SK932020A3 - Radial piston rotary machine - Google Patents

Abstract

Radial piston rotary machine can be used as a compressor, pump and vacuum pump or even as a motor. It comprises a fixed frame (1), at least one opening (13) for the entry of the medium into the machine and at least one opening (14) for the exit of the medium from the machine. The frame (1) comprises fronts (11), between which a rotor (2) with an axial bore (21) for the machine shaft (5) is mounted in rotary bearings and further comprises at least two chambers (22) for pistons (4), transversely to shaft (5) axis oriented and angularly displaced. The shaft (5) of the machine passes through an axial hole (21) in the rotor (2) and is mounted in rotary bearings in the fronts (11) of the frame (1). The shaft (5) is mounted eccentrically with respect to the rotor (2) and circular cams (51) are arranged on it. Each piston (4) is rotatably mounted on a circular cam (51) and slidably reciprocatingly in a chamber (22). Heads (3) enclose the ends of the chamber (22). The head (3) and / or the rotor (2) comprise at least one passage (32) for the supply and outlet of medium to and from the chamber (22) for the piston (4), which at one end opens in the axial direction to the front (11) of the frame (1) and which is opened and closed at the axial outlet by valve means in the form of separate arcuate openings (61).

Description

SK 93-2020 A3

Technical field

The invention relates to a radial piston rotary machine which can be used as a pump, compressor, vacuum pump or motor.

Prior art

Piston rotary machines are known, in particular pumps or compressors, which comprise a rotor of circular cross-section in which piston chambers are formed, the pistons being mounted on circular cams for rectilinear reciprocating motion, and these cams being formed on a shaft which is mounted eccentrically to rotor. The eccentricity of the shaft axis from the rotor axis is equal to the cam eccentricity from the shaft axis.

Reciprocating rotary machines of this type are described, for example, in U.S. Pat. No. 1,853,394, U.S. Pat. No. 1,910,876 and U.S. Pat. No. 4,423,895.

U.S. Pat. No. 1,853,394 discloses a rotary machine or pump comprising a housing, with a circular chamber in the housing, where the inlet and the outlet are on opposite sides of the housing. In the chamber there is a rotatably mounted cylinder, which comprises an axial opening, a pair of mutually perpendicular working chambers extending transversely in the direction of the diameter of this cylinder and on opposite sides of the axial opening of the cylinder. The pistons in the working chambers have circular holes through which the shaft passes with a pair of opposite eccentrics formed in one piece with the shaft. The eccentrics move in the bores of the pistons. The shaft is mounted eccentrically with respect to the axis of the circular chamber. The respective diameters of the eccentrics, the holes in the pistons and the axial hole in the cylinder are substantially the same, and the diameters of the rotary cylinder and the eccentrics are limited to the sizes at which the axial cylinder bore is covered by each of the reciprocating pistons during their entire working cycle. The aim of the solution according to this document is to provide an extremely efficient rotary machine for extruding, transferring, or compressing fluids or gases.

Subsequent document US 1 910 867, of the same applicant, which refers to said document US 1 853 394, then discusses the properties of the described rotary pump in more detail.

In the case of the pumps described in the said documents, it is essential that the central, axial bore in the cylinder be continuously covered by the pistons and that it never be exposed and thus no working medium can flow from one cylinder chamber to another. This condition makes it impossible to design a single-cylinder pump with a ratio of pump rotor diameter to piston stroke of less than 5 to 1. This is because the rotor assembly with pistons can only be achieved by axially moving the drive shaft through the central rotor bore and piston holes in the pistons. . In order for such a folding process to be possible, the central hole must have such a cross section that the eccentric drive shaft can easily rotate therein. In addition, the lateral distance between the piston chambers must be approximately equal to the diameter of the piston to allow the drive shaft to rotate to properly align its eccentrics with respect to the circular piston bores after one of the eccentrics has been moved through the circular bore of one of the pistons. Consequently, pumps with a ratio of less than 5 to 1 will be provided with an opening of such a size that the reciprocating pistons will not continuously reside through this opening and these pumps will thus be unusable. The pump design of Figures 5 to 10 of U.S. Pat. No. 1,910,867 has a ratio of approximately 6 to 1. In order to assemble pumps of this type with a ratio of less than 5 to 1, the rotor must be divided to allow assembly with a smaller central bore.

