SK288973B6 - 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

The field of technology

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

Current state of the art

Reciprocating rotary machines, in particular pumps or compressors, are known, which include a rotor of circular cross-section, in which piston chambers are formed, the pistons being mounted on circular cams to carry out a reciprocating movement, and these cams are formed on a shaft, which is mounted eccentrically against the rotor. The eccentricity of the shaft axis from the rotor axis is equal to the eccentricity of the cam from the shaft axis.

Reciprocating rotary machines of the mentioned type are described, for example, in documents US 1 853 394, US 1 910 876 and US 4 723 895.

Document US 1,853,394 describes a rotary machine or pump comprising a casing with a circular chamber within the casing, where the inlet and outlet are on opposite sides of the casing. A cylinder is rotatably placed in the chamber, which contains an axial opening, a pair of mutually perpendicular working chambers passing 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. Eccentrics move in the holes of the pistons. The shaft is placed eccentrically with respect to the axis of the circular chamber. The respective diameters of the eccentrics, holes in the pistons and the axial hole in the cylinder are essentially the same, and the diameters of the rotating cylinder and eccentrics are limited to sizes where the axial hole of the cylinder 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 liquids or gases.

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

With the pumps described in the mentioned documents, it is essential that the central, axial opening in the cylinder is continuously covered by the pistons and that it is never uncovered, and thus the flow of the working medium cannot occur from one chamber of the cylinder to another. This condition makes it impossible to construct a single-cylinder pump with a ratio of pump rotor diameter to piston stroke of less than 5 to 1. This is because the assembly of the rotor with the pistons can only be achieved by axially sliding the drive shaft through the central rotor hole and the circular holes in the pistons. . In order for such a folding procedure to be possible, the central hole must have such a cross-section that the drive shaft with eccentrics can easily rotate in it. Additionally, the lateral distance between the piston chambers must be approximately equal to the diameter of the piston to allow the drive shaft to rotate into proper alignment of its eccentrics with respect to the piston bores after one of the eccentrics has been moved through the bore of one of the pistons. Subsequently, 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 overlap the opening, rendering the pumps unusable. The pump design of Figures 5 to 10 of US 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 split to allow assembly with a smaller central bore.

However, the split rotor must show the same characteristics as the single-cast 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.

Document US 7,423,895 describes a method and apparatus for providing volume control of a compressor for compressing compressible gases such as refrigerant for a refrigeration cycle. This document describes a compressor with the principle on which devices according to US 1853 394, US 1910 876 work. In this solution, the relevant rotating parts of the compressor are mounted on rolling bearings. Each cam on the compressor shaft is designed so that the cam diameter is reduced without changing the eccentricity of the cam by positioning the cam portion of the opposite cam boss closer to the center of the shaft than its outer circular surface and on the outer circular surface of the shaft at parts of the cam opposite the cam protrusion are created reliefs for assembly of the pistons with the shaft.

Said shaft reliefs are important in order to reduce the diameter of the holes created in the pistons in which the cam is inserted, and to be able to assemble the shaft, pistons and rotor in the described configuration. The disadvantage of the construction of the compressor according to document US 7,423,895 is its structural complexity.

In the document US 2015/0098841 A1, a rotary epicyclic pump with pistons mounted on circular cams, as is known from said documents, is described. This pump uses a split rotor, but not for the reason that a higher piston stroke can be achieved, but for the reason that the described pump can be assembled without the need to split one piston into two parts.

Suction and discharge are ensured by the rotation of the rotor in the cylindrical opening, where the rotor body opens and closes the inlet and outlet radial openings, in the cylindrical surface of the cylindrical opening in the housing - the pump stator.

