closure piston is at least 180 °.

Sind mehr als zwei Rotoreinheiten mit jeweils In einer Ebene liegenden Scheiben mit Kolben vorgesehen, so bildet ein Kolben (Verschlusskolben) immer mindestens zwei gemeinsame Kämmbereiche mit jeweils einem anderen Kolben (Arbeitskolben).If more than two rotor units with disks lying in one plane with pistons are provided, then a piston (closure piston) always forms at least two common combing areas, each with a different piston (working piston).

Mehrstufige Pumpen bzw. Verdichter können mit im Außendurchmesser unterschiedlich großen Scheiben und/oder mit einer unterschiedlichen großen Anzahl an Kolben ausgerüstet sein.Multi-stage pumps or compressors may be equipped with disks of different sizes in outer diameter and / or with a different large number of pistons.

Die Summe der Kreisbogenlänge zweier ineinanderkämmender Kolben entspricht dem Umfang eines Kreises mit dem Außenradius des Kolbens, der als Verschlusskolben wirkt, oder dem einer Bogenmaßlänge von 360°.The sum of the circular arc length of two intermeshing pistons corresponds to the circumference of a circle with the outer radius of the piston, which acts as a closure piston, or a radian length of 360 °.

Bei einer mehrstufigen Ausführung ist ein Gehäuse aus mehreren Gehäusebauteilen vorgesehen, für jede Stufe zwei Gehäusebauteile.In a multi-stage design, a housing of several housing components is provided, for each stage two housing components.

Das Gehäuse besitzt bei mindestens zwei Rotoreinheiten mindestens eine Saugöffnung mit Saugkanal zum Ansaugen des Fördermediums und mindestens einen Druckkanal für das komprimierte Medium. Der Saugkanal sowie der Druckkanal sind mit der ringförmigen Zylinderkammer der Arbeitsrotoreinheit verbunden, die das Ansaugen und Komprimieren durchführt. Bei zwei identischen Rotoreinheiten besitzen beide einen gemeinsamen Saug- und Druckkanal. Bei mindestens drei Rotoreinheiten besitzt jede Arbeitsrotoreinheit einen eigenen Saug- und einen eigenen Druckkanal.The housing has at least two rotor units at least one suction opening with a suction channel for sucking the pumped medium and at least one pressure channel for the compressed medium. The suction channel and the pressure channel are with the annular Cylinder chamber of the working rotor unit connected, which performs the suction and compression. With two identical rotor units both have a common suction and pressure channel. With at least three rotor units, each working rotor unit has its own suction and its own pressure channel.

Grundsätzlich sind im Gehäuse, im Überschneidungebereich zweier Kolben, ein Saugkenal zum Ansaugen von Fördermedium und gegenüberliegend zu diesem ein Druckkanal für komprimiertes Medium vorgesehen.In principle, in the housing, in the region of overlap of two pistons, a suction cup for sucking in conveying medium and opposite to this a pressure channel for compressed medium are provided.

Die ringförmige Zylinderkammer in den Gehäusebauteilen dient zur Aufnahme der Kolbenabschnitte und wird durch mindestens zwei sich überschneidende kreisförmige verlaufende Nuten in den Gehäusebauteilen gebildet.The annular cylinder chamber in the housing components serves to receive the piston sections and is formed by at least two intersecting circular grooves extending in the housing components.

Aufgrund der gegenläufigen Rotation der Kolben, insbesondere von Arbeits- und Verschlusskolben, zweier benachbarter Scheiben einer Ebene verändert sich das Raumvolumen in der zugehörigen kreisrunden Zylinderkammer zwischen zwei benachbarten Kolben.Due to the opposite rotation of the piston, in particular working and closure piston, two adjacent disks of a plane, the volume of space in the associated circular cylinder chamber changes between two adjacent pistons.

Die einstufigen Pumpen bzw. Verdichter sind für Niederdruckbereiche von bis zu ca. 20 bar vorgesehen. Je nach Anzahl der Rotoreinheiten können mehreren Saugkanäle und Druckkanäle vorhanden sein, wobei mehrere Druckkanäle in einem Druckspeicher zusammengeführt werden können.The single-stage pumps or compressors are designed for low pressure ranges of up to approx. 20 bar. Depending on the number of rotor units, multiple suction channels and pressure channels may be present, with multiple pressure channels can be combined in a pressure accumulator.

Mehrstufige Pumpen bzw. Verdichter sind für Hochdruckbereiche von bis zu ca. 500 bar vorgesehen. Die Komprimierung des Fördermediums erfolgt durch Vorverdichtung des Fördermediums in mindestens einer zusätzlichen Ebene. Die Endkomprimierung findet in der Haupt- bzw. letzten Ebene statt. Zwischen allen Ebenen sind Verbindungskanäle im Gehäuse für die Übertragung von vorverdichtetem Fördermedium von einer in die andere Ebene eingebracht. Bei einer mehrstufigen Ausführung Ist von Vorteil, dass mehrere standardisierte Bauteile einstufiger Ausführungen verwendet werden können.Multi-stage pumps or compressors are designed for high-pressure ranges of up to approx. 500 bar. The compression of the pumped liquid takes place by pre-compression of the pumped medium in at least one additional level. The final compression takes place in the main or last level. Between all levels connecting channels are placed in the housing for the transmission of precompressed fluid from one to the other level. In a multi-stage design is advantageous that several standardized components of single-stage versions can be used.

Die erfindungsgemäßen Pumpen bzw. Verdichter zeichnen sich durch eine einfache und kompakte Bauweise aus und ermöglichen einen Betrieb ohne Schmierung.The pumps or compressors according to the invention are characterized by a simple and compact design and enable operation without lubrication.

Die Erfindung soll nachstehend näher erläutert werden. In der zugehörigen Zeichnung zeigen:

Fig. 1
einen Verdichter mit zwei Rotoreinheiten, als Draufsicht,
Fig. 2
einen Schnitt gemäß der Linie A-A in Fig. 1,
Fig. 3
die Einzelheit C gemäß Fig. 2 in vergrößerter Darstellung,
Fig. 4
einen Schnitt gemäß der Linie B-B In Fig. 2,
Fig. 5
eine zweite Ausführungsvariante eines Verdichters mit zwei Rotoreinheiten, einem Verschlusskolben und drei Arbeitskolben, als Querschnittsdarstellung,
Fig. 6
eine dritte Ausführungsvariante eines Verdichters mit drei Rotoreinheiten, als Querschnittdarstellung.
Fig. 7
eine vierte Ausführungsvariante eines Verdichters mit vier Rotoreinheiten, als Querschnittdarstellung,
Fig. 8
eine fünfte Ausführungsvariante eines Verdichters mit zehn Rotoreinheiten, als Querschnittdarstellung,
Fig. 9
die Anordnung einer mehrstufigen Ausführung eines Verdichters in vereinfachter Darstellung.
The invention will be explained in more detail below. In the accompanying drawing show:
Fig. 1
a compressor with two rotor units, as plan view,
Fig. 2
a section along the line AA in Fig. 1 .
Fig. 3
the detail C according to Fig. 2 in an enlarged view,
Fig. 4
a section along the line BB In Fig. 2 .
Fig. 5
A second embodiment of a compressor with two rotor units, a closure piston and three working pistons, as a cross-sectional view,
Fig. 6
a third embodiment of a compressor with three rotor units, as a cross-sectional view.
Fig. 7
A fourth embodiment of a compressor with four rotor units, as a cross-sectional view,
Fig. 8
a fifth embodiment of a compressor with ten rotor units, as a cross-sectional representation,
Fig. 9
the arrangement of a multi-stage design of a compressor in a simplified representation.