However, the split rotor must have the same characteristics as a single rotor, and thus the connection of the individual parts of the split rotor must be made very precisely with minimal deviations and also sufficiently strong. Such a design increases the production complexity and thus also the production costs.

U.S. Pat. No. 7,423,895 describes a method and apparatus for providing volume control of a compressor on a compressible gas compressor, such as a refrigerant for a refrigeration cycle. This document describes a compressor with the principle on which the devices according to U.S. Pat. No. 1,853,394 and U.S. Pat. No. 1,910,876 operate. The respective rotating parts of the compressor are mounted on roller bearings in this solution. Each cam on the compressor shaft is constructed such that the cam diameter is reduced without changing the cam eccentricity by placing a portion of the cam of the opposite cam protrusion closer to the center of the shaft than its outer circular surface and on the outer circular surface of the shaft at The cams of the opposite cam projection are provided with reliefs for assembling the pistons with the shaft.

Said shaft reliefs are important in order to be able to reduce the diameter of the holes formed in the pistons into which the cam is inserted and to be able to assemble the shaft, the pistons and the rotor in the described arrangement. A disadvantage of the construction of the compressor according to US 7,423,895 is its design complexity.

US 2015/0098841 A1 describes a rotary epicyclic pump, with pistons mounted on circular cams, as is known from said documents. This pump uses a split rotor, but not in order to achieve a higher piston stroke, but in order to allow the described pump to be assembled without the need to divide one piston into two parts.

Suction and discharge is ensured in the mentioned pump constructions by rotating the rotor in the cylinder

SK 93-2020 A3 holes, where the rotor body opens and closes the inlet and outlet radial holes, in the cylindrical surface of the cylindrical hole in the housing - stator of the pump.

For the correct operation of the pump, both to ensure tightness between the suction and discharge part and due to the smooth rotation of the rotor and the drive shaft with circular cams, it is necessary to produce a very precise rotor mounting in a cylindrical recess for the rotor in the pump housing. This condition is extremely important especially if these machines are intended for operation without lubricant, ie as a so-called oil-free. Ensuring the required accuracy increases production demands. Failure to observe strict tolerances can already cause leaks and irregularities in the operation of the machine, ie "jamming" in positions that do not show the necessary accuracy. To some extent, such a drawback can be overcome by providing a 2: 1 ratio between the shaft and the pump rotor. Although such a distribution may facilitate the operation and loading of the working parts of the pump, for example a substantial lateral load on the pistons, it is a negative with regard to the simplicity of machine efficiency, such as in US 2015/0098841 A1.

US 2015/0098841 A1 also describes a possible embodiment of a pump where the ends of a bore for a piston in a rotor are connected to heads. The valve plates may include valves that control the inlet and outlet of the medium supplied to the respective side ports in the faces. Thus, at least one valve is connected to one of the bores for the piston. In one embodiment, one of the valves is an outlet valve on the piston head and the other valve is an inlet valve on the piston, wherein the medium can enter through the central portion of the pump crankcase and exit through the head. This arrangement uses known check valves used in reciprocating compressor heads. To the disadvantages of these non-return valves, which consist in particular in their construction, in the case of the described embodiment, negative effects from the rotation of the valve plate about the rotor axis can be added, i.e. negative effects of centrifugal / centrifugal forces increasing . The rotor in this case does not have to have a cylindrical shape.

It is an object of the present invention to provide a reciprocating rotary machine which can be used as a pump, compressor, vacuum pump or motor, which is characterized by simple production, while practically eliminating all the disadvantages and limitations resulting from the designs described in the documents described. Such a reciprocating rotary machine would allow the production of pumps, compressors and pumps in particular for a wide range of applications and pressure ranges while maintaining the same design. At the same time, it is also desirable that such a design of a particular compressor or pump be able to work without lubricant, or in the so-called. oil-free operation.