For the correct operation of the pump, both for the sake of ensuring tightness between the suction and discharge parts, as well as for the smooth rotation of the rotor and the drive shaft with circular cams, it is necessary to make a very precise fit of the rotor in the cylindrical recess on the rotor in the casing - the pump stator. This condition is extremely important, especially if these machines are intended for operation without lubricant, i.e. as so-called oil-free. Ensuring the necessary accuracy increases production demands. Failure to comply with strict tolerances can already cause leaks and irregularities in the operation of the machine, i.e. "jamming in positions that do not show the necessary accuracy." To some extent, such a shortcoming can be overcome by creating a 2:1 gear ratio between the shaft and the pump rotor. Although such a distribution can facilitate the operation and loading of the working parts of the pump, for example substantial lateral loading of the pistons, it represents a negative with respect to the simplicity, efficiency of the machine, as for example stated in US 2015/0098841 Al.

Document US 2015/0098841 A1 also describes a possible embodiment of the pump where the ends of the piston bore in the rotor are connected to the heads. The valve plates may contain valves that control the inlet and outlet of the medium supplied to the respective side ports in the fronts. Thus, at least one valve is connected to one of the piston bores. In a certain embodiment, one of the valves is an outlet valve on the piston head and the other valve is an inlet valve on the piston, whereby the medium can enter through the central part of the pump crankcase and exit through the head. This arrangement uses the familiar check valves used in reciprocating compressor heads. To the disadvantages of these non-return valves, which mainly lie in their construction, in the case of the described embodiment, negative effects from the rotation of the valve plate around the axis of rotation of the rotor can be added, i.e. negative effects of centrifugal/centrifugal forces that will increase with the distance of the valve plate from the axis of rotation of the rotor . In this case, the rotor does not have to be cylindrical.

The aim of this invention is a piston rotary machine that can be used as a pump, compressor, vacuum cleaner or motor, which is characterized by low production costs, while practically eliminating all disadvantages and limitations resulting from the constructions in the described documents. At the same time, such a piston rotary machine would enable the production of pumps, compressors and vacuum cleaners for a wide range of applications and pressure ranges while maintaining the same structural arrangement. At the same time, it is also desirable that such a construction, namely a compressor or a vacuum pump, should be able to work without lubricant or in the so-called oil-free operation.

The essence of the invention

The stated objective is achieved by a radial piston rotary machine according to the invention comprising a fixed frame, at least one opening for the medium to enter the machine and at least one opening for the medium to exit from the machine, where the frame contains faces between which a rotor is placed in rotating bearings, this rotor contains axial hole for the machine shaft and further contains transversely to its axis at least two chambers for pistons angularly offset against each other, the machine shaft passes through the axial hole in the rotor and is mounted in rotating bearings in the fronts of the frame, circular cams are arranged on the shaft, the shaft is mounted eccentrically against rotor, while 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. the head or rotor includes at least one passage for the supply and exit of the medium from the piston chamber, which are opened and closed valve means. The essence of the piston rotary machine according to the present invention is that the head and/or the rotor contain at least one transition for the input and output of the medium into and from the piston chamber at one end opening in the axial direction to the face of the frame, which is opened and closed by valves at the axial outlet means in the form of separate arc openings.

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

It is advantageous if the insert passes through the piston chamber up to the vicinity of the shaft of the pump, compressor or vacuum cleaner.

It is advantageous if the valve means in the form of separate arc openings are formed in the valve plate placed between the end of the rotor and the face of the frame. It is advantageous if the end of the rotor is equipped with a sliding sealing plate with an opening for the transfer of medium to and from the passage in the head and/or rotor.

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

It is advantageous if the piston ring is undivided, while the end of the piston is made removable to insert this undivided piston ring.

