EP4196679A1 - Machine à piston rotatif radial - Google Patents

Machine à piston rotatif radial

Info

Publication number
EP4196679A1
EP4196679A1 EP21789892.3A EP21789892A EP4196679A1 EP 4196679 A1 EP4196679 A1 EP 4196679A1 EP 21789892 A EP21789892 A EP 21789892A EP 4196679 A1 EP4196679 A1 EP 4196679A1
Authority
EP
European Patent Office
Prior art keywords
rotor
piston
machine
shaft
chamber
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP21789892.3A
Other languages
German (de)
English (en)
Other versions
EP4196679B1 (fr
EP4196679C0 (fr
Inventor
Lubos URBAN
Ján PAVLACKA
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.)
Up Steel SRO
Original Assignee
Up Steel SRO
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Up Steel SRO filed Critical Up Steel SRO
Publication of EP4196679A1 publication Critical patent/EP4196679A1/fr
Application granted granted Critical
Publication of EP4196679B1 publication Critical patent/EP4196679B1/fr
Publication of EP4196679C0 publication Critical patent/EP4196679C0/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/10—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary
    • F04B1/113—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary with actuating or actuated elements at the inner ends of the cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/10—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary
    • F04B1/113—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary with actuating or actuated elements at the inner ends of the cylinders
    • F04B1/1133—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary with actuating or actuated elements at the inner ends of the cylinders with rotary cylinder blocks
    • F04B1/1136—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary with actuating or actuated elements at the inner ends of the cylinders with rotary cylinder blocks with a rotary cylinder with a single piston reciprocating within the cylinder
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/14—Pistons, piston-rods or piston-rod connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/22—Arrangements for enabling ready assembly or disassembly