The essence of the invention

This object is achieved by a radial piston rotary machine according to the invention comprising a fixed frame, at least one opening for the entry of medium into the machine and at least one opening for the exit of medium from the machine, the frame comprising faces between which a rotor is mounted in rotary bearings axial bore for the machine shaft and further comprising at least two axially displaced piston chambers transversely to its axis, the machine shaft passes through an axial bore in the rotor and is mounted in rotatable bearings in the frame faces, the cam cams are arranged eccentrically on the shaft, the shaft is mounted eccentrically relative to the rotors, the eccentricity of the axis of rotation of the shaft from the axis of the rotor being equal to the eccentricity of the axis of the camshaft from the axis of rotation of the shaft, each piston slidably mounted in a piston chamber in the rotor and rotatable on a circular cam on the shaft , the head or rotor comprises at least one passage for the inlet and outlet of the medium from the piston chamber, which are opened and closed by valve means. The essence of the reciprocating rotary machine according to the invention is that the head and / or the rotor comprise at least one passage for the inlet and outlet of the medium to and from the piston chamber at one end leading in the axial direction to the frame face, which is opened and closed at the axial outlet by valves. means in the form of separate arcuate openings.

It is advantageous if the piston chamber is provided with an insert, and this insert is connected to the chamber head.

It is advantageous if the insert passes through the piston chamber close to the shaft of the pump, compressor or pump.

It is advantageous if the valve means in the form of separate arcuate openings are formed in a valve plate located between the end of the rotor and the front of the frame. It is advantageous if the end of the rotor is provided with a sliding sealing plate with an opening for the transfer of the medium to and from the transition in the head and / or the rotor.

It is advantageous if the piston is provided with a piston ring at each end.

It is advantageous if the piston ring is undivided, the end of the piston being designed to be removable for the insertion of this undivided piston ring.

Overview of figures in the drawings

For a better understanding, the invention is illustrated in the accompanying drawings, in which:

SK 93-2020 A3

FIG. 1 shows a cross-sectional axonometric view of a radial piston rotary machine, in particular a compressor;

FIG. 2 shows an axonometric exploded view of the machine of FIG. 1;

FIG. 3 shows an axonometric exploded view of the valve means of the machine;

FIG. 4 shows an axonometric view of the machine piston;

FIG. 5 shows an axonometric view of the rotor of a machine without a sliding sealing plate at one end of the rotor;

FIG. 6 shows an axonometric exploded view of the rotor of a machine with sliding sealing plates at the ends of the rotor and venous plates;

FIG. 7 schematically shows the operating phase of the machine with the medium inlet and outlet closed;

FIG. 8 schematically shows the operating phase of a machine with an open inlet and outlet of the medium;

FIG. 9 shows an overall external axonometric view of the radial piston rotary machine of FIG. 1, in a frame in the form of a closed housing with openings for air inlet and outlet, and with a protruding shaft of the machine.

FIG. 10 shows a cross-sectional axonometric view of a variant of a radial rotary machine with rings without rings, in a piston chamber without an insert, without sliding sealing plates at the rotor ends, and with a transition to medium inlet and outlet to or from a piston chamber formed in the rotor;

FIG. 11 shows an axonometric exploded view of the machine of FIG. 10.

Examples of embodiments of the invention

The radial piston rotary machine according to the invention is explained in more detail by means of exemplary embodiments shown in the figures.

The machine shown in FIG. 1 to 6 is in particular a compressor, and the rotary machine shown in FIG. 10 and 11 can be a pump or also a compressor of small dimensions.

The machine according to the illustrated examples is formed with two pistons 4, each slidably reciprocally movable to one chamber 22 of the rotor 2, where the chambers 22 are arranged at an angle of 90 ° to each other.

The machine, compressor according to FIG. 1 to 6, comprises a frame 1, in the example shown in the form of a two-part housing. In the frame 1 a rotor 2 is rotatably mounted in bearings 12 in the faces 11 of the frame 1. In the rotor 2 an axial hole 21 is formed for the shaft 5 of the machine and a chamber 22 for the pistons 4.