Overview of images on drawings

The invention is illustrated for better understanding in the attached drawings, in which:

Fig. 1 shows an axonometric sectional view of a radial piston rotary machine, namely a compressor;

Fig. 2 shows an axonometric exploded view of the machine from fig. 1;

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

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

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

fig. 6 shows an axonometric exploded view of the rotor of the machine with sliding sealing plates at the ends of the rotor and valve plates;

Fig. 7 schematically shows the working phase of the machine with the media inlet and outlet closed;

Fig. 8 schematically shows the working phase of the machine with an open supply and outlet of the medium;

Fig. 9 shows a general exterior axonometric view of the radial piston rotary machine of FIG. 1 in a frame in the form of a closed case with openings for air inlet and outlet and with a projecting shaft of the machine;

fig. 10 shows an axonometric cross-sectional view of a variant of a radial rotary machine with pistons without rings, in a piston chamber without an insert, without sliding sealing plates at the ends of the rotor and with a passage for the input and output of the medium to or from the piston chamber formed in the rotor;

fig. 11 shows an axonometric exploded view of the machine from fig. 10.

Examples of implementation of the invention

The radial piston rotary machine according to the present invention is explained in more detail on the examples of implementation shown in the figures.

The machine shown in fig. 1 to 6 is specifically the compressor and rotary machine shown in fig. 10 and 11 can be a pump or a compressor of small dimensions.

The machine according to the illustrated examples is made with two pistons 4, each sliding and reciprocating in one chamber 22 of the rotor 2, where the chambers 22 are arranged at an angle of 90° to each other.

Machine, compressor according to fig. 1 to 6, includes the frame 1 in the illustrated example in the form of a two-part case. In the frame 1, the rotor 2 is rotatably mounted in bearings 12 in the fronts 11 of the frame 1. In the rotor 2, an axial opening 21 for the shaft 5 of the machine and a chamber 22 for the pistons 4 are created.

The shaft 5 passes through the axial opening 21 of the rotor 2 and is rotatably mounted in bearings 15 in the faces 11 of the frame 1. The shaft 5 on one side protrudes through the face 11 of the frame 1, where it is sealed, for example, by a common shaft seal. Circular cams 51 are arranged on the shaft 5. The shaft 5 is placed eccentrically against the rotor 2, while 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.

The circular cams 51 are mounted on the shaft 5 by a detachable tongue-and-groove joint. This is advantageous in terms of production and also when assembling the machine. However, it is equally possible to form the shaft 5 in one unit with the cams 51, as is common in the state of the art.

A piston 4 is rotatably mounted on the circular cam 51. The piston 4 has a corresponding hole 41 created for mounting on the circular cam 51. This hole 41 passes transversely through the center of the piston 4. The piston 4 thus has two ends, where the piston 4 is equipped with a piston ring 43. The piston ring 43 is placed in the groove 42 formed in the piston 4. The piston ring 43 can be used both divided and undivided. In the case of using a non-split piston ring 43, the corresponding end of the piston 4 is made removable in order to make available a groove 42 for inserting such a non-split piston ring 43.

In the illustrated example, the piston 4 is equipped at each end with one piston ring 43. One piston ring 43 for each end of the piston 4 is sufficient, but it is possible to choose a larger number of piston rings 43 as needed, if necessary in terms of dimensions or material. piston rings 43, or applications where the machine according to this invention will be used.

The piston ring 43 ensures the tightness of the piston 4 in the chamber 22 to the piston 4 in the rotor 2 or the tightness of the piston 4 in the insert 31 of the chamber 22 to the piston 4. As it was surprisingly found, the piston ring 4 also ensures the smooth operation of the machine without having to observe extraordinary small tolerances in the relative positions of the respective rotating and moving parts, i.e. the rotor 2, the shaft 5, the circular cams 51 and the pistons 4, as required in machines according to the prior art. Such required small tolerances can be observed without major problems for small-sized machines, but for larger machines it is problematic to observe such small tolerances, requiring special and expensive production. Non-observance of the prescribed tolerances means for machines in the current state of the art that during rotation, due to insufficient alignment of the relevant rotating and moving parts, these parts may seize and run irregularly. This can be eliminated either by increasing the power supplied to the shaft, or by including e.g. gear between the shaft 5 and the rotor 2. The additional gear then practically takes over the function of driving the rotor 2 from the pistons 4.

