SK500572019U1 - Piston rotary pump, compressor or vacuum pump - Google Patents

Abstract

A reciprocating rotary pump, compressor or vacuum pump comprising a housing (1) fitted with a cylindrical hole (11) for a cylindrical rotor (4) wherein the rotor (4) comprises an axial bore (41) for the shaft (7) of the pump, compressor or vacuum pump and at least two chambers (42) angularly offset relative to the rotor axis (4), wherein a piston (5) is slidably mounted in each chamber (42) and is formed with an opening (53) for a circular cam (8) on the shaft (7) of a pump, compressor or vacuum pump and wherein at least one cam (8) is detachably firmly mounted on the shaft (7). The shaft (7) is mounted eccentrically to the rotor (4), the housing (1) is equipped with removable faces (2) with bearings (21) for the shaft (7) and for sealing the cylindrical hole (11) for the rotor (4), the housing (1) further comprises at least one inlet opening (12) for the supply of medium to the chamber (42) of the piston (5) and at least one outlet opening (13) for the outlet of the medium from the chamber (42) of the piston (5).

Description

SK 50057-2019 U1

Field of technology

The technical solution relates to a reciprocating rotary pump, a compressor or a vacuum pump, in general to pumps for liquids or compressible fluids.

Prior art

Pumps or compressors 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 and U.S. Pat. No. 1,910,876 come from the same author. U.S. Pat. No. 1,853,394 to D. Appel discloses a rotary machine or pump comprising a housing, with a circular chamber in the housing, where the inlet and 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 piston bores. 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 essentially 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, the same applicant, which refers to said US 1,853,394, then discusses the properties of the described rotary pump in more detail. With the pumps described in these 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 fluid 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 and 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 circular 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 the same as the piston diameter to allow the drive shaft to rotate correctly to align its eccentrics with respect to the circular piston holes after one of the eccentrics has been moved through the circular hole of one of the pistons. Consequently, pumps with a ratio of less than 5 to 1 will be formed with an orifice of such a size that the reciprocating pistons will not continuously overlap this orifice and these pumps will thus be unusable. The pump design of Figures 5 to 10 of U.S. Pat.

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 compressor volume control on the compression of compressible fluids, such as 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. The compressor shaft is formed integrally with the circular cams. Each cam is constructed such that the cam diameter is reduced without changing the cam eccentricity by placing the cam portion 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 opposite cam portion. reliefs on the cam assembly are provided 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 U.S. Pat. No. 7,423,895 is its design complexity, which results in particular from the use of rolling bearings.

The aim of this technical solution is to design a pump, compressor or pump of this type, which is characterized by low production, while practically eliminating all the disadvantages and limitations resulting from the construction in the described documents. Such a pump, compressor or pump design would allow the production of pumps or compressors for a wide range of applications and pressure ranges while maintaining the same design.

SK 50057-2019 U1

The essence of the technical solution

This object is achieved by a reciprocating rotary pump, compressor or pump according to this technical solution comprising a housing in which there is a cylindrical hole for a cylindrical rotor, the rotor comprising an axial bore for the pump, compressor or pump shaft and at least two angularly offset transversely to the rotor axis. chamber, where in each chamber there is a sliding reciprocating piston which is formed with an opening for a circular cam on the shaft of a pump, compressor or pump, the shaft being mounted eccentric to the rotor, the housing being provided with removable faces with shaft bearings and for tight sealing of the cylinder the rotor hole, and the housing further includes at least one fluid inlet to the piston chamber and at least one fluid outlet from the piston chamber, wherein the eccentricity of the axis of rotation of the shaft from the axis of the cylindrical rotor is equal to the eccentricity of the axis of the circular cam from the axis of rotation of the shaft. The essence of the pump, compressor or pump according to this technical solution lies in the fact that at least one cam is mounted on the shaft detachably fixed.

Preferably, the detachable fixed bearing of the cam on the shaft is formed by a detachable connection and the axial position of the cams and the shaft is secured by a cam stop on the shaft and a delimiting element arranged between the cam and the housing face of the rotary piston pump, compressor or pump. The most advantageous detachable cam bearing is a tongue-and-groove joint. The cam stop on the shaft can advantageously be formed by a shaft shoulder.

Preferably, the delimiting element is formed integrally with the face. The spacer element may also advantageously comprise a bearing for the rotor.

The main advantage of the technical solution is that the axial bore in the single cylindrical rotor can have the minimum possible diameter, ie only such a diameter is sufficient to allow smooth rotation of the eccentric shaft mounted against the rotor, and also such that it is possible when assembling a pump, compressor or pump. place the cams on the shaft through this hole. It is not necessary for the diameter of the axial bore in the rotor between the piston chambers to be at least such that the shaft formed with the cams can easily pass through, as in the construction described in the prior art. This orifice in prior art pumps has a minimum diameter such as the diameter of the circle described by the cam when the shaft rotates, which then results in the disadvantages described in the prior art. The pump, compressor or pump according to this technical part can thus be formed in different ratios of rotor diameter and piston stroke without having to assemble a rotor from several parts as stated in the prior art for certain values of these ratios and the rotor can always be formed as monolithic body. This then ensures the structural simplicity of the rotor as well as the strength of the rotor body.