The shaft 5 passes through the axial bore 21 of the rotor 2 and is rotatably mounted in bearings 15 in the faces 11 of the frame 1. The shaft 5 projects on one side through the face 11 of the frame 1, where it is sealed for example by a conventional shaft seal. Circular cams 51 are arranged on the shaft 5. The shaft 5 is mounted eccentrically with respect to the rotor 2, the eccentricity of the axis of rotation of the shaft 5 from the axis of rotation of the rotor 2 equal to the eccentricity of the axis of the stem cam 51 from the axis of rotation of the shaft 5.

The circular cams 51 are mounted on the shaft 5 by a detachable tongue-and-groove connection. This is advantageous from the point of view of production and also when folding the machine. However, it is also possible to form the shaft 5 in one piece with the cams 51 as is customary in the prior art.

A piston 4 is rotatably mounted on the circular cam 51. The piston 4 has a respective opening 41 for mounting on the circular cam 51. This opening 41 extends transversely to the center of the piston 4. The piston 4 thus has two ends, where at each of them the piston 4 is provided with a piston. The piston ring 43 is received in a groove 42 formed in the piston 4. The piston ring 43 can be used both split and undivided. In the case of using an undivided piston ring 43, the respective end of the piston 4 is made removably designed to make available a groove 42 for inserting such an undivided piston ring 43.

In the example shown, the piston 4 is provided at each end with one piston ring 43. One piston ring 43 for each end of the piston 4 is sufficient, but a larger number of piston rings 43 can be selected as required, if necessary in terms of dimensions, or the material of the piston rings 43, or the applications where the machine according to the invention will be used.

The piston ring 43 ensures the tightness of the piston 4 in the chamber 22 for the piston 4 in the rotor 2, or the tightness of the piston 4 in the insert 31 of the chamber 22 for the piston 4. As surprisingly found, the piston ring 4 small tolerances in the relative seating of the respective rotating and moving parts, i.e. the rotor 2, the shaft 5, the circular cams 51a of the pistons 4, as required in the machines according to the prior art. Such required small tolerances can be maintained without major problems with small machines, but with larger machines it is problematic to maintain such small tolerances while requiring special and expensive production. Failure to comply with the prescribed tolerances means that in the prior art machines, due to insufficient alignment of the respective rotating and moving parts, these parts can become stuck and run erratically. This can be eliminated either by increasing the power supplied to the shaft, or also by including e.g. of the gear transmission between the shaft 5 and the rotor 2. The additional transmission then practically takes over the function of driving the rotor 2 from the pistons 4.

When the piston 4 is accommodated in the chamber 22, or the insert 31, by means of the piston rings 43, work is carried out

SK 93-2020 A3 of the machine, the respective rotating moving parts are continuously aligned to each other in an ideal position ensuring the smooth running of the machine. During production, tolerances of the order of hundreds of millimeters are sufficient, which do not increase the production costs in any way due to the need for special precision production. In this way, the machine runs completely smoothly, while the tightness of the piston 4 is fully preserved, practically from the start-up of the machine.

The chamber 22 for the piston 4 in the rotor 2 is closed by a head 3. The head 3 is arranged removably fixed on the rotor 2, and is at each end of the chamber 22. In the illustrated embodiment, the head 3 is formed with an insert 31 of the chamber 22 for the piston 4. In this case, the insert 31 forms the inner space of the chamber 22 in which the piston 4 moves, and thus the tight sliding bearing of the piston is formed by the inner wall of the insert 31a by the piston ring 43. The insert 31 is preferably designed to extend as close as possible to to the distance between the axes of rotation of the shaft 5 and the rotor 2.