When the piston 4 is placed in the chamber 22 or the insert 31 by means of the piston rings 43, during the operation of the machine, the corresponding rotating movable parts are continuously aligned to each other in an ideal position ensuring smooth operation of the machine. During production, there are then sufficient tolerances in the order of hundredths of a millimeter, which in no way increase production costs due to the need for special precise production. In this way, the machine runs completely smoothly, while the tightness of the piston 4 will be fully preserved, practically from the start of the machine.

The chamber 22 for the piston 4 in the rotor 2 is closed by the head 3. The head 3 is arranged on the rotor 2 in a removably fixed manner and is at each end of the chamber 22. In the shown embodiment, the head 3 is formed with the insert 31 of the chamber 22 for the piston 4. In this case the insert 31 creates 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 31 and the piston ring 43. It is advantageous to make the insert 31 so that it passes as close as possible to the shaft 5, of course with regard to the distance between the axis of rotation of the shaft 5 and the rotor 2.

The insert 31 is advantageous due to its simple replacement when worn, i.e. it is not necessary to replace or grind the entire rotor 2 when the chambers 22 wear out directly, if the pistons 4 move directly in the chambers 22 without the inserts 31. Furthermore, using the insert 31, it is possible to ensure that the chambers 22 are not connected through the axial opening 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 under the contour of the axial opening 21, which would result in an unwanted leakage of the medium from the chamber 22 of the piston 4 into this axial opening 21. This then makes it possible to manufacture the machine without the necessity of, for example, a split rotor 2, in order to achieve the smallest possible diameter of the axial opening 21 of the rotor 2. In the head 3, at least one passage 32 is created for the entry and exit of the medium into and out of the chamber 22 to the piston 4, in this example the chamber 22 with an insert 31. If the chamber 22 to the piston 4 does not contain an insert 31, this transition 32 can be created either also only in the head 3, or partially in the head 3 and partly entirely in the body of the rotor 2, or only in the body of the rotor 2, as will be described in the embodiment example according to fig. 10 and 11. The passage 32 created only in the body of the rotor 2 can reduce the volumetric efficiency of the compressor in a certain way, but for example in the case of pumps or blowers this is insignificant.

The transition 32 for the input and output of the medium to and from the chamber 22 to the piston 4 is axially opened 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 to the piston 4 of the machine according to this embodiment.

The entry and exit of the medium to and from the chamber 22 to the piston 4, in this example the chamber 22 with the insert 31, is controlled by valve means for opening and closing the entry and exit of the medium to and from the chamber 22. These valve means are formed in the form of separate arc openings 61 opening the passage 32 for the entry and exit of the medium to and from the chamber 22. The closure of the passage 32 is ensured by a solid part, between the arc openings 61, of the material of the body in which the separate arc openings 61 are formed.

In the illustrated embodiment, the arc openings 61 are preferably arranged on the valve plate 6 arranged between the rotor 2 and the face 11 of the frame 1. The valve plate 6 is preferably seated in the groove 16 in the face 11 of the frame. However, the groove 16 is not necessarily needed to accommodate the valve plate 6. The valve plate 6 must only be secured against turning for proper function. In the illustrated example, 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. It is of course also possible to use other suitable known means 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 practically excluded in compressors known from the prior art.

In the illustrated embodiment, a sealing plate 7 is preferably fixed at the end of the rotor 2 to ensure a reliable sealing of the head 3 and/or the rotor 2 against the valve plate 6, with respect to the transition 32 for the inlet and outlet of the medium. The sealing plate 7 contains an opening 71, i.e. openings 71, for the passage of the medium to and from the transition 32 to the entry and exit of the medium to and from the chamber 22 to the piston 4. Around the axial outlet of the passage 32, in the case of a compressor, a seal 322 can be advantageously formed in order to prevent possible leaks of pressurized air between the sealing plate 7 and head 3 and/or rotor 2. It is also advantageous if a similar seal 64 is formed around the arc opening 61 on the valve plate 6 against the face 11. The above description regarding the valve means also applies to the other end of the rotor 2.