In den Figuren 1 bis 4 ist eine erste Ausführungsvariante eines Verdichters gezeigt, der aus zwei zentrisch gelagerten und achsparallel zueinander gegenläufig drehbaren Rotoreinheiten 8, 12 besteht, die identisch ausgebildet und in einem Gehäuse, bestehend aus zwei Gehäusebauteilen 1, 2, in einer Ebene angeordnet sind.In the FIGS. 1 to 4 a first embodiment of a compressor is shown, which consists of two centrally mounted and axially parallel to each other in opposite directions rotatable rotor units 8, 12, which are identical and arranged in a housing, consisting of two housing components 1, 2, in a plane.

Jede Rotoreinheit 8, 12 besteht aus einer Rotorwelle 9, 13 mit jeweils einer drehfest angeordneten kreisrunden Scheibe 10, 14.Each rotor unit 8, 12 consists of a rotor shaft 9, 13, each with a rotationally fixed circular disc 10, 14th

Auf beiden Stirnseiten jeder Scheibe 10, 14 ist ein ringförmiger Kolbenabschnitt 10b, 14b angeordnet. Die beiden Kolbenabschnitte 10b oder 14b jeweils einer Scheibe 10, 14 sind identisch ausgeführt und spiegelsymmetrisch angeordnet. Dies trifft für alle erfindungsgemäßen Ausführungen zu. Identisch bedeutet hier, gleiche Geometrie, Masse und Querschnittform. Die Querschnittsform ist in den gezeigten Beispielen rechteckig.On both end faces of each disc 10, 14, an annular piston portion 10b, 14b is arranged. The two piston sections 10b or 14b each of a disc 10, 14 are identical and arranged mirror-symmetrically. This applies to all embodiments according to the invention. Identical here means the same geometry, mass and cross-sectional shape. The cross-sectional shape is rectangular in the examples shown.

Die Kolbenabschnitte 10b, 14b sind so angeordnet, dass diese die zugehörige Scheibe 10, 14 in radialer Richtung gleichmäßig überragen. Demzufolge überragen die Kolbenabschnitte die äußere Kante der zugehörigen Scheibe, bezogen auf ihre Bogenmaßlänge, mit gleichem Maß. Der Überstand bzw. das Maß, um das die ringförmigen Kolbenabschnitte die zugehörige Scheibe überragen, ist z.B. vom vorgegebenen Arbeitsvolumen abhängig.The piston portions 10b, 14b are arranged so that they project beyond the associated disc 10, 14 in the radial direction uniformly. As a result, the piston sections project beyond the outer edge of the associated disc, with respect to their radian length, to the same extent. The supernatant or extent to which the annular piston portions project beyond the associated disc is e.g. depending on the given work volume.

In der Fig. 3 sind die im Betriebszustand radial auf die Scheibenmantelfläche wirkenden Kräfte gezeigt. Die Kraft Fr wird in zwei gleichgroße axiale Kräfte F1 und F2 transformiert bzw. zerlegt, die in gegenläufiger Richtung wirken, wobei F1 = F2.In the Fig. 3 the forces acting radially on the disk surface in the operating state are shown. The force Fr is transformed into two equal axial forces F1 and F2 acting in opposite directions, where F1 = F2.

Beide Kräfte kompensieren sich auf der Stirnseite der jeweiligen Scheibe. Die Belastung auf der Rotorwelle wird somit durch zwei gegeneinander wirkende Kräfte aufgenommen. Die beiden spiegelsymmetrisch angeordneten Kolbenabschnitte einer Scheibe bilden in ihrer Funktion jeweils einen Kolben 10a bzw. 14a. Im Betriebszustand übernehmen die Kolben beider Scheiben während einer Umdrehung (360°) wechselseitig die Funktion als Arbeitskolben und Verschlusskolben. Dies ist jedoch nur bei der in den Figuren 1 bis 4 gezeigten Ausführungsvariante der Fall.Both forces compensate each other on the front side of the respective disc. The load on the rotor shaft is thus absorbed by two opposing forces. The two mirror-symmetrically arranged piston sections of a disk in their function respectively form a piston 10a or 14a. In the operating state, the pistons of both discs alternately assume the function of a working piston and closure piston during one revolution (360 °). However, this is only in the case of FIGS. 1 to 4 shown embodiment of the case.

Gegenüberliegend zu den Kolbenabschnitten 10b, 14b sind auf jeder Stirnseite der Scheiben 10, 14 Ausgleichsgewichte 10c, 14c angeordnet (Fig. 2). Jedem Kolbenabschnitt Ist erforderlichenfalls ein Ausgleichsgewicht zugeordnet, um im Betriebszustand den erforderlichen Rundlauf zu gewährleisten. Die Scheibe, die zugehörigen Kolbenabschnitte und die Ausgleichsgewichte bilden eine kompakte Baueinheit.Opposite to the piston sections 10b, 14b, balancing weights 10c, 14c are arranged on each end face of the discs 10, 14 ( Fig. 2 ). Each piston section is assigned, if necessary, a balance weight to the required in the operating state To ensure concentricity. The disc, the associated piston sections and the balance weights form a compact unit.

Der Abstand zwischen den zwei benachbarten Scheiben 10 und 14 ist so bemessen, dass deren in einer Ebene liegende Kolben im Betriebszustand in einem gemeinsamen Überschneidungsbereich berührungslos ineinanderkämmen. Dieser Bereich befindet sich an den Stellen wo sich die Kreisbahn des einen Kolbens der einen Rotoreinheit mit der Kreisbahn des Kolbens der benachbarten Rotoreinheit schneidet (Fig. 4). Der Überschneidungsbereich entspricht der Differenz zwischen Außen- und Innenradius der jeweiligen Kolben, die bei benachbarten Kolben gleich ist.The distance between the two adjacent disks 10 and 14 is dimensioned so that their piston lying in a plane in the operating state in a common overlap region non-contact mesh. This region is located at the points where the circular path of the one piston of a rotor unit intersects with the circular path of the piston of the adjacent rotor unit ( Fig. 4 ). The overlap area corresponds to the difference between the outer and inner radius of the respective pistons, which is the same for adjacent pistons.