The insert 31 is advantageous due to its simple replacement during wear, i.e. it is not necessary to replace or grind the entire rotor 2 directly to the chambers 22 when the pistons 4 move directly in the chambers 22 without inserts 31. Furthermore, by means of the insert 31 it is possible ensure that the chambers 22 are not connected via the axial bore 21 in the rotor 2, in the case of larger machine dimensions and larger strokes of the piston 4, when the edge of the piston 4 could pass below the contour of the axial bore 21, causing undesired leakage of medium from the chamber 22 of the piston 4 into this axial hole 21. This then makes it possible to manufacture the machine without the need for, for example, a split rotor 2, in order to achieve the smallest possible diameter of the axial hole 21 of the rotor 2. At least one passage 32 is formed in the head 3 to enter and exit the medium. and from the chamber 22 for the piston 4, in this example the chamber 22 with the insert 31. If the chamber 22 for the piston 4 does not contain the insert 31, this transition 32 can be formed either also only in the head 3 or partially in the head 3 and whether partially in the rotor body 2, or only in the rotor body 2 as will be described below in the exemplary embodiment according to FIG. 10 and 11. The passage 32 formed only in the rotor body 2 can in some way reduce the volumetric efficiency of the compressor, but in the case of pumps or blowers, for example, this is irrelevant.

The passage 32 for the inlet and outlet of the medium to and from the chamber 22 for the piston 4 is axially opening in the direction of the face 11 of the frame 1, i.e. axially with respect to the rotor 2 and the shaft 5. The description also applies to the second piston 4 and the second chamber 22 for the piston 4. machine according to this exemplary embodiment.

The inlet and outlet of the medium to and from the chamber 22 for the piston 4, in this example chamber 22 with insert 31, is controlled by valve means for opening and closing the inlet and outlet of the medium to and from chamber 22. These valve means are formed in the form of separate arcuate openings 61 opening the passage 32 for the inlet and outlet of the medium to and from the chamber 22. We close the passage 32 is provided by a full part, between the arcuate openings 61, of the body material in which the separate arcuate openings 61 are formed.

In the illustrated embodiment, the arcuate openings 61 are preferably arranged on a valve plate 6 arranged between the rotor 2 and the face 11 of the frame 1. The valve plate 6 is preferably arranged in a groove 16 in the face 11 of the frame. However, a groove 16 is not necessary for accommodating the valve plate 6. The valve plate 6 only needs to be secured against rotation for correct function. In the example shown, the position of the valve plate 6 is secured against rotation by at least one locking pin 63 extending into the plate 6 and the face 11. Of course, other suitable known means can be used to secure the position of the plate 6.

The described type of valve plate 6 is used in axial piston hydraulic pumps, but its use in radial piston rotary machines is not described anywhere, and in compressors known from the prior art it is practically excluded.

In the illustrated embodiment, a sealing plate 7 is preferably mounted at the end of the rotor 2 to ensure a reliable seal of the head 3 and / or the rotor 2 against the valve plate 6, with respect to the medium inlet and outlet passage 32. The sealing plate 7 comprises an opening 71, i.e. openings 71, for the passage of the medium into and out of the passage 32 for the inlet and outlet of the medium to and from the chamber 22 for the piston 4. A seal 322 can advantageously be formed around the axial outlet of the passage 32 in the case of a compressor head 3 and / or rotor 2. It is also advantageous if a similar seal 64 is formed around the arcuate opening 61 on the valve plate 6, relative to the face 11. The above description concerning the valve means also applies to the other end of the rotor 2.

The passage 32, i.e. the passages 32, for the inlet and outlet of the medium to or from the chamber 22 for the piston 4, in the illustrated embodiment with the sealing plate 7, the medium passage openings 71 are opened or closed respectively with the arcuate openings 61 of the valve plate 6. The arcuate openings 61 then respectively communicate with the medium inlet opening 13 for the machine and the medium outlet opening 14 for the machine, which are arranged on the frame 1 of the machine.

In this exemplary embodiment of the machine shown in FIG. 1 to 6, the medium inlet opening 13 for the machine is formed after the connection of the two-part housing, which forms a closed package for the compressor. The opening 13 connects the inner space of the housing to the source of the medium, in this case ambient air. An opening 14, i.e. openings 14 for the outlet of the medium from the machine, are formed on the faces 11 of the housing, in which case they emerge from a groove 16 in which the valve plate 6 is seated.