Passage 32, i.e. passages 32, for the entry and exit of the medium into or from the chamber 22 to the piston 4, in the illustrated embodiment with the sealing plate 7, the openings 71 for the passage of the medium, are opened or closed respectively against the arched openings 61 of the valve plate 6. Arched openings 61 then they respectively communicate with the opening 13 for the input of the medium into the machine and the opening 14 for the output of the medium from the machine, which are arranged on the frame 1 of the machine.

In this example of the embodiment of the machine shown in fig. 1 to 6 is the opening 13 for the medium to enter the machine, created after joining the two-part case, which forms a closed casing for the compressor. The opening 13 connects the inner space of the case with the medium source, in this case the ambient air. The opening 14, i.e. the openings 14 for the outlet of the medium from the machine, are created on the fronts 11 of the housing, while in this case they come out of the groove 16, in which the valve plate 6 is seated.

With regard to the valve means, an embodiment variant is also possible, for example without the valve plate 6, where the arc openings 61 would be created directly in the fronts 11 of the frame 1. An embodiment variant without the sliding sealing plate 7 at the end of the rotor 2 is also possible, where the sliding surface would be directly on the lateral surface of the rotor 2, on which there would be a passage 32 for the entry and exit of the medium to and from the chamber 22 to the piston. For a better idea, such a variant will be described in the next embodiment, which is shown in fig. 10 and 11.

In general, however, the valve plate 6 and the sliding sealing plate 7 advantageously provide sealing means easily replaceable when worn.

In the illustrated example of the machine design, all rotary bearings are equipped with rolling bearings. Sliding bearings or combinations of rolling and sliding bearings can also be used as needed.

Radial piston rotary machine, compressor, in the described embodiment shown in fig. 1 to 6 work as follows.

The shaft 5 connected to the drive (not shown) rotates the circular cams 51, which reciprocate the pistons 4 in the corresponding chambers 22 with inserts 31. The pistons 4 also rotate the rotor 2. Thanks to the piston rings 43, even with the normal tolerances of the storage and alignment of the corresponding rotating parts, the operation compressor completely smooth and balanced.

In fig. 7 and 8 show the positions of the rotating parts after turning the shaft 5 by 180°, while for a simpler illustration, one extreme position of one of the pistons 4 is determined as the initial position, i.e. j. the position at the end of the path of the piston 4 in the chamber 22. This starting position is shown in fig. 7.

In the given initial position, the cam 51 is in the extreme position of its largest eccentricity, the piston 4 is thus in the extreme position at the end of its travel. One end of the piston 4 is therefore in the position closest to the head 3. The other end of the piston 4 is then in the position farthest from the head 3. The body of the valve plate 6 in this position closes the passages 32 for the entry and exit of the medium into or from the chamber 22 on 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 the mentioned phase, on the one hand, the air is essentially completely expelled from the chamber 22 and, on the other hand, sucked into the maximum working volume of the chamber 22.

By rotating the shaft 5, the opening 71 passes on one side behind the edge of the arc opening 61, while connecting the chamber 22 with the air inlet. In the example shown, the air inlet is ensured by the hole 13 on the compressor housing, which supplies air to the inner space of the housing. From the inner space of the case, the air is led through the inlet grooves 62 into the arched opening 61 in the valve plate 6.

At the same time, on the other side, the opening 71 goes beyond the edge of the second arc opening 61, while connecting the chamber 22 with the air outlet. In the illustrated example, the air outlet is ensured by an opening 14 in the front 11 of the case, where this opening leads to the channel 17 in the end 11 on the side of the valve plate 6.

The arc holes 61 on the valve plate 6 are segmented in the figures, i.e. j. it is not a continuous arc opening 61. This is due to the preservation of the strength of the valve plate 6, while the material of the plate 6 between the segments of the arc opening 61 does not in any way affect the permeability of the medium to and from the chamber 22 to the piston 4. Where the design allows, the openings 61 can be created as ongoing. The separation of the arc openings 61 with respect to the separation of the input and output parts of the medium must of course be preserved.

