EP2613052B1 - Compresseur à pistons rotatifs ou pompe à pistons rotatifs - Google Patents

Compresseur à pistons rotatifs ou pompe à pistons rotatifs 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.)
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Application number
EP12000060.9A
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German (de)
English (en)
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EP2613052A1 (fr
Inventor
Oleksandr Bezeliuk
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Noble Products International GmbH
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Noble Products International GmbH
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Publication of EP2613052A1 publication Critical patent/EP2613052A1/fr
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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)

Claims (15)

  1. Pompe à piston rotatif, respectivement compresseur à piston rotatif comprenant au moins deux ensembles rotoriques disposés centralement parallèlement à leur axe dans un boîtier avec orifice d'aspiration et orifice de refoulement, comprenant chacun un arbre rotatif doté d'au moins un disque immobilisé en rotation, sachant qu'au moins deux disques adjacents situés sur le même plan tournent en sens inverse de manière synchronisée, caractérisé(e) par le fait que chaque disque (10, 14, 18, 21, 24, 27) est de forme circulaire et possède au moins un piston (10a, 14a, 18a, 21a, 24a, 27a), un piston étant constitué de deux sections identiques (10b, 14b, 18b) en forme de sections annulaires disposées symétriquement l'une par rapport à l'autre à chaque extrémité du disque, de manière à ce que ces sections de piston ((10b, 14b, 18b) dépassent autant en termes de longueur de l'arc le bord extérieur du disque correspondant, et à ce que l'écart entre ensembles rotoriques adjacents (8, 12, 16, 19, 22, 25) soit tel que les pistons (10a et 14a ; respectivement 24a, 24b, 24c et 27a ; respectivement 10a, 14a et 18a ; respectivement 10a, 14a, 18a et 21 a) situés sur le même plan s'engrènent lors de leur fonctionnement dans une zone commune de chevauchement sans entrer en contact, et que le boîtier consiste en deux composants (1,2) minimum, situés à l'intérieur d'une chambre à vérins de forme annulaire (4) destinée à recevoir les sections de piston (10b, 14b, 18b), la chambre à vérins 4 étant subdivisée par un anneau intermédiaire (3) dépassant entre les deux composants (1, 2) adjacents du boîtier jusque dans l'espace intermédiaire situé entre les deux sections de piston disposées de manière symétrique (10b, 14b, 18b).
  2. Pompe à piston rotatif, respectivement compresseur à piston rotatif conformément à la revendication 1, caractérisé(e) par le fait qu'elle/il est équipé(e) de deux ensembles rotoriques identiques (8, 12) avec un disque (10, 14) et un piston (10a, 14a) chacun, la longueur de l'arc des deux pistons (10a, 14a) étant de 180° chacun, et au cours d'une rotation complète, chaque piston (10a, 14a) faisant alternativement office de piston de travail et de piston de blocage.
  3. Pompe à piston rotatif, respectivement compresseur à piston rotatif conformément à la revendication 1, caractérisé(e) par le fait qu'elle/il est composé(e) de deux ensembles rotoriques (22, 25) dotés respectivement d'un disque (24, 27) tous deux situés sur le même plan, les pistons (24a, 24b, 24c respectivement 27a) se distinguant en termes de rayon extérieur ou de nombre, et le piston (27a) ayant le rayon extérieur le plus faible faisant office de piston de blocage et le/les pistons (24a, 24b, 24c) ayant le rayon extérieur plus grand que le piston de travail.
  4. Pompe à piston rotatif, respectivement compresseur à piston rotatif conformément à la revendication 2 ou 3, caractérisé(e) par le fait que la longueur de l'arc du piston de travail (10a, 18a, 21 a, 24a) fait au maximum 180° et la longueur de la mesure de l'arc du piston de blocage (14a, 27a) au minimum 180°.
  5. Pompe à piston rotatif, respectivement compresseur à piston rotatif conformément à l'une des revendications de 1 à 4, caractérisé(e) par le fait qu'elle/il est équipé(e) de plus de deux ensembles rotoriques (8, 12, 16) dotés respectivement de disques situés sur le même plan (10, 14, 18) avec pistons (10a, 14a, 18a), un piston (14a) faisant office de piston de blocage et formant au moins deux zones d'engrènement communes, soit chacun une avec un autre piston (10a, 18a) faisant office de piston de travail.