With regard to the valve means, a variant of the embodiment is also possible, for example without a valve plate 6, where arcuate openings 61 would be formed directly in the faces 11 of the frame 1. It is also possible.

SK 93-2020 A3 without a sliding sealing plate 7 at the end of the rotor 2, where the sliding surface would be directly a side surface of the rotor 2, on which there would be a passage 32 for the inlet and outlet of the medium to and from the piston chamber 22. Such a variant will be described for the sake of clarity in a further exemplary embodiment, which is shown in FIG. 10 and 11.

In general, however, the valve plate 6 and the sliding sealing plate 7 preferably provide sealing means which are easily replaceable when they wear out.

In the illustrated embodiment of the machine, all rotary bearings are provided with roller bearings. Sliding bearings or combinations of rolling and plain bearings can also be used as required.

The radial piston rotary machine, the compressor, in the described exemplary embodiment shown in FIG. 1 to 6. works as follows.

A shaft 5 connected to a drive (not shown) rotates the circular cams 51, which slidably reciprocate the pistons 4 in respective chambers 22 with inserts 31. The pistons 4 simultaneously rotate the rotor 2. Thanks to the piston rings 43, the compressor operation completely smooth and balanced.

In FIG. 7 and 8 show the positions of the rotating parts after the rotation of the shaft 5 by 180 °, one end position of one of the pistons 4, i being determined as the initial position for easier illustration. j. position at the end of the path of the piston 4 in the chamber 22. This initial position is shown in FIG. 7.

In a given initial position, the cam 51 is in the extreme position of its greatest eccentricity, the piston 4 is thus 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 position furthest from the head 3. The valve plate body 6 in this position closes the media inlet and outlet passages 32 to or from the chamber 22 for the piston 4. In this case, when the sealing plate 7 is present, the openings 71 for the passage of the medium are closed. In said ice, on the one hand, the air from the chamber 22 is substantially completely expelled and, on the other hand, sucked into the maximum working volume of the chamber 22.

By rotating the shaft 5, on one side, the hole 71 passes beyond the edge of the arcuate hole 61, connecting the chamber 22 to the air inlet. In the example shown, the air inlet is provided by an opening 13 on the compressor housing, which supplies air to the interior of the housing. From the interior of the housing, air is led through the inlet grooves 62 to the arcuate opening 61 in the valve plate 6.

At the same time, on the other hand, the opening 71 passes beyond the edge of the second arcuate opening 61, connecting the chamber 22 to the air outlet. In the example shown, the air outlet is provided by an opening 14 in the face 11 of the housing, where this opening leads to a channel 17 in the face 11 on the side of the valve plate 6.

The arcuate openings 61 on the valve plate 6 are segmented in the figures, i. j. it is not a continuous arcuate opening 61. This is to maintain the strength of the valve plate 6, the material of the plate 6 between the segments of the arcuate opening 61 not affecting the permeability of the medium to and from the piston chamber 22. Where the construction allows, the openings 61 can be formed. as continuous. The separation of the arcuate openings 61 with respect to the separation of the inlet and outlet part of the medium must, of course, be maintained.

In the case of a pump, i.e. when pumping liquids, due to their incompressibility, the opening of the chamber 22 into the passages 32 must take place simultaneously. In compressors, depending on the outlet pressure, the edge of the outlet arc 61 can be shifted so that the opening 32, in this case the opening 71, is closed longer by the valve plate body 6, thereby compressing the air as the working volume of the chamber 22 decreases.

Further rotation of the shaft 5 decreases at one end of the piston 4 the volume of the chamber 22 above the piston 4 and at the other end of the piston 4 the volume of the chamber 22 above the piston 4 increases, whereby air is expelled on one side and sucked on the other.

In the position shown in FIG. 8, the piston 4 is in the middle position, the passages 32, in this case also the openings 71, being fully open.