With the 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 the case of compressors, depending on the output pressure, the edge of the output arc opening 61 can be moved so that the opening 32, in this case the opening 71, is closed longer by the body of the valve plate 6, thereby compressing the air while reducing the working volume of the chamber 22.

Further rotation of the shaft 5 results in a decrease in the volume of the chamber 22 above the piston 4 at one end of the piston 4 and an increase in the volume of the chamber 22 above the piston 4 at the other end of the piston 4, whereby air is pushed out on the one hand and sucked in 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, are fully open.

As the shaft 5 rotates further, the volume of the chamber 22 at one end of the piston 4 decreases, continuing to push air out of the chamber 22, and the volume of the chamber 22 at the other end of the piston 4 increases, continuing to draw air into the chamber 22. Air is forced out through the passage 32, in in this example, also through the opening 71 of the pressing plate 7 into the arc groove 61 and from it to the opening 14 for the outlet of the medium from the machine. After the completion of the entire cycle, i.e. during 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 body of the valve plate 6 in this position closes the openings 32, in this case holes 71 so that no backflow of air can occur between the chambers 22 above the respective ends of the piston 4.

The mentioned method of work is the same for machine variants, where, for example, valve plates 6 and sliding sealing plate 7 will not be used, and the valve means will be created directly in the frame 1 of the machine, practically in the fronts 11.

With the compressor, it is most advantageous to make the frame 1 in the form of a casing, as shown in Fig. 9. In this way, a compact machine is obtained, while such a case both protects the rotating parts of the machine and also contributes to reducing the noise of the machine. Moreover, in the case of a compressor, the rotor 2 can be cooled by its own rotation in the surrounding medium, air, so that no additional cooling device, such as a fan, is needed. Unlike the known piston 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.

To illustrate the efficiency of the machine, the compressor, according to the illustrated example of implementation, the specific dimensions and parameters of the manufactured prototype of the compressor are listed 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 level, output power v/min was measured. and input power. Specifically measured values at 800 rpm. were: - noise level 54 dBA, without acoustic covering, - output capacity 60 l/min. at a pressure of 2 bars, input power 280 W, - output power 40 l/min. at a pressure of 8 bar, power consumption 520 W.

Overall, the operation of the compressor was tested at operating speeds from 200 to 3,500 rpm. The maximum pressure measured so far was 16 bars.

From the layout of the machine according to this invention, it follows that with the dimensions of the outer case 200 x 200 x 270 mm, the compressor will have a volume of 305 cm ³ /rev. and with the dimensions of the outer case 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 a multiple times larger working volume.

If necessary, the frame 1 can, for example, also be created in such a way that it will not form a complete case, but will be in the form of a frame structure that ensures the necessary position and strength of the faces 11 against each other. The opening 13 for the input of the medium into the machine will then be created accordingly on the front body 11.

In fig. 10 and 11 shows a variant of the radial piston rotary machine according to this solution, i.e. the complete rotor part of the machine with 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 the rotor 2 and with a transition 32 for the entrance and exit of the medium to and from the chamber 22 only in the rotor 2. A machine with such a rotor part could be, for example, a pump or a compressor with small dimensions, where small tolerances can be observed due to the tightness and alignment of the rotating parts of the machine. Greater tolerances are possible with pumps of larger dimensions, as these are balanced by the working fluid. The valve means, i.e. the arc openings 61, possibly the valve plate 6, as well as the sliding sealing plate 7 and their possible combinations for this example of the machine are the same as described in the embodiment example according to fig. 1 to 6. The frame 1 of the machine can, as needed, be created as a case or also in the form of a frame structure, which ensures the necessary position and strength of the faces 11 against each other, as described.