Bei der in den Figuren 1 bis 4 gezeigten Ausführungsvariante beträgt die Bogenmaßlänge beider benachbarter Kolben jeweils 180°. Wenn die Bogenmaßlänge des Arbeitskolbens kleiner als 180° ist, so ist die Bogenmaßlänge des Verschlusskolbens um den Differenzbetrag zu 180° größer als 180°. Dadurch kann das erforderliche Kompressionsvolumen realisiert werden.In the in the FIGS. 1 to 4 shown embodiment, the radian length of both adjacent pistons is 180 °. If the radian measurement length of the working piston is less than 180 °, the radian length of the closure piston is 180 ° greater than 180 ° by the difference. As a result, the required compression volume can be realized.

In beiden Gehäusebauteilen 1, 2 befinden sich in einer Ebene ringförmige Nuten, im ersten Gehäusebauteil 1 ringförmige Nuten 4a und im zweiten Gehäusebauteil 2 ringförmige Nuten 4b, die unmittelbar aneinandergrenzen und die Zylinderkammer 4 bilden. Der nutenförmige Abschnitt 4.1 ist zur Aufnahme des Arbeitskolbens 10a und der nutenförmige Abschnitt 4.2 zur Aufnahme des Verschlusskolbens 14a bestimmt.In two housing components 1, 2 are in a plane annular grooves, in the first housing member 1 annular grooves 4a and in the second housing member 2 annular grooves 4b, which adjoin one another directly and form the cylinder chamber 4. The groove-shaped section 4.1 is intended for receiving the working piston 10a and the groove-shaped section 4.2 for receiving the closure piston 14a.

Im Betriebszustand rotieren die ringförmigen Kolbenabschnitte in den Nuten, die in ihrer Geometrie auf die Querschnittsform der Kolbenabschnitte abgestimmt sind.In operation, the annular piston sections rotate in the grooves, which are tuned in their geometry to the cross-sectional shape of the piston sections.

Aus fertigungstechnischen Gründen wird als Querschnittform die Rechteckform bevorzugt. Geeignet sind jedoch auch andere Querschnittformen, wie z.B. rund oder oval. Nach der Montage der Gehäusebauteile 1 und 2 (Fig. 2) entsteht durch die beiden ringförmigen Nuten 4.1 und 4.2 in den Gehäusebauteilen eine gemeinsame umlaufende ringförmige Zylinderkammer 4 als kurvenförmig verlaufende Acht. Wie in Fig. 4 zu sehen, wird die Zylinderkammer 4 durch zwei sich überschneidende kreisförmige verlaufende, spiegelverkehrt angeordnete Nuten 4a, 4b der benachbarten Gehäusebauteile 1, 2 gebildet.For manufacturing reasons, the rectangular shape is preferred as a cross-sectional shape. Also suitable, however, are other cross-sectional shapes, such as round or oval. After mounting the housing components 1 and 2 ( Fig. 2 ) is formed by the two annular grooves 4.1 and 4.2 in the housing components, a common circumferential annular cylinder chamber 4 as a curved extending eight. As in Fig. 4 can be seen, the cylinder chamber 4 by two overlapping circular extending, mirror-inverted arranged grooves 4a, 4b of the adjacent housing components 1, 2 is formed.

Die Gehäusebauteile 1, 2 sind konstruktiv so ausgelegt, dass die auf der Arbeitsscheibe 10 und die auf der Verschlussscheibe 14 angeordneten Ausgleichsgewichte 10c, 14c durch eine umlaufende Gehäuseinnenwand von den Kolbenabschnitten getrennt sind (Fig. 2). In den Gehäusebauteilen 1, 2 befinden sich im zusammengebauten Zustand jeweils eine Saugöffnung 5a, die in einen Saugkanal 5 münden (Fig. 4). Um 180° versetzt ist zu der Saugöffnung 5a oder den Saugöffnungen in den Gehäusebauteilen 1, 2 eine Drucköffnung 6a vorgesehen, die mit einem Druckkanal 6 für das komprimierte Medium in Verbindung steht. Zwischen den zwei montierten Gehäusebauteilen 1 und 2 ist ein Zwischenring 3 ange-ordnet, der bis unmittelbar an die gegenläufig rotierenden Scheiben einer Ebene heranreicht und den ringförmigen Zwischenraum zwischen zwei spiegelsymmetrisch angeordneten Kolbenabschnitten 10b und 14b ausfüllt, unter Berücksichtigung eines ausreichenden Spiels für eine reibungsfreie Rotation der Scheiben 10 und 14.The housing components 1, 2 are structurally designed so that the balancing weights 10c, 14c arranged on the working disk 10 and on the closure disk 14 are separated from the piston portions by a circumferential housing inner wall ( Fig. 2 ). In the housing components 1, 2 are in the assembled state in each case a suction opening 5a, which open into a suction channel 5 ( Fig. 4 ). Offset by 180 ° to the suction opening 5a or the suction openings in the housing components 1, 2, a pressure port 6a is provided, which is in communication with a pressure channel 6 for the compressed medium. Between the two mounted housing components 1 and 2 is a Arranged intermediate ring 3, which extends to directly to the counter-rotating disks of a plane and the annular space between two mirror-symmetrically arranged piston portions 10b and 14b fills, taking into account a sufficient clearance for a frictionless rotation of the discs 10 and 14th

An den freien Enden der aus dem Gehäusebauteil 1 hervorstehenden Wollen 9 und 13 (Fig. 1) ist jeweils ein Zahnrad befestigt, an der Arbeitsrotorwelle 9 das Zahnrad 11 und an der Verschlussrotorwelle 13 das Zahnrad 15. Die zwei Zahnräder 11, 15 greifen ineinander und bilden ein Getriebe, über das die Drehbewegungen der beiden Wellen 9, 13 synchronisiert werden. Das Zahnradgetriebe ist bei dieser Ausführungsvariante so ausgelegt, dass sich die Arbeitsrotorwelle 9 zu der Verschlussrotorwelle 13 im Verhältnis 1:1 dreht. Die beiden Wellen 9, 13 sind in entsprechenden Zylinderrollenlagem 7 der Gehäusebauteile 1, 2 gelagert, wobei für jede Welle zwei Lagerstellen vorgesehen sind. Die Arbeitsscheibe und Verschlussscheibe sowie die Zahnräder werden beispielsweise mittels Keilwellenverbindungen auf der jeweiligen Welle befestigt und mittels an sich bekannter Mittel gegen Verdrehen gesichert.At the free ends of the protruding from the housing part 1 wools 9 and 13 ( Fig. 1 In each case a gear is fixed to the working rotor shaft 9, the gear 11 and the shutter rotor shaft 13, the gear 15. The two gears 11, 15 engage each other and form a gear via which the rotational movements of the two shafts 9, 13 are synchronized. The gear transmission is designed in this embodiment so that the working rotor shaft 9 rotates to the shutter rotor shaft 13 in the ratio 1: 1. The two shafts 9, 13 are mounted in corresponding cylindrical roller bearings 7 of the housing components 1, 2, wherein two bearings are provided for each shaft. The working disk and shutter disk and the gears are fastened, for example by means of splined connections on the respective shaft and secured by means known per se against rotation.