By further rotating the shaft 5, the volume of the chamber 22 at one end of the piston 4 decreases, continuing to expel air from the chamber 22, and increasing the volume of the chamber 22 at the other end of the piston 4, thereby continuing to suck air into the chamber 22. in this example further through the opening 71 in the sealing plate 7 into the arcuate groove 61 and from there into the opening 14 for the exit of the medium from the machine. At the end of the whole cycle, i.e. with two rotations of the shaft 5, the piston 4 is again at one end in the position closest to the head 3, and at the other end in the position furthest from the head 3. The valve plate body 6 closes the openings 32 in this position. in the case of openings 71, so that no backflow of air can occur between the chambers 22 above the respective ends of the piston 4.

Said method of operation is the same also for machine variants, where for example valve plates 6 and sliding sealing plate 7 will not be used and valve means will be formed directly in the frame 1 of the machine, practically in the faces 11.

In the case of a compressor, it is most advantageous to form the frame 1 in the form of a housing, as shown in its entirety on the outside in FIG. 9. In this way, a compact machine is obtained, wherein such a housing protects the rotating parts of the machine and also contributes to reducing the noise of the machine. In addition, in the case of a compressor, the rotor 2 can be cooled by rotating itself in the surrounding air intake medium, so that no additional cooling device, such as a fan, is required. Unlike a known reciprocating compressor, such a compressor is capable of continuous operation. The cooling efficiency can also be further increased by injecting a small amount of oil into the intake air.

SK 93-2020 A3

To illustrate the efficiency of the machine, the compressor, according to the illustrated embodiment, the specific dimensions and parameters of the manufactured compressor prototype are given below.

The external dimensions of the compressor housing shown in FIG. 9 are 140 x 140 x 180 mm. The volume of the compressor is 90 cm ³ per 1 revolution of shaft 5. The compressor was connected to an electric motor with a power of 1.5 kW. Noise was measured, output power in 1 / min. and power consumption. Specifically measured values at 800 rpm. were: - noise level 54 dBA, without acoustic cover

- output power 60 1 / min. at a pressure of 2 bar, power consumption 280 W

- output power 40 1 / min. at a pressure of 8 bar, power consumption 520 W

In total, the operation of the compressor was tested at operating speeds from 200 to 3,500 rpm. The maximum measured pressure has so far been 16 bar.

It follows from the configuration of the machine according to the invention that for the dimensions of the outer casing 200 x 200 x 270 mm the compressor will have a volume of 305 cm ³ / rev, and for the dimensions of the outer casing 250 x 250 x 350 mm the compressor will have a volume of 720 cm ³ / rev. With relatively small external dimensions, the compressor will have many times the working volume.

For example, the frame 1 can also be designed, for example, in such a way that it does not form an integral housing, but will be in the form of a frame structure which ensures the required position and strength of the faces 11 relative to each other. An opening 13 for the entry of the medium into the machine will then be formed accordingly on the body of the face 11.

In FIG. 10 and 11 show a variant of a radial piston rotary machine according to this solution, i.e. a complete rotor part of a machine with a shaft 5, with pistons 4 without rings 43, chambers 22 for piston 4 without insert 31, without sliding sealing plates 7 at the ends of rotor 2, as by a passage 32 for the inlet and outlet of the medium to and from the chamber 22 only in the rotor 2. A machine with such a rotor part can be, for example, a pump or a compressor of small dimensions, in which small tolerances can be maintained Larger tolerances are possible with larger pumps, as these are balanced by the working fluid. The valve means, i.e. the arcuate openings 61 or the valve plate 6, as well as the sliding sealing plate 7, and their possible combinations for this machine example are the same as described in the exemplary embodiment according to FIG. 1 to 6. The frame 1 of the machine can, if desired, be formed as a housing, or also in the form of a frame structure which ensures the required position and strength of the faces 11 relative to each other, as described.

The method of operation of the machine according to the exemplary embodiment shown in FIG. 10 and 11 is the same as described above, except, of course, that the respective parts present in the exemplary embodiment shown in FIG. 10 and 11. The radial rotary machine according to the invention can be a compressor, a pump, a vacuum pump, or possibly also a motor.