If the cam and shaft axial position delimiter arranged between the cam and the pump or compressor housing closing face is formed in one piece with the pump or compressor housing closing face, this delimiting element forms a shaft bearing which carries the shaft from the outer edge of the main edge. passes to the inside of the rotor up to the cam on the shaft. Such a bearing then provides a very good shaft support, especially for high pressure pump or compressor applications, where these bearings ensure that the geometry of the circular eccentric mechanism required to operate the pump or compressor is maintained.

In the case of heavy-duty pumps, compressors or pumps, it is also advantageous to move the shaft and the rotor in motion, so that the rotor is rotated by both the pistons and the pump or compressor shaft.

For a reciprocating rotary compressor, it is advantageous if the shaft comprises lubricant lines and / or openings on the lubricant distributor under pressure to the friction surfaces of the moving parts of the compressor, where the lubricant lines and / or openings on the shaft are connected to the lubricant lines and / or openings in moving and / or fixed parts of the compressor, with a lubricant inlet to the compressor and a lubricant outlet from the compressor. It is also advantageous to lubricate the reciprocating rotary compressor so that the lubricant outlet is only in the space between the piston wall and the piston chamber wall.

It is also advantageous to lubricate the reciprocating rotary compressor so that a lubricant pump is connected to the shaft and connected to the lubricant inlet and lines and / or the lubricant orifice.

Preferably, the lubricant pump is a vane pump having at least one vane, the vane being received in a groove at the end of the shaft. The end of the shaft with the vane is inserted in a lubricant pump chamber formed in a lubricant pump housing mounted on the front of the compressor housing.

For a reciprocating rotary pump, it is advantageous if the shaft comprises lubricant lines and / or openings for distributing lubricant under pressure to the friction surfaces of the moving parts of the pump, where the lubrication lines and / or openings on the shaft are connected to lubricant lines and / or openings in moving and / or fixed parts of the pump, the lubricant inlet to the pump and the lubricant outlet from the pump. A lubricant pump is then connected to the pump shaft and connected to the lubricant inlet and the lubricant lines and / or ports.

Preferably, the lubricant pump for the reciprocating rotary pump is a vane pump having at least one vane, the vane being received in a groove at the end of the shaft. The end of the shaft with the vane is inserted in a lubricant pump chamber formed in a lubricant pump housing mounted on the front of the pump housing.

SK 50057-2019 U1

Overview of figures in the drawings

The technical solution is shown for better understanding in the attached drawings, in which:

FIG. 1 shows an axonometric exploded view of a pump, compressor or pump according to this technical solution;

FIG. 2 shows a side view in a sectioned section of a pump, compressor or pump according to this technical solution;

FIG. 3 schematically shows the operating phases of a pump, compressor or pump according to this technical solution;

FIG. 4 shows an axonometric exploded view of a compressor or pump according to this technical solution with a lubrication system;

FIG. 5 shows a side view of a compressor or a pump according to this technical solution in the assembled state with a lubrication system;

FIG. 6 is a cross-sectional view of a lubricant pump for the lubrication system of the compressor or pump of FIG. 4 and FIG. 5.

Examples of embodiments

A reciprocating rotary pump, compressor or pump according to this technical solution is further described and explained by way of example with reference to the figures. According to the figures, the pump, compressor or vacuum pump is designed as a two-cylinder, i.e. with two chambers 42 for the pistons 5.

The pump, compressor or pump comprises a pump, compressor or pump housing 1 with inlet openings 12 for the supply of medium to the chamber 42 of the piston 5 and outlet openings 13 for the outlet of the medium from the chamber 42 of the piston 5. In the housing 1 there is a cylindrical hole 11 for the cylindrical rotor 4. The housing 1 is provided with removable faces 2 with bearings 21 for the shaft 7 and for tightly closing the cylindrical hole 11.

The rotor 4 comprises an axial bore 41 for the shaft 7 of a pump, compressor or pump. In the rotor 4, two chambers 42 for pistons 5 are formed transversely to the axis of the rotor 4. In the example shown, the chambers 42 are at an angle of 90 ° to each other. One piston 5 is slidably mounted in each chamber 42.

The piston 5 is formed as a symmetrical body with two ends 51, 52, where the end surfaces 51, 52 of the piston 5 are rounded with the outer cylindrical surface of the rotor 4. The piston 5 is cylindrical in the example shown and the chambers 42 are then cylindrical. However, the shape of the pistons 5 can also be other than cylindrical. The piston 5 can also have a cross section, e.g. rectangular, square, polygonal, elliptical, etc. The piston 5 is formed in the middle with an opening 53 for a circular cam 8, which ensures the reciprocating movement of the piston 5.

The circular cam 8 is mounted on a shaft 7. The shaft 7 is mounted eccentric to the rotor 4. The eccentricity of the axis of rotation of the shaft 7 from the axis of the cylindrical rotor 4 is equal to the eccentricity of the axis of the circular cam 8 from the axis of rotation of the shaft 7.