Die Arbeitsweise der in den Figuren 1 bis 4 gezeigten Ausführung ist folgende: Die erforderlichen Verfahrensschritte "Ansaugen" und "Verdichten" erfolgen gleichzeitig. Über ein geeignetes Antriebssystem und das Zahnradgetriebe 11, 15 werden die beiden Rotorwellen 9 und 13 in entgegengesetzter Richtung in Rotation versetzt. Die Drehrichtungen sind in den Figuren 1 und 4 durch Pfeile gekennzeichnet.The way of working in the FIGS. 1 to 4 the embodiment shown is the following: The required process steps "suction" and "compaction" occur simultaneously. By means of a suitable drive system and the toothed gearing 11, 15, the two rotor shafts 9 and 13 are set in rotation in the opposite direction. The directions of rotation are in the FIGS. 1 and 4 indicated by arrows.

Während der Rotation der Rotorwellen 9, 13 wird über den Arbeitskolbens 10a Fördermedium durch den Saugkanal 5 angesaugt und dieses gegen die Mantelfläche des Kolbens 14a verdichtet. Gleichzeitig mit dieser Bewegung gelangt der synchron rotierende Verschlusskolben 14a in den Überschneidungsbereich und verschließt diesen mittels seiner Mantelfläche. Durch die Drehbewegung der Kolben 10a, 14a werden im Bereich der ringförmigen Nuten 4.1 und 4.2 eine Saugkammer S und eine Kompressionskammer K gebildet, die durch die freien Seitenflächen des einen Kolbens und die Mantelfläche des anderen Kolbens begrenzt sind, wie in Fig. 4 gezeigt.During the rotation of the rotor shafts 9, 13, via the working piston 10 a, the conveying medium is sucked through the suction channel 5 and this is compressed against the lateral surface of the piston 14 a. Simultaneously with this movement, the synchronously rotating closure piston 14a enters the overlap region and closes it by means of its lateral surface. By the rotational movement of the pistons 10a, 14a, a suction chamber S and a compression chamber K are formed in the region of the annular grooves 4.1 and 4.2, which are bounded by the free side surfaces of one piston and the lateral surface of the other piston, as in Fig. 4 shown.

Die Saugseite (Saugkammer S und Saugkanal 5) und die Kompressionsseite (Kompressionskammer K und Kompressionskanal 6) sind verschlossen bzw. abgetrennt.The suction side (suction chamber S and suction channel 5) and the compression side (compression chamber K and compression channel 6) are closed or separated.

Der Kolben 14a der zweiten Rotoreinheit 12 wirkt als Verschlusskolben.The piston 14a of the second rotor unit 12 acts as a closure piston.

Nach einer Drehbewegung von 180° beider Kolben 10a, 14a saugt der Kolben 14a Fördermedium aus dem Saugkanal 5 in die saugseitig angeordnete ringförmige Nut 4.2 und verdichtet dabei das Fördermedium in der Kompressionskammer K gegen die Mantelfläche des Kolbens 10a der ersten Rotoreinheit 8.After a rotational movement of 180.degree. Of both pistons 10a, 14a, the piston 14a sucks conveying medium out of the suction channel 5 into the annular groove 4.2 arranged on the suction side, thereby compressing the conveying medium in the compression chamber K against the lateral surface of the piston 10a of the first rotor unit 8.

Der Kolben 10a der ersten Rotoreinheit trennt bzw. verschließt den saugseitigen und den kompressionsseitigen Bereich der Zylinderkammer und erfüllt damit die Funktion eines Verschlusskolbens. Beide Prozesse "Saugen" und "Komprimieren" erfolgen bei jeder 180° Umdrehung der beiden Kolben 10a, 14a gleichzeitig. Damit übernehmen die Kolben der ersten Rotoreinheit 8 und der zweiten Rotoreinheit 12 während einer vollständigen Umdrehung abwechselnd nacheinander nach jeder 180° Umdrehung die Funktion als Arbeits- bzw. Verschlusskolben.The piston 10a of the first rotor unit separates and closes the suction side and the compression side region of the cylinder chamber, thereby fulfilling the function of a shutter piston. Both processes "sucking" and "compressing" occur at each 180 ° rotation of the two pistons 10a, 14a simultaneously. Thus assume the piston of the first rotor unit 8 and the second rotor unit 12 during a complete revolution alternately successively after each 180 ° rotation, the function as a working or closure piston.

In Fig. 5 ist eine zweite Ausführungsvariante als Querschnittsdarstellung gezeigt, in Blickrichtung auf das untere Gehäusebauteil 2. Diese Ausführung unterscheidet sich von der vorhergehenden Ausführung gemäß Figuren 1 bis 4 dadurch, dass die zwei Rotoreinheiten 22, 25 Scheiben 27, 24 und Kolben 27a, 24a mit unterschiedlichem Durchmesser bzw. Außenradius besitzen, wobei der Kolben 27a mit dem kleineren Außenradius Verschlusskolben ist und mit drei Arbeitskolben 24a, 24b, 24c in einer Ebene zusammenwirkt. Das Ineinanderkämmen des Verschlusskolbens 27a mit jedem Arbeitskolben 24a, 24b, 24c erfolgt immer nacheinander während einer 360° Umdrehung der Arbeitsrotoreinheit 22. Dem Verschlusskolben 27a sind drei identische Arbeitskolben 24a, 24b, 24c mit gleicher Bogenmaßlänge zugeordnet, die jeweils um 120° zueinander versetzt sind.In Fig. 5 a second embodiment variant is shown as a cross-sectional view, in the direction of the lower housing component 2. This embodiment differs from the previous embodiment according to FIGS. 1 to 4 in that the two rotor units 22, 25 have discs 27, 24 and pistons 27a, 24a of different diameter or outer radius, the piston 27a having the smaller outer radius being a closure piston and cooperating with three working pistons 24a, 24b, 24c in one plane. The interlocking of the closure piston 27a with each working piston 24a, 24b, 24c always takes place successively during a 360 ° rotation of the working rotor unit 22. The closure piston 27a is associated with three identical working pistons 24a, 24b, 24c with the same radian length, which are each offset by 120 ° to each other ,