Definitions

  • the invention relates to a radial rotary piston machine, which can be used as a pump, compressor, vacuum pump or motor.
  • Rotary piston machines are known, particularly pumps or compressors, which comprise a rotor of circular section, in which chambers for pistons are formed, the pistons being mounted on circular cams to produce their linear reciprocating motion, and these cams are mounted on a shaft, which is eccentrically positioned in relation to the rotor.
  • the eccentricity of axis of the shaft from axis of the rotor is equal to the eccentricity of the cam from the axis of the shaft.
  • Document US 1 853 394 discloses a rotary machine or pump, including a casing, a circular chamber within said casing having inlet and, outlet ports at opposite sides thereof.
  • a cylinder rotatably confined within said chamber having an axial opening, a pair of working chambers extending at right angles to each other, diametrically through said cylinder and at opposite sides of said opening thereof.
  • Pistons within said working chambers having circular openings therein, and a revoluble shaft having a pair of diametrically related integral eccentrics. Eccentrics operating within said piston openings. Said shaft being eccentrically mounted with respect to the axis of said circular chamber.
  • the lateral distance between the piston chambers must be approximately the same as the diameter of the piston, to allow the drive shaft to rotate to the proper alignment of its eccentrics with respect to the circular openings of the pistons, after one of the eccentrics has been moved through the circular opening of one of the pistons. Consequently, pumps with the ratio of less than 5 to 1 would be provided with an opening of such dimension that the reciprocating pistons would not continuously cover this opening and thus these pumps would be unusable.
  • Design of the pump in Figures 5 to 10 of the document US 1 910 867 has the ratio of approximately 6 to 1. In order to assemble pumps of this type with the ratio of less than 5 to 1 , the rotor must be split to allow assembly with a smaller central opening.
  • Each cam has such construction that the cam diameter is reduced without varying the eccentricity of the cam by causing a portion of the cam diametrically opposed to the protuberance of the cam to be disposed in a position nearer to the centre of the shaft than its outer circumferential surface, and reliefs for assembling the pistons with the shaft are formed at the outer circumferential surface of the shaft in the vicinity of the portion of the cam diametrically opposed to the protuberance of the cam.
  • Said reliefs of the shaft are important for allowing the reduction in diameter of openings formed in the pistons, into which the cams are inserted to render possible the assembly of the shaft, the pistons and the rotor in described arrangement.
  • Disadvantage of the compressor design according to the document US 4 723 895 resides in tis construction complexity.
  • Document US 2015/0098841 A1 discloses a spin pump with spun- epicyclic geometry, having pistons driven by eccentrics of circular section, as known from the above-mentioned documents.
  • This pump uses a split rotor, however, not in order to provide a longer piston travel, but in order to allow an assembly of the described pump without a need to divide the piston into two pieces.
  • Intake and discharge with the above-described pump designs is provided by rotating a rotor in cylindric hole, where the body of the rotor opens and closes intake and discharge radial openings on cylindrical surface of the cylindric hole in the housing - stator of the pump.
  • timing gear can facilitate the running and load of working parts of the pump, for example substantial lateral load on pistons, it however may be deleterious to the simplicity and efficiency of the machine, as is for example mentioned in the US 2015/0098841 A1.
  • Valve plates may include valves that regulate fluid inflow and fluid outflow routed to respective side ports in bearing plates.
  • at least one valve is coupled to one of the piston bores.
  • one of the valves is an outlet valve on a piston head and another valve is an inlet valve on a piston, whereby inflow may be drawn through the central crankcase portion of the pump and outflow discharged through the head.
  • This embodiment exploits check valves known and used in heads of piston compressors. In the embodiment described, adverse effects derived from a rotation of the valve plate around the axis of rotation of the rotor, i.e.
  • centrifugal/centripetal forces which would increase with the distance of the valve plate from the axis of rotation of the rotor, can add to drawbacks of the known check valves originating particularly from their own design.
  • the rotor does not have to be of cylindric shape.
  • Object of the invention is rotary piston machine that can be used as a pump, compressor, vacuum pump or motor, which is characterized by simplicity in manufacturing, while practically eliminating all disadvantages and limitations resulting from designs in the above-described documents.
  • Such rotary piston machine would allow production particularly of pumps, compressors and vacuum pumps for a wide range of applications and pressure ranges while maintaining the same construction arrangement.
  • a radial rotary piston machine comprising a frame, at least one opening for inlet of a medium into the machine and at least one opening for discharge of a medium out of the machine, where the frame comprises end plates between which a rotor is placed, this rotor comprises axial opening for a shaft of the machine and further comprises at least two angularly offset piston chambers transversely to the rotor axis, the shaft of the machine extends through the axial opening in the rotor and is mounted in bearings in the end plates of the frame, circular cams are arranged on the shaft, the shaft being positioned eccentrically to the rotor, where the eccentricity of the axis of rotation of the shaft from the axis of the rotor is equal to the eccentricity of the axis of the circular cam from the axis of rotation of the shaft, each piston is arranged for reciprocal movement in the piston chamber in the rotor and mounted rotatively on the circular cam on the shaft, where the piston