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

Thanks to the described valve means, reverse operation of the machine is also possible without any additional modifications, when practically only the function of the opening 13 for the medium input into the machine is changed to the function of the opening 14 for the medium output and vice versa. The design of the radial piston rotary machine according to the present invention also enables the compressor to be produced as a multi-stage one, for example to achieve higher pressures. In the described and illustrated example of the compressor, the chambers 22 and the pistons 4 are the same size, i.e. j. the working volume of each chamber 22 is equally large.

In the case of a multistage compressor, it is possible to create 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 input would then be realized in the chamber 22 with a larger volume and the output from of this larger chamber 22 would be brought 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 chamber 22 with a smaller volume.

Also, versions of the machine, which will contain more chambers 22 with pistons 4, or a blue mutual angle, as in the described examples of implementation, are also not excluded. In such cases, however, it will be a design solution of only the chambers 22 for the pistons 4 and their arrangement in the rotor 2, while the essence of the solution with all its advantages will be preserved.

The radial rotary piston machine according to the present invention can be produced by commonly available and used technological procedures and with common materials. Individual parts of the machine can also be easily produced using 3D printing technology. The use of special materials is assumed only for special applications, such as oil-free compressors, pumps or compressors for extreme loads, etc.

Industrial applicability

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

The radial piston rotary machine as a compressor can be used for a wide range of applications in a wide range of pressures and flows, for example as blowers, low pressure, medium pressure or high pressure compressors.

The radial piston rotary machine as a vacuum cleaner can be used as an efficient vacuum cleaner to create vacuum as well as a multi-stage vacuum cleaner to achieve high vacuum. At the same time, the vacuum cleaner is simply created by just connecting the suction to the space where the vacuum is required without the need for any other structural modifications.

Claims (7)

PATENT CLAIMS 1. A radial piston rotary machine comprising a fixed frame, at least one opening for the medium to enter the machine and at least one opening for the medium to exit the machine, where the frame includes faces between which a rotor is mounted in pivoting bearings, this rotor includes an axial opening for the machine shaft and further contains transversely to its axis at least two angularly displaced chambers for pistons, the shaft of the machine passes through an axial hole in the rotor and is mounted in rotary bearings in the fronts of the frame, circular cams are arranged on the shaft, the shaft is mounted eccentrically against the rotor, while the eccentricity 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 mounted reciprocatingly in a piston chamber in the rotor and pivotable on a circular cam on the shaft, where the ends of the piston chamber are closed by heads, the head or the rotor contain at least one passage for the supply and exit of the medium from the piston chamber, which are opened and closed by valve means, characterized by that the head (3) and/or the rotor (2) contain at least one passage (32) for the input and output of the medium to and from the chamber (22) to the piston (4), which at one end exits in the axial direction to the face (11) of the frame (1) and which is opened and closed on the axial outlet by valve means in the form of separate arc openings (61). 2. Radial piston rotary machine according to claim 1, characterized in that the chamber (22) for the piston (4) is equipped with an insert (31) and the insert (31) is connected to the head (3) of the chamber (22). 3. Radial piston rotary machine according to claim 2, characterized in that the insert (31) passes through the chamber (22) on the piston (4) up to the vicinity of the shaft (5) of the machine. 4. Radial piston rotary machine according to any one of the preceding claims, characterized in that the separated arc openings (61) are formed in the valve plate (6) placed between the end of the rotor (2) and the face (11) of the frame (1). 5. Radial piston rotary machine according to any one of the preceding claims, characterized in that the end of the rotor (2) is equipped with a sliding sealing plate (7) with an opening (71) for the transfer of the medium to and from the passage (32) in the head (3) and /or rotors (2). 6. A radial piston rotary machine according to any one of the preceding claims, characterized in that the piston (4) is equipped with a piston ring (43) at each end. 7. Radial piston rotary machine according to claim 6, characterized in that the piston ring (43) is undivided, while the end of the piston (4) is made removable for inserting the undivided piston ring (43). 9 drawings