  6. Pompe à piston rotatif, respectivement compresseur à piston rotatif conformément à la revendication 5, caractérisé(e) par le fait qu'elle/il est équipé(e) de pistons de rayons extérieurs différents (10a, 14a) et/ou d'un nombre différent de pistons.
  7. Pompe à piston rotatif, respectivement compresseur à piston rotatif conformément à l'une des revendications de 1 à 6, caractérisé(e) par le fait qu'elle/il est équipé(e) d'au moins deux ensembles rotoriques (8, 12), chaque rotor étant doté d'au moins deux disques disposés sur l'axe du rotor respectif à égale distance l'un de l'autre, de manière à ce que les disques des ensembles rotoriques adjacents se situent sur le même plan, qu'au moins l'un des ensembles rotoriques possède des pistons de blocage et les autres ensembles rotoriques des pistons de travail.
  8. Pompe à piston rotatif, respectivement compresseur à piston rotatif conformément à la revendication 7, caractérisé(e) par le fait que certains disques sont équipés de pistons de rayons extérieurs différents et/ou d'un nombre différent de pistons.
  9. Pompe à piston rotatif, respectivement compresseur à piston rotatif conformément à l'une des revendications de 1 à 8, caractérisé(e) par le fait que la somme des longueurs de l'arc de deux pistons (10a, 14a) qui s'engrènent correspond à la circonférence d'un cercle possédant le rayon extérieur du piston (14a) faisant office de piston de blocage ou à celle d'un arc d'une longueur de 360°.
  10. Pompe à piston rotatif, respectivement compresseur à piston rotatif conformément à l'une des revendications de 1 à 9, caractérisé(e) par le fait que, dans le boîtier (1, 2) sont prévus dans la zone de chevauchement de deux pistons (10a 14a), un canal d'aspiration du liquide refoulé et, à l'opposé de celui-ci, un canal de refoulement (6) pour le liquide comprimé.
  11. Pompe à piston rotatif, respectivement compresseur à piston rotatif conformément à l'une des revendications de 1 à 10, caractérisé(e) par le fait que la chambre à vérins annulaire (4) destinée à recevoir les sections des pistons (10b, 14b, 18b), est formée au minimum de deux rainures circulaires (4a, 4b) qui se chevauchent et sont disposées de manière inversement symétrique dans des composants de boîtiers adjacents (1, 2).
  12. Pompe à piston rotatif, respectivement compresseur à piston rotatif conformément à l'une des revendications de 1 à 11, caractérisé(e) par le fait que suite à la rotation en sens contraire des deux pistons (10a et 14a) de deux disques adjacents (10, 14) situés sur un même plan, le volume d'espace à l'intérieur de la chambre à vérins circulaire correspondante (4) entre les deux pistons adjacents (10a et 14a) est modifiable.
  13. Pompe à piston rotatif, respectivement compresseur à piston rotatif conformément à l'une des revendications de 1 à 12, caractérisé(e) par le fait que dans un modèle doté d'au moins deux ensembles rotoriques, avec deux plans parallèles, les plans sont connectés par un canal équipé d'un refroidisseur et que dans le boîtier (1, 2) sont disposés au moins deux canaux d'aspiration (5) et un canal de refoulement (6).
  14. Pompe à piston rotatif, respectivement compresseur à piston rotatif conformément à l'une des revendications de 1 à 13, caractérisé(e) par le fait que les disques (10, 14, 18) sont équipés de contrepoids (10c, 14c, 18c).
  15. Pompe à piston rotatif, respectivement compresseur à piston rotatif conformément à l'une des revendications de 1 à 14, caractérisé(e) par le fait que les deux surfaces latérales d'une section de piston (10b, 14b, 18b) présentent une section rectangulaire ou carrée.
EP12000060.9A 2012-01-05 2012-01-05 Compresseur à pistons rotatifs ou pompe à pistons rotatifs Active EP2613052B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP12000060.9A EP2613052B1 (fr) 2012-01-05 2012-01-05 Compresseur à pistons rotatifs ou pompe à pistons rotatifs

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP12000060.9A EP2613052B1 (fr) 2012-01-05 2012-01-05 Compresseur à pistons rotatifs ou pompe à pistons rotatifs

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EP2613052A1 EP2613052A1 (fr) 2013-07-10
EP2613052B1 true EP2613052B1 (fr) 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 (de) * 1970-12-15 1972-06-29 Frischwelt Anstalt, Vaduz Rotationskompressor
US3941521A (en) * 1974-08-28 1976-03-02 Calspan Corporation Rotary compressor
DE102007038966B4 (de) 2007-08-17 2024-05-02 Busch Produktions Gmbh Mehrstufige Drehkolbenvakuumpumpe bzw. - verdichter

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