  • Rotary piston machine is characterized in that the head and/or the rotor comprise at least one passage for inlet and discharge of a medium to and from the piston chamber leading on one end in axial direction to the end plate of the frame, and which is opened and closed at its axial opening by valve means in the form of separate arcuate slots.
  • the piston chamber is provided with an insert, and this insert is connected with the head of the piston chamber.
  • the insert extends along the piston chamber to the proximity of the shaft of a pump, compressor or vacuum pump.
  • the valve means in the form of separate arcuate slots are provided in a valve plate positioned between the rotor end and the end plate of the frame.
  • the rotor end is provided by a slide sealing plate with an aperture for passage of a medium to and from the passage in the head and/or rotor.
  • the piston is provided at each of its ends by a piston ring.
  • the piston ring is jointless, where the piston end is provided removable for insertion of this jointless piston ring.
  • FIG. 1 shows axonometric section view of radial rotary piston machine, specifically a compressor
  • FIG. 2 shows axonometric expanded view of the machine of Fig. 1 ;
  • FIG. 3 shows axonometric expanded view of the valve means of the machine
  • Fig. 4 shows axonometric view of the piston of the machine
  • Fig. 5 shows axonometric view of the rotor of the machine without the slide sealing palate at one end of the rotor.
  • FIG. 6 shows axonometric expanded view of the rotor of the machine with the slide sealing plates at both ends of the rotor and the valve plates;
  • FIG. 7 schematically shows working phase of the machine with the inlet and discharge of a medium closed
  • FIG. 8 schematically shows working phase of the machine with the intake and discharge of a medium opened
  • Fig. 9 shows overall outside view of the radial rotary piston machine of Fig. 1 , in a frame in the form of closed casing with openings for inlet and discharge of the air, and with protruding shaft of the machine.
  • FIG. 10 shows axonometric section view of a variant of the radial rotary piston machine having pistons without piston rings, in the piston chamber without the insert, without the slide sealing plates at the ends of the rotor, and with the passage for inlet and discharge of a medium to or from the piston chamber, provided in the rotor;
  • Fig. 11 shows axonometric expanded view of the machine of Fig. 10.
  • a machine shown in Fig. 1 to 6 is specifically a compressor, and a rotary machine shown in Fig. 10 and 11 can be a pump, or also a small size compressor.
  • the machine according to the examples shown is provided with two pistons 4, each reciprocally movable in one chamber 22 of a rotor 2, where chambers 22 are mutually arranged under 90° angle.
  • the machine, compressor according to Fig. 1 to 6, comprise a frame 1 , in the shown example, in the form of two-piece casing.
  • a rotor 2 is rotatively mounted in bearings 12 in end plates 11 of the frame 1.
  • Axial opening 21 for a shaft 5 of the machine and chambers 22 for pistons 4 are provided in the rotor 2.
  • the shaft 5 extends through axial opening 21 of the rotor 2 and is rotatably mounted in bearings 15 in the end plates 11 of the frame 1.
  • the shaft 5 protrudes through the end plate 11 of the frame 1 on one side, where it is sealed for example by a common shaft seal.
  • Circular cams 51 are arranged on the shaft 5.
  • the shaft 5 is positioned eccentrically to the rotor 2, where the eccentricity of the axis of rotation of the shaft 5 from the axis of rotation of the rotor 2 is equal to the eccentricity of the axis of the circular cam 51 from the axis of rotation of the shaft 5.
  • Circular cams 51 are mounted on the shaft 5 through detachable keyed joint. This is preferable with regard to the production and also to assembling of the machine. However, it is equally possible to provide the shaft 5 with integral cams 51 as commonly known in the prior art.
  • a piston 4 is rotatively mounted on the circular cam 51.
  • the piston 4 has opening 41 to be mounted on the circular cam 51. This opening 41 passes transversely through the centre of the piston 4.
  • the piston 4 has two ends, where the piston 4 is equipped with a piston ring 43 on each of the two ends.
  • the piston ring 43 is placed in a groove 42 provided in the piston 4.
  • the piston ring 43 with a joint or jointless can both be equally used. When jointless piston ring 43 is used, relative end of the piston 4 is made removable in order to make the groove 42 accessible for insertion of such jointless piston ring 43.
  • the piston 4 is provided with one piston ring 43 on each of its ends.
  • One piston ring 43 on each end of the piston 4 is sufficient, however, greater number of piston rings 43 can be chosen if required, be it necessary regarding dimensions, or material of the piston rings 43, or applications, which the machine according to the invention will be used for.
  • the piston ring 43 provides tightness of the piston 4 in the piston chamber 22 in the rotor 2, or tightness of the piston 4 in an insert 31 of the piston chamber 22. It was surprisingly found that the piston ring 43 also provides for smooth running of the machine without a need to follow extremely tight tolerances in mutual positions of related rotating and moving parts, that is, the rotor 2, the shaft 5, circular cams 51 , and pistons 4, as required in machines according to the prior art. Such required tight tolerances can be followed without any considerable problems in machines having small dimensions, however, it is problematic to follow such tight tolerances in larger machines, while these require special and costly manufacturing.
  • the piston chamber 22 in the rotor 2 is closed by a head 3.
  • the head 3 is arranged on the rotor 2 detachably, and is provided on each end of the chamber 22.
  • the head 3 is provided with the insert 33 of the piston chamber 22.
  • the insert 31 creates the inner space of the chamber 22, in which the piston 4 is moving, and therefore, tight sliding placement of the piston 4 is formed by inner wall of the insert 31 and the piston ring 43.
  • the insert can be provided such that it extends to the closest possible proximity of the shaft 5, of course not disregarding a displacement of axes of rotation of the shaft 5 and the rotor 2.