Nach jeder 120° Umdrehung der Arbeitsrotoreinheit 22 kämmt ein Arbeitskolben 24a, 24b, 24c berührungslos mit dem Verschlusskolben 27a. Die Vorgänge "Saugen" und "Verdichten" erfolgen gleichzeitig durch die jeweiligen Arbeitskolben. Während der Arbeitskolben 24a Fördermedium ansaugt, verdichtet der Arbeitskolben 24c Fördermedium gegen die Mantelfläche des Verschlusskolbens 27a. Zwischen den Arbeitskolben 24a und 24b sowie zwischen den Arbeitskolben 24b und 24c wird Fördermedium ohne zu verdichten in der Zylinderkammer 4 transportiert. In analoger Weise, wie bei der Ausführung gemäß der Figuren 1 bis 4, sind auch bei dieser Ausführung Saugöffnung 5a, Saugkanal 5, Druckkanalöffnung 6a und Druckkanal 6 vorgesehen sowie eine Saugkammer S und eine Druckkammer K. Die Rotoreinheiten 22 und 25 sind in üblicher Bauweise mit Rotorwellen 23 und 26 ausgerüstet.After every 120 ° rotation of the working rotor unit 22, a working piston 24a, 24b, 24c meshes with the closure piston 27a without contact. The processes "suction" and "compression" are carried out simultaneously by the respective working piston. While the working piston 24a sucks in the conveying medium, the working piston 24c compresses the conveying medium against the lateral surface of the closing piston 27a. Between the working piston 24a and 24b and between the working piston 24b and 24c conveying medium is transported without compressing in the cylinder chamber 4. In an analogous manner, as in the embodiment according to the FIGS. 1 to 4 , In this embodiment, suction opening 5a, suction channel 5, pressure channel opening 6a and pressure channel 6 are provided and a suction chamber S and a pressure chamber K. The rotor units 22 and 25 are equipped in conventional construction with rotor shafts 23 and 26.

Die in Figur 6 gezeigte dritte Ausführung besteht im Unterschied zu der ersten Ausführung nicht aus zwei sondern aus drei identischen Rotoreinheiten 8, 12, 16 mit jeweils einer Rotorwelle 9, 13, 17 mit einer kreisrunden Scheibe 10, 14, 18, wobei jede kreisrunde Scheibe an ihren Stirnseiten jeweils einen ringförmigen Kolbenabschnitt 10b, 14b, 18b aufweist. Die Kolben 10a, 14a und 18a sind analog wie bei der in den Figuren 1 bis 4 gezeigten Ausführung. Bei drei oder mehr in einer Reihe verbundenen Rotoreinheiten ist die Verschlussrotoreinheit 12 immer zwischen zwei Arbeitsrotoreinheiten 8, 16 angeordnet.In the FIG. 6 shown third embodiment, in contrast to the first embodiment not two but three identical rotor units 8, 12, 16, each having a rotor shaft 9, 13, 17 with a circular disc 10, 14, 18, each circular disc at their end faces respectively an annular piston portion 10b, 14b, 18b has. The pistons 10a, 14a and 18a are analogous to those in the FIGS. 1 to 4 shown execution. With three or more rotor units connected in a row, the shutter rotor unit 12 is always arranged between two working rotor units 8, 16.

Der Arbeitskolben 18a der dritten Rotoreinheit 16 bildet wie der Kolben 10a der ersten Rotoreinheit 8 mit dem benachbarten Kolben 14a der zweiten Rotoreinheit 12 einen Überschneidungsbereich, wo jeweils zwei benachbarte Kolben zeitversetzt ineinanderkämmen. Die zwischen zwei Rotoreinheiten 8, 16 mittig angeordnete Rotoreinheit 12 ist infolge ihrer Funktion immer Verschlussrotoreinheit, da der Verschlusskolben 14a den Saug- bzw. Kompressionsbereich beider benachbarter Arbeitsrotoreinheiten 8, 16 schließt. Der Verschlusskolben 14a schließt mit seiner Mantelfläche die Saug- S und Kompressionsbereiche K der Zylinderkammer (im Abschnitt 4.1) der ersten Arbeitsrotoreinheit 8 und danach die Zylinderkammer (im Abschnitt 4.3) der zweiten Arbeitsrotoreinheit 16.The working piston 18a of the third rotor unit 16, like the piston 10a, forms the first rotor unit 8 with the adjacent piston 14a of the second rotor unit 12 Overlapping area, where each two adjacent pistons mesh with a time delay. The rotor unit 12, which is arranged centrally between two rotor units 8, 16, is always a shutter rotor unit due to its function, since the closing piston 14a closes the suction or compression area of both adjacent working rotor units 8, 16. The closure piston 14a closes with its lateral surface the suction S and compression regions K of the cylinder chamber (in section 4.1) of the first working rotor unit 8 and then the cylinder chamber (in section 4.3) of the second working rotor unit 16th

Die erste Arbeitsrotoreinheit 8 und die zweite Arbeitsrotoreinheit 16 haben jeweils einen eigenen mit der jeweiligen Zylinderkammer 4.1, 4.3 verbundenen Saugkanal 5 mit jeweiliger Saugöffnung 5a sowie einen eigenen ebenfalls mit der jeweiligen Zylinderkammer verbundenen Druckkanal 6 mit jeweiliger Druckkanalöffnung 6a. Zur Vereinfachung sind Saug- und Druckkanäle beider Rotoreinheiten identisch bezeichnet. Die Saugkanäle und die Druckkanäle der ersten Arbeitsrotoreinheit 8 und der zweiten Arbeitsrotoreinheiten 16 sind um 180° versetzt im Gehäuse angeordnet.The first working rotor unit 8 and the second working rotor unit 16 each have their own suction channel 5 connected to the respective cylinder chamber 4.1, 4.3 with respective suction opening 5a as well as a separate pressure channel 6 also connected to the respective cylinder chamber with respective pressure channel opening 6a. For simplicity, suction and pressure channels of both rotor units are designated identically. The suction channels and the pressure channels of the first working rotor unit 8 and the second working rotor units 16 are arranged offset by 180 ° in the housing.