Thanks to the described valve means, it is also possible to reverse the machine without any additional modifications, where practically only the function of the opening 13 for the entry of the medium into the machine changes to the function of the opening 14 for the exit of the medium and vice versa. The design of the radial piston rotary machine according to the invention also makes it possible to manufacture the compressor as a multistage, for example to achieve higher pressures. In the described and illustrated example of a compressor, the chambers 22 and the pistons 4 are of the same size, i. j. the working volume of each chamber 22 is the same size.

In a multistage compressor, it is possible to form one chamber 22 with a larger volume, i.e. also with a larger piston 4, and one chamber 22 with a smaller volume, i.e. also with a smaller piston 4. The medium inlet would then be made into the chamber 22 with a larger volume, and of this larger chamber 22 would be fed to the medium inlet of the chamber 22 with a smaller volume. The outlet of the high pressure medium would then be the outlet of the medium from the chamber 22 with a smaller volume.

Also not excluded are embodiments of the machine which will comprise several chambers 22 with pistons 4, or with a different mutual angle than in the described exemplary embodiments. In such cases, however, these will be the design solutions only of the chambers 22 for the pistons 4 and their arrangement in the rotor 2, while the essence of the solution will be preserved with all its advantages.

The radial rotary piston machine of the present invention can be manufactured by commonly available and used techniques and materials. The individual parts of the machine can also be easily produced using 3D printing technology. The use of special materials is only envisaged for special applications such as oil-free compressors, pumps or compressors for extreme loads, etc.

Industrial applicability

The radial piston rotary machine according to the invention can be used as a compressor, a pump, a vacuum pump or even a motor.

A radial reciprocating rotary machine as a compressor can be used for a wide range of applications in a wide range of pressures and flow rates, for example as blowers, low pressure, medium pressure or high pressure compressors.

SK 93-2020 A3

A radial piston rotary machine such as a vacuum pump can be used as an efficient vacuum pump to create a vacuum, as well as a multi-stage vacuum pump to achieve a high vacuum. The pump is simply created only by connecting the suction to the space where the vacuum is required without the need for any further design modifications.

Claims (7)

SK 93-2020 A3 PATENT CLAIMS A radial piston rotary machine comprising a fixed frame, at least one opening for the entry of medium into the machine and at least one opening for the exit of medium from the machine, wherein the frame comprises faces between which a rotor is mounted in rotatable bearings, the rotor comprising an axial opening for a machine shaft and further comprising at least two axially displaced piston chambers transversely to its axis, the machine shaft passing through an axial hole in the rotor and being mounted in rotatable bearings in the frame faces, circular cams arranged on the shaft, the shaft being mounted eccentric to the rotor, the eccentricity 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 slidably mounted in the piston chamber in the rotor and rotatable on a circular cam on the shaft where the ends of the piston chamber are closed at least one passage for the inlet and outlet of the medium from the piston chamber, which are opened and closed by valve means, characterized by t in that the head (3) and / or the rotor (2) comprise at least one passage (32) for the inlet and outlet of the medium to and from the chamber (22) for the piston (4), which at one end opens in the axial direction to the face (11). ) of the frame (1), and which is opened and closed at the axial outlet by valve means in the form of separate arcuate openings (61). A radial piston rotary machine according to claim 1, characterized in that the chamber (22) for the piston (4) is provided with an insert (31), and this insert (31) is connected to the head (3) of the chamber (22). A radial piston rotary machine according to claim 2, characterized in that the insert (31) passes through the chamber (22) for the piston (4) up to the vicinity of the machine shaft (5). Radial piston rotary machine according to any one of the preceding claims, characterized in that separate arcuate openings (61) are formed in a valve plate (6) arranged between the end of the rotor (2) and the face (11) of the frame (1). A radial piston rotary machine according to any one of the preceding claims, characterized in that the end of the rotor (2) is provided with a sliding sealing plate (7) with an opening (71) for medium transfer to and from the passage (32) in the head (3) and / or rotor (2). A radial piston rotary machine according to any one of the preceding claims, characterized in that the piston (4) is provided at each end with a piston ring (43). A radial piston rotary machine according to claim 6, characterized in that the piston ring (43) is undivided, the end of the piston (4) being formed removably for the insertion of an undivided piston ring (43). 9 drawings