  • the insert 31 is preferable regarding its simple replacement when worn- out, thus it is not necessary to replace, or optionally re-bore, the whole rotor 2, when directly chambers 22 are worn-out in case the pistons 4 move directly in the chambers 22 without the inserts 31. Further, the insert 31 allows that an interconnection of the chambers 22 through the axial opening 21 in the rotor 2 cannot occur in case of greater dimensions of the machine and longer travels of the piston 4, when the piston 4 edge could pass under the outline of the axial opening 21 , thus creating undesired leak of a medium from the piston chamber 22 to this axial opening 21. Then, this allows to produce the machine without for example a requirement for split rotor 2 in order to achieve the least possible diameter of axial opening 21 of the rotor 2.
  • At least one passage 32 is provided in the head 3 for inlet and discharge of a medium to and from the piston chamber 22, in this example, the chamber 22 with the insert 31.
  • this passage 32 can be provided also in the head 3 only, or partially in the head 3 and partially in the body of the rotor 2, or in the body of the rotor 2 only, as will be described later in the example of embodiment according to Fig. 10 and 11.
  • the passage 32 provided in the body of the rotor 2 only can somehow decrease volumetric efficiency of the compressor, however in the case of pumps, or blowers this is negligible.
  • the passage 32 for inlet and discharge of a medium to and from the piston chamber 22 is axially opening in direction to the end plate 11 of the frame 1 , that is axially in regard to the rotor 2 and the shaft 5.
  • These valve means are provided in the form of separate arcuate slots 61 opening the passage 32 for inlet and discharge of a medium to and from the chamber 22. Closing of the passage 32 is carried by a solid part, the part between the separate arcuate slots 61 , of the body in which the separate arcuate slots 61 are provided.
  • the arcuate slots 61 are preferably arranged in a valve plate 6, positioned between the rotor 2 and the bearing plate 11 of the frame 1.
  • the valve plate 6 is preferably lodged in a groove 16 in the end plate 11 of the frame 1.
  • the groove 16 is not essential for placing the valve plate 6.
  • the valve plate 6 must be for proper functioning secured against its own turning only.
  • the position of the valve plate 6 is secured against turning by at least one locking pin 63 interfering the plate 6 and the end plate 11. In order to secure position of the plate 6 it is of course possible to use also other known suitable means.
  • Valve plate 6 of the type described is used in hydraulic axial piston pumps, however its application in radial rotary piston machines is not disclosed elsewhere, and in fact excluded in compressors known in the prior art.
  • a sealing plate 7 is attached to the end of the rotor 2, in order to provide reliable sealing of the head 3 and/or the rotor 2 against the valve plate 6, with regard to the passage 32 for inlet and discharge of a medium.
  • the sealing plate 7 comprises an aperture 71 , in fact apertures 71 , for passage of a medium to and from the passage 32 for inlet and discharge of a medium to and from the piston chamber 22.
  • a sealing 322 can be provided around axial opening of the passage 32 to prevent accidental leaks of pressure air between the sealing plate 7 and the head 3 and/or the rotor 2. It is equally preferable when similar sealing 64 is provided around the arcuate slot 61 on the valve plate 6 against the end plate 11.
  • valve means is the same also for the other end of the rotor 2.
  • the passage 32 i.e. passages 32, for inlet and discharge of a medium to or from the piston chamber 22, in the embodiment shown with the sealing plate 7 the apertures 71 for inlet and discharge of a medium are opened or closed respectively against the arcuate slots 61 of the valve plate 6. Then, the arcuate slots 61 respectively communicate with an opening 13 for inlet of a medium to the machine and an opening 14 for discharge a medium form the machine, which are arranged on the frame 1 of the machine.
  • the opening 13 for inlet of a medium to the machine is formed after connecting a two-pieces casing, which produces closed enclosure for the compressor.
  • the opening 13 connects inner space of the casing with a source of a medium, in this case the ambient air.
  • the opening 14, i.e. openings 14, for discharge of a medium from the machine are provided in the end plates 11 of the casing, while in this case they are led out form the groove 16 wherein the valve plate 6 is lodged.
  • valve means a variant of embodiment is possible for example without the valve plate 6, where the arcuate slots 61 would be provided directly in the end plates 11 of the frame 1.
  • a variant of embodiment is possible without the slide sealing plate 7 at the end of the rotor 2, where a slide surface would be directly end surface of the rotor 2, whereon the passage 32 for inlet and discharge of a medium to and from the piston chamber 22 would be provided.
  • Such variant will be for a better understanding described in the next example of embodiment, which is shown in Fig. 10 and 11.
  • the valve plate 6 and the slide sealing plate 7 preferably provide sealing means that can be easily replaced when worn- out.
  • roller bearings In the example of embodiment of the machine shown, all rotative mounts are provided with roller bearings. Plain bearings can equally be used, or combinations of roller and plain bearings if required.
  • the shaft 5 connected to a drive rotates the circular cams 51 , which drive the pistons 4 in reciprocating motion in their chambers 22 with the inserts 31.
  • the pistons 4 at the same time rotate the rotor 2. Due to presence of the piston rings 43 the compressor runs completely smoothly and evenly also with standard tolerances in positions and alignment of related rotative parts.
  • Fig. 7 and 8 show positions of rotative parts when turning the shaft 5 for 180°, where for a simpler illustration one extreme position of one of the pistons 4 is chosen as starting position, i.e. the position at the end of the piston 4 travel in the chamber 22. This starting position is shown in Fig. 7.
  • the cam 51 is in extreme position of its highest eccentricity, thus the piston 4 is in the extreme position at the end of its travel.