Aufgrund der Überschneidung der im Durchmesser drei gleichen kreisförmigen Öffnungen entsteht eine Querschnittsfläche, deren äußere Kontur in ihrer Form drei reihenweise angeordneter und sich überschneidender Kreise entspricht.Due to the intersection of the same diameter three circular openings creates a cross-sectional area whose outer contour corresponds in shape three rows arranged and intersecting circles.

Der Verschlusskolben 14a der Verschlussrotoreinheit 12 hat immer die Funktion, die saugseitigen Bereiche sowie die kompressionsseitigen Bereiche der Zylinderkammer 4.1, 4.3 zu verschließen.The closure piston 14a of the closure rotor unit 12 always has the function of closing the suction-side regions as well as the compression-side regions of the cylinder chamber 4.1, 4.3.

In Betriebszustand saugt der Arbeitskolben 10a aus dem Saugkanal 5 während einer 180° Umdrehung Fördermedium mit der saugseitig gesehenen rechteckförmigen Seitenfläche des Kolbens durch Drehbewegung in Uhrzeigerrichtung und komprimiert Fördermedium mit seiner gegenüberliegenden, rechteckförmigen Seitenfläche gegen die Mantelfläche des Verschlusskolbens 14a.In the operating state, the working piston 10 a sucks from the suction channel 5 during a 180 ° rotation conveying medium with the suction side seen rectangular side surface of the piston by rotation in a clockwise direction and compresses the medium with its opposite, rectangular side surface against the lateral surface of the closure piston 14 a.

Während dieses Vorganges schließt der in Uhrzeigerrichtung rotierende zweite Arbeitskolben 18a mit seiner Mantelfläche den benachbarten Saug- 5 und Druckkanal 6 und damit die Verbindung zur ringförmigen Zylinderkammer (Abschnitt 4.2). Nach einer Umdrehung von 180° saugt der zweite Arbeitskolben 18a aus seinem Saugkanal 5 Fördermedium mit seiner saugseitig gesehenen rechteckförmigen Seitenfläche durch seine Drehbewegung und komprimiert es mit seiner gegenüberliegenden rechteckförmigen Seitenfläche gegen die Mantelfläche des Verschlusskolbens 14a. Der Verschlusskolben 14a schließt mit seiner Mantelfläche während einer Drehung um 180° die ringförmige Zylinderkammer (Abschnitt 4.1) der ersten Arbeitsrotoreinheit 8 und nach einer weiteren Drehung um 180° die ringförmige Zylinderkammer (Abschnitt 4.3) der zweiten Arbeitsrotoreinheit 16, sodass Innerhalb einer vollständiger Umdrehung um 360° beide Arbeitsrotoreinheiten den Saug- und den Kompressionsvorgang jeweils um 180° versetzt nacheinander ausführen.During this process, the clockwise rotating second working piston 18a closes with its lateral surface the adjacent suction 5 and pressure channel 6 and thus the connection to the annular cylinder chamber (Section 4.2). After a rotation of 180 °, the second working piston 18a draws from its suction channel 5 conveying medium with its suction side seen rectangular side surface by its rotational movement and compresses it with its opposite rectangular side surface against the lateral surface of the closure piston 14a. The closure piston 14a closes with its lateral surface during a rotation through 180 °, the annular cylinder chamber (section 4.1) of the first working rotor unit 8 and after another rotation through 180 °, the annular cylinder chamber (section 4.3) of the second working rotor unit 16, so within a complete revolution to 360 ° both working rotor units the suction and the compression process offset by 180 ° in succession.

Um den erforderlichen Rundlauf zu gewährleisten sind an den jeweiligen Scheiben noch Ausgleichsgewichte 10c, 14c und 18c befestigt.In order to ensure the required concentricity still balance weights 10c, 14c and 18c are attached to the respective discs.

Als vierte Ausführungsvariante ist in Fig. 7 eine sternförmige Anbindung von drei Arbeitsrotoreinheiten 8, 16, 19 um eine zentrisch bzw. mittig angeordnete Verschlussrotoreinheit 12 gezeigt. Dabei ist der Winkel zwischen der Drehachse der Verschlussrotoreinheit zur Drehachse jeder Arbeitsrotoreinheit von der Anzahl der Arbeitsrotoreinheiten abhängig und beträgt z.B. bei Anordnung von drei Arbeitsrotoreinheiten 120° und bei Anordnung von vier Arbeitsrotoreinheiten 90°.As the fourth embodiment variant is in Fig. 7 a star-shaped connection of three working rotor units 8, 16, 19 to a centrally or centrally arranged shutter rotor unit 12 is shown. In this case, the angle between the axis of rotation of the shutter rotor unit to the axis of rotation of each working rotor unit depends on the number of working rotor units and is, for example, with the arrangement of three working rotor units 120 ° and with the arrangement of four working rotor units 90 °.

Bei der in Fig. 7 gezeigten Ausführung kämmt der Verschlusskolben 14a der mittig angeordneten Verschlussrotoreinheit 12 immer nacheinander mit den jeweiligen Arbeitskolben 10a, 18a, 21 a. Dabei entsteht jeweils ein gleich großer Überschneidungsbereich mit jedem Arbeitskolben der jeweiligen Arbeitsrotoreinheiten. Auf einer Arbeitsscheibe können auch mehrere Arbeitskolben angeordnet sein.At the in Fig. 7 In the embodiment shown, the closure piston 14a of the centrally arranged shutter rotor unit 12 always meshes successively with the respective power pistons 10a, 18a, 21a. In each case, an equally large overlap area arises with each working piston of the respective working rotor units. On a work disk and several working piston can be arranged.

Die Arbeitsrotoreinheiten 8, 16 und 19 sind analog wie die in Fig. 6 gezeigten Einheiten ausgeführt. Der Verschlusskolben 14a der mittig angeordneten Verschlussrotoreinheit 12 ist im Durchmesser kleiner als die Kolben der Arbeitsrotoreinheiten.The work rotor units 8, 16 and 19 are analogous to those in Fig. 6 executed units executed. The closure piston 14a of the centrally arranged shutter rotor unit 12 is smaller in diameter than the pistons of the working rotor units.