  • One end of the piston 4 is thus in the position closest to the head 3.
  • the other end of the piston 4 is then in the farthermost position from the head 3.
  • Body of the valve plate 6 closes in this position the passages 32 for inlet and discharge of a medium to and from the piston chamber 22.
  • the sealing plate 7 is present, the apertures 71 for passage of a medium are closed.
  • the air is on one side in fact completely pushed out from the chamber 22 and on the other side, drawn in into the highest working volume of the chamber 22.
  • the aperture on one side passes by the edge of the arcuate slot 61 while connecting the chamber 22 with the air inlet.
  • the air inlet is provided by the opening 13 in the compressor casing, which supplies the air into the inner space of the casing.
  • the air is guided from the inner space of the casing by inlet grooves 62 into the arcuate slot 61 in the valve plate 6.
  • the aperture 71 passes the edge of the other arcuate slot 61 while connecting the chamber 22 with the air discharge.
  • the air discharge is provided by the opening 14 in the end plate 11 of the casing, where this opening leads to a channel 17 in the end plate 11 on the side of the valve plate 6.
  • the arcuate slots 61 in the valve plate 6 shown in drawings are segmented, i.e. it is not continuous arcuate slot 61. The reason is to maintain strength of the valve plate 6, while material of the plate 6 between segments of the arcuate slot 61 does not affect the passage of a medium to and from the piston chamber 22 in any way. Anywhere the construction allows it, the slots 61 can be provided as continuous. Separation of the arcuate slots 61 regarding the separation of inlet and discharge parts for a medium must of course be maintained.
  • valve plate 6 and slide sealing plate 7 will not be used and the valve means will be provided directly in the frame 1 of the machine, in fact in the end plates 11.
  • the most preferable is to create the frame 1 in the form of the casing as shown in overall outside view in Fig. 9. This way, compact machine is produced, where such casing protects rotating parts of the machine and also contributes to lowering the machine noise.
  • the rotor 2 is able to cool itself by own rotation in the surrounding drawn in medium, the air, such that no additional cooling equipment, such as a fan, is necessary.
  • this compressor is capable of uninterrupted operation, Cooling efficiency can further be increased also by injecting of a small amount of oil into the air drawn in.
  • Outer dimensions of the compressor casing, shown in Fig. 9 are 140 x 140 x 180 mm. Compressor displacement is 90 cm 3 per 1 revolution of the shaft 5. The compressor was driven by electric motor with 1 ,5 kW output. Noise, compressor output in l/min., and input were measured. Particular values measured at 800 rev./min. were:
  • the framel can also be for example provided such that it will not form compact casing, but will form a frame structure providing necessary mutual position and rigidity of the end plates 11.
  • the opening 13 for inlet of a medium to the machine will be then appropriately provided on a body of the end plate 11.
  • FIG. 10 and 11 show a variant of radial rotary piston machine according to the invention, that is complete rotor part of the machine with the shaft 5, with the pistons 4 without the rings 43, with piston chambers 22 without the insert 31 , without the slide sealing plates at the end of the rotor 2, and with the passage for inlet and discharge of a medium to and from the chamber 22 in the rotor 2 only.
  • the machine with such rotor part can be for example a pump, or a compressor having small dimensions, where tight tolerances can be followed due to the tightness and alignment of rotative parts of the machine. Pumps having larger dimensions looser tolerances are possible, as such tolerances are balanced by the working fluid.
  • Valve means i.e.
  • the frame of the machine can be provided as the casing, or also in the form of the frame structure, providing necessary mutual position and rigidity of the end plates 11 as described above.
  • Radial rotary piston machine can be a compressor, pump, vacuum pump, or optionally also a motor.
  • valve means described Due to valve means described also reverse running of the machine is possible without any additional arrangements, when in fact, only the function of the opening 13 for inlet of a medium to the machine is turned to the function of the opening 14 for discharge of a medium and vice versa.
  • Design of the radial rotary piston machine according to the invention also allows for producing a compressor as multi-stage compressor, for example to obtain higher pressures.
  • the chambers 22 and the pistons 4 have the same dimensions, i.e. working volume of each chamber 22 is equally large.
  • Embodiments of the machine comprising more chambers 22 with pistons 4, or with different mutual angle as in the examples already described are not excluded. However, in such cases, this will concern design solutions of piston chambers 22 only and their arrangement in the rotor 2, while the essence of the solution will remain with all its advantages.
  • Radial rotary piston machine according to the invention can be manufactured with technologies commonly available and used and with conventional materials. [0091] Individual parts of the machine can also be produced using 3D printing without any problems. Use of special materials is anticipated only in special applications as for example oil-free compressors, pumps or compressors for extreme loads and similar.
  • Radial rotary piston machine according to the invention can be used as a compressor, pump, vacuum pump, or also a motor.
  • Radial rotary piston machine as a compressor can be used for a wide range of applications in a wide range of pressures and flow rates, as for example, blowers, low-pressure, middle-pressure or high-pressure compressors.
  • Radial rotary piston machine as a vacuum pump can be used as efficient vacuum pump to create negative pressure, as well as multi-stage vacuum pump to reach high vacuum.
  • the vacuum pump is simply provided only by connecting the intake to a volume where a negative pressure is required without a demand for any further design adjustments.

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

Abstract

L'invention concerne une machine à piston rotatif radial comprenant un châssis (1), au moins une ouverture (13) pour l'admission d'un fluide dans la machine et au moins une ouverture (14) pour le refoulement d'un fluide hors de la machine, le châssis (1) comprenant des plaques d'extrémité (11) entre lesquelles est placé un rotor (2), ce rotor (2) comprenant une ouverture axiale (21) pour un arbre (5) de la machine et comprenant aussi au moins deux chambres de piston décalées angulairement (22) transversalement par rapport à l'axe du rotor, l'arbre (5) de la machine s'étendant à travers l'ouverture axiale (21) dans le rotor (2) et étant monté dans des paliers dans les plaques d'extrémité (11) du châssis (1), des cames circulaires (51) étant agencées sur l'arbre (5), l'arbre (5) étant positionné de manière excentrée par rapport au rotor (2), chaque piston (4) étant agencé pour un mouvement de va-et-vient dans la chambre (22) et monté en rotation sur la came circulaire (51), les extrémités de la chambre (22) étant fermées par des têtes (3), la tête (3) ou le rotor (2) comprenant au moins un passage (32) pour l'admission et le refoulement d'un fluide à partir de la chambre (22), qui est ouvert et fermé par des moyens soupapes, la tête (3) et/ou le rotor (2) comprenant au moins un passage (32) pour l'admission et le refoulement d'un fluide vers et depuis la chambre de piston (22) menant d'une extrémité dans la direction axiale à la plaque d'extrémité (11) du châssis (1), et qui est ouvert et fermé au niveau de son ouverture axiale par des moyens soupapes sous la forme de fentes arquées séparées (61).
EP21789892.3A 2020-08-13 2021-08-13 Machine à piston rotatif radial Active EP4196679B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SK932020A SK288973B6 (sk) 2020-08-13 2020-08-13 Radiálny piestový rotačný stroj
PCT/SK2021/050010 WO2022035383A1 (fr) 2020-08-13 2021-08-13 Machine à piston rotatif radial

Publications (3)

Publication Number Publication Date
EP4196679A1 true EP4196679A1 (fr) 2023-06-21
EP4196679B1 EP4196679B1 (fr) 2025-04-09
EP4196679C0 EP4196679C0 (fr) 2025-04-09

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EP21789892.3A Active EP4196679B1 (fr) 2020-08-13 2021-08-13 Machine à piston rotatif radial

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US (1) US20230296088A1 (fr)
EP (1) EP4196679B1 (fr)
HU (1) HUE071789T2 (fr)
PL (1) PL4196679T3 (fr)
SK (1) SK288973B6 (fr)
WO (1) WO2022035383A1 (fr)

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EE01644U1 (et) * 2024-01-26 2024-09-16 Scandic Technologies OÜ Pöördkolbpump

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WO2022035383A1 (fr) 2022-02-17
SK288973B6 (sk) 2022-06-30
EP4196679B1 (fr) 2025-04-09
US20230296088A1 (en) 2023-09-21
PL4196679T3 (pl) 2025-08-04
EP4196679C0 (fr) 2025-04-09
HUE071789T2 (hu) 2025-09-28
SK932020A3 (sk) 2021-08-25

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