Gemäß einer fünften Ausführungsvariante (Fig. 8) können auch mehrere Arbeitsrotoreinheiten und mehrere Verschlussrotoreinheiten achsparallel kreisförmig miteinander verbun-den werden, dabei ist die Anzahl der Arbeits- und Verschlussrotoreinheiten gleich und eine Verschlussrotoreinheit muss immer zwischen zwei Arbeitsrotoreinheiten angeordnet sein. Wie in Fig. 8 gezeigt, sind die einzelnen Arbeitsrotoreinheiten mit zwei identischen Arbeitskolben 10a ausgerüstet, wobei jeder Arbeitskolben 10a eine Bogenmaßlänge von 80° besitzt. Die im Durchmesser kleineren Verschlussrotoreinheiten sind nur mit einem Verschlusskolben 14a mit einer Bogenmaßlänge von 170° ausgerüstet. Bisher bereits erwähnte Bauteile sind mit gleichen Bezugszeichen gekennzeichnet.According to a fifth embodiment ( Fig. 8 ) can also be several working rotor units and a plurality of shutter rotor units axially parallel circular verbun-related, the number of working and shutter rotor units is the same and a shutter rotor unit must always be arranged between two working rotor units. As in Fig. 8 As shown, the individual working rotor units are equipped with two identical working pistons 10a, each working piston 10a having a radian length of 80 °. The smaller diameter shutter rotor units are equipped only with a shutter piston 14a with a radian length of 170 °. Previously mentioned components are identified by the same reference numerals.

Das Zusammenwirken zweier ineinanderkämmender benachbarter Kolben ist analog wie bei den anderen gezeigten Ausführungen. Jede Arbeitsrotoreinheit kann zwei eigene, versetzt zu einander an der jeweiligen Zylinderkammer angeschlossene Saugkanäle sowie zwei eigene ebenfalls versetzt zu einander an der Zylinderkammer angeschlossene Druckkanäle besitzen. Wie in Fig. 8 gezeigt, besitzt jede Arbeitsrotoreinheit jeweils eine Arbeitsscheibe, auf der jeweils zwei identische Arbeitskolben symmetrisch zueinander angeordnet sind und jede Verschlussrotoreinheit jeweils eine Verschlussscheibe, auf der jeweils ein Verschlusskolben angeordnet ist.The interaction of two intermeshing adjacent pistons is analogous to the other embodiments shown. Each work rotor unit may have two separate, connected to each other at the respective cylinder chamber suction channels and two own also offset to each other connected to the cylinder chamber pressure channels. As in Fig. 8 shown, each work rotor unit each has a working disk on which two identical working piston are arranged symmetrically to each other and each shutter rotor unit each have a shutter disc, on each of which a shutter piston is arranged.

Durch eine Erhöhung der Anzahl an Rotoreinheiten lässt sich eine höhere Leistung erzielen. Alternativ kann dies auch durch eine mehrstufige Ausführung der Rotoreinheiten erfolgen wie in Figur 9 vereinfacht dargestellt.By increasing the number of rotor units, a higher performance can be achieved. Alternatively, this can also be done by a multi-stage design of the rotor units as in FIG. 9 shown in simplified form.

Hierzu sind zwei Rotoreinheiten mit Kolben ausgerüstet, die in mehrere Arbeitsebenen angeordnet und miteinander verbunden sind, wobei jede Ebene in verschiedenen Varianten bzw. Modular beliebig aufgebaut werden kann. Grundsätzlich können für den Aufbau mehrstufiger Ausführungen alle bisher beschriebenen einstufigen Ausführungen in etagenartiger Bauweise angewendet werden. Auch in der Funktionsweise bestehen prinzipiell keine Unterschiede.For this purpose, two rotor units are equipped with pistons, which are arranged in several working planes and connected to each other, each level can be arbitrarily constructed in different variants or modular. In principle, all previously described single-stage designs in floor-type design can be used for the construction of multi-stage designs. In principle, there are no differences in the mode of operation either.

Fig. 9 zeigt in vereinfachter schematischer Darstellung zwei Rotoreinheiten 8, 12 mit vier Ebenen bzw. mit vier Stufen. Auf den Rotorwellen sind Arbeits- oder Verschlussschelben mit Arbeits- oder Verschlusskolben befestigt, die in ihrer Ausführung den bereits beschriebenen Bauteilen entsprechen. Durch ineinanderkämmende Arbeits- und Verschlusskolben wird das Fördermedium angesaugt und komprimiert. Der Unterschied zur einstufigen Ausführung besteht lediglich darin, dass in mindestens einer zusätzlichen Ebene das Fürdermedium durch einen Saugkanal angesaugt und vorkomprimiert wird. Das vorkomprimierte Medium wird durch einen Verbindungskanal auf eine benachbarte Ebene übergeben, wobei diese Ebene einen zusätzlichen Saugkanal besitzt. Auf dieser Ebene wird vorverdichtetes Medium endkomprimiert und über eine Druckleitung in einen Druckbehälter übergeben. Jeder Verbindungskanal ist dabei mit einem Kühler ausgerüstet. Fig. 9 shows a simplified schematic representation of two rotor units 8, 12 with four levels or four stages. On the rotor shafts working or Verschlussschelben are fixed with working or closure piston, which correspond in their execution to the components already described. By interlocking working and closing piston, the fluid is sucked and compressed. The difference to the single-stage design consists only in that in at least one additional level, the feeder medium is sucked through a suction channel and precompressed. The precompressed medium is passed through a connection channel to an adjacent level, this level having an additional suction channel. At this level, precompressed medium is finally compressed and transferred via a pressure line into a pressure vessel. Each connection channel is equipped with a cooler.

Bei mehrstufigen Ausführungen sind in jeder Stufe zwei Gehäusebauteile angeordnet, die analog wie bei den zuvor bereits erläutert einstufigen Ausführungen aufgebaut sind.In multi-stage versions two housing components are arranged in each stage, which are constructed analogously as in the previously explained single-stage versions.

Bei allen erfindungsgemäßen Varianten drehen sich die Verschlussrotoreinheiten und die Arbeitsrotoreinheiten In einem Geschwindigkeitsverhältnis zueinander, das von der Anzahl an Arbeitskolben abhängig ist. Bei Ausführungen mit mindestens zwei Rotoreinheiten, wo alle Scheiben mit der gleichen Anzahl an Kolben ausgerüstet sind, beträgt das Geschwindigkeitsverhältnis von Verschlussrotoreinheit zu Arbeitsrotoreinheit 1:1.In all the variants according to the invention, the shutter rotor units and the working rotor units rotate in a speed ratio which depends on the number of working pistons. In versions with at least two rotor units, where all disks are equipped with the same number of pistons, the speed ratio of shutter rotor unit to working rotor unit is 1: 1.

Bei Ausführungen mit ungleicher Anzahl an Kolben zwei benachbarter Rotoreinheiten ist das Geschwindigkeitsverhältnis proportional zum Verhältnis der Anzahl an Kolben der einen Rotoreinheit zur Anzahl an Kolben der anderen Rotoreinheit.In embodiments with unequal numbers of pistons of two adjacent rotor units, the speed ratio is proportional to the ratio of the number of pistons of one rotor unit to the number of pistons of the other rotor unit.

Bei einstufigen Ausführungen mit mehr als zwei Rotoreinheiten können durch Zusammenfügen mehrerer Druckkanäle in einem Druckbehälter die Leistungsparameter erhöht werden.In single-stage designs with more than two rotor units, the performance parameters can be increased by joining several pressure channels in a pressure vessel.

Claims (15)

  1. Rotary piston pump respectively rotary piston compressor with at least two rotor units arranged to be axially parallel to one another and mounted centrically in a housing with suction opening and pressure opening, each consisting of a rotatable shaft with at least one torque-proof disc, whereby at least two adjacent discs in the same plane synchronized rotatable in opposite directions, characterised in that each disc (10, 14, 18, 21, 24, 27) is circular in form and has at least one piston (10a, 14a, 18a, 21a, 24a, 27a), whereby a piston consists of two identical piston sections (10b, 14b, 18b) in the form of ring sections that are arranged mirror-symmetrically to each other, each one on each end face of the disc, in such a manner that these piston sections (10b, 14b, 18b) protrude equally over the outer edge of the respective disc in relation to their radian length and the space between two adjacent rotor units (8, 12, 16, 19, 22, 25) is measured in such a manner that their pistons (10a and 14a; respectively 24a, 24b, 24c and 27a; respectively 10a, 14a and 18a; respectively 10a, 14a, 18a and 21a) in the same plane intermesh during the operating state without making contact within a common overlapping area, and the housing consists of at least two housing components (1,2) with a ring-shaped cylinder chamber (4) to accommodate the piston sections (10b, 14b, 18b) whereby the cylinder chamber 4 is subdivided by an intermediate ring 3 arranged between two adjacent housing components (1, 2), which projects into the intermediate space between two mirror-symmetrically arranged piston sections (10b, 14b, 18b).
  2. Rotary piston pump respectively rotary piston compressor of claim 1, characterized in that it/they are equipped from two identical rotor units (8, 12) each with a disc (10, 14) and a piston (10a, 14a), with the radian measure length of the two pistons (10a, 14a) being 180° for each and acting for one complete rotation of each piston (10a, 14a) in operational condition alternately as the working piston and as the locking piston.
  3. Rotary piston pump respectively rotary piston compressor of claim 1, characterized in that it/they consist of two rotor units (22, 25) each with a disc (24, 27) on one plain, with the pistons (24a, 24b, 24c respectively 27a) differing in outer radius and/or number and piston (27a) with the smaller outer radius acting as the locking piston and the pistons (24a, 24b, 24c) with the larger outer radius as the working piston.
  4. Rotary piston pump respectively rotary piston compressor according to one of the claim 2 or 3, characterized in that the radian measure length of the working piston (10a, 18a, 21a, 24a) is a maximum of 180° and the radian measure length of the locking piston (14a, 27a) at least 180°.
  5. Rotary piston pump respectively rotary piston compressor according to any one of claims 1 to 4, characterized in that it/they are equipped with more than two rotor units (8, 12, 16) each with a disc on one plane (10, 14, 18) with pistons (10a, 14a, 18a), with one piston (14a) that acts as the locking piston always forming at least two joint comb areas respectively with one other piston (10a, 18a), which acts as the working piston.
  6. Rotary piston pump respectively rotary piston compressor of claim 5, characterized in that it/they are equipped with pistons (10a, 14a) of differently sized outer radius and/or with a different number of pistons.
  7. Rotary piston pump respectively rotary piston compressor according to any one of claims 1 to 6, characterized in that it/they are equipped with at least two rotor units (8, 12) wherein each rotor units has at least two discs which are arranged on the respective rotor shaft at an equal distance from each other in such a way that the discs of adjacent rotor units are on one plane, at least one rotor unit has locking pistons and the other rotor units working pistons.
  8. Rotary piston pump respectively rotary piston compressor of claim 7, characterized in that individual discs are equipped with pistons with differently sized outer radius and/or with a different number of pistons.
  9. Rotary piston pump respectively rotary piston compressor according to any one of claims 1 to 8, characterized in that the sum of the circular arc length of two pistons (10a, 14a) that comb together is equal to the circumference of a circle with the outer radius of piston (14a) that acts as the locking piston or to that of a radian measure length of 360°.
  10. Rotary piston pump / respectively rotary piston compressor according to any one of the claims 1 to 9, characterized in that a suction channel (5) is provided in the housing (1, 2) in the overlapping area of two pistons (10a 14a) to suck in pumping medium and a pressure channel (6) is provided opposite this for compressed medium.
  11. Rotary piston pump respectively rotary piston compressor according to any one of claims 1 to 10, characterized in that annular cylinder chamber (4) to receiving the piston sections (10b, 14b, 18b) is formed with at least two overlapping and mirror-symmetrically arranged circular grooves (4a, 4b) arranged in adjacent housing components (1, 2).
  12. Rotary piston pump respectively rotary piston compressor according to any one of claims 1 to 11, characterized that due to the opposite rotation of the pistons (10a und 14a) of two adjacent discs (10, 14) one plane the space volume in the corresponding annular cylinder chamber 4 between two adjacent pistons (10a und 14a) is changeable.
  13. Rotary piston pump respectively rotary piston compressor according to any one of claims 1 to 12, characterized in that in an embodiment having at least two rotor units, with at least two parallel to each other planes which planes are connected by a duct equipped with a cooler channel and in the housing (1, 2) at least two suction channels (5) and a pressure channel (6) are arranged.
  14. Rotary piston pump respectively rotary piston compressor according to any one of claims 1 to 13, characterized that discs (10, 14, 18) are equipped with counterweights (10c, 14c, 18c).
  15. Rotary piston pump respectively rotary piston compressor according to any one of claims 1 to 14, characterized that both side faces of a piston section (10b, 14b, 18b) display a rectangular or square cross sectional area.
EP12000060.9A 2012-01-05 2012-01-05 Rotating piston compressor or rotating piston pump Active EP2613052B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP12000060.9A EP2613052B1 (en) 2012-01-05 2012-01-05 Rotating piston compressor or rotating piston pump

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP12000060.9A EP2613052B1 (en) 2012-01-05 2012-01-05 Rotating piston compressor or rotating piston pump

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EP2613052A1 EP2613052A1 (en) 2013-07-10
EP2613052B1 true EP2613052B1 (en) 2015-09-23

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Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB207065A (en) * 1922-12-29 1923-11-22 Alfred Hugh Tyler Improvements in or relating to rotary pumps, blowers, and the like
DE2061567A1 (en) * 1970-12-15 1972-06-29 Frischwelt Anstalt, Vaduz Rotary compressor
US3941521A (en) * 1974-08-28 1976-03-02 Calspan Corporation Rotary compressor
DE102007038966B4 (en) 2007-08-17 2024-05-02 Busch Produktions Gmbh Multi-stage rotary piston vacuum pump or compressor

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