The circular cam 8 is detachably fixed on the shaft 7. That is, there is a connection between the cam 8 and the shaft which allows the cam 8 to be mounted or withdrawn from the shaft and at the same time the cam 8 mounted on the shaft in the desired position does not move relative to the shaft 7, i.e. it cannot rotate freely on the shaft 7. move along shaft 7. The movement of the cam 8 on the shaft 7 within the manufacturing tolerances is not considered to be a free movement of the cam 8 on the shaft.

In the exemplary embodiments described and shown in the figures, the fixed cams 8 are detachably mounted on the shaft 7. As will be described below when describing the assembly of a pump or compressor according to this technical solution, it is also possible to form the shaft 7 in such a way 8 formed together with the shaft 7, i.e. not detachably fixed but only fixedly on the shaft 7. However, in this way a shaft 7 can be formed with only one cam 8, this fixed cam 8 having to be arranged in position on the shaft 7 in the case of more than two cylinders. closest to the center of the rotor 4.

In the exemplary embodiment shown, the detachable connection of the cam 8 and the shaft 7 is formed by a tongue-and-groove shaft bearing. In the shaft 7, a groove 71 for the tongue 6 is formed in the usual manner at the location of the cam 8, and a hole 81 for the shaft 7 with a groove for the tongue 6 is then formed in the conventional housing in the conventional manner. stated purpose, such as e.g. grooving, pin connection, etc. The tongue-and-groove connection used appears to be the most advantageous in terms of the production and assembly of the pump, compressor or pump.

The shaft 7 and the cams 8 must also be secured within the pump, compressor of the pump, against axial movement, i.e. against axial movement relative to the housing 1 of the pump, compressor or pump.

This axial position of the shaft 7 and the cams 8 is ensured in the illustrated embodiment by a stop 72 of the cam 8 n of the shaft 7 and a delimiting element 3 arranged between the cam 8 and the face 2 of the housing 1.

In the embodiment shown, the stop 72 on the shaft 7 is in the form of a shaft shoulder 7. This stop 72 can also be formed in another form, e.g. shaft circlip, etc. However, the illustrated embodiment of the stop 72 is the most advantageous and practically simplest from the point of view of production.

SK 50057-2019 U1

In the preferred embodiment shown, the delimiting element 3 is formed in one piece with the face 2, i.e. the face 2 is practically formed into an extension extending inside the rotor 4 up to the respective cam 8.

The face 2 thus formed forms a bearing for the shaft 7, which carries the shaft 7 along a length substantially from the outer edge of the face 2 of the housing 1 to the cam 8 on the shaft 7. Such a bearing provides very good support for the shaft 7 in the case of a high-vacuum pump, where these bearings ensure that the geometry of the circular eccentric mechanism is maintained. The geometry of the circular eccentric mechanism could be disturbed at high pressures by bending the shaft 7, which would block the rotational movement and interrupt the operation of the pump, compressor or pump. The delimiting element 3 can also be designed as a separate element, e.g. in the form of a ring or sleeve and the like. slid onto the shaft 7 between the cam 8 and the face 2 of the housing 1. In this case, however, the bearing capacity of the shaft 7 at the face 2 is limited.

Although in the above description, the means for securing the cam 8 and the shaft 7 against axial movement, i. j. the stop 72 and the delimiting element 3, described with one cam at one end of the housing 1, these means are analogous also to the expensive cam 8, i.e. at the expensive end of the housing 1.

If necessary, preferably for example for pumps, compressors or heavy-duty pumps, an embodiment is also possible in which a bearing for the rotor 4 is also formed on the delimiting element 3. Thus, a bearing surface is formed on the inside of the rotor end 4 and the corresponding bearing surface is then formed on the delimiting element 3. The delimiting element 3 can be formed integrally with the face 2, but can also be formed separately, e.g. in the form of a ring or sleeve and the like. slid onto the shaft 7 between the cam 8 and the face 2, as described.

In the case of heavy-duty pumps or compressors, it is also advantageous to movably connect the shaft 7 and the rotor 4, i.e. that the driven shaft 7 also rotates the rotor 4, which is otherwise rotated only by the pistons 5 driven by the shaft 7. This connection of the shaft 7 and the rotor 4 can be created by any known transfer, e.g. gears, toothed belt, chain drive, etc. in such a ratio that the rotor 4 makes one revolution for two revolutions of the shaft 7.

The method of operation of a rotary piston pump or compressor according to this technical solution is described below with reference to FIG. 3. The pump, compressor or pump is shown in fig. 3 shown in cross section, seen from the output end of the shaft 7 to which the drive of the pump, compressor or pump is connected. In the case of a vacuum pump, it is clear that the medium inlet 12 is connected to a space in which a vacuum or vacuum needs to be created.

The shaft 7 is rotated in the direction shown by the arrow R, clockwise. The figure shows the positions of the rotating parts successively after the rotation of the shaft by 90 °, while for the sake of simplicity one extreme position of one of the pistons 5, i is determined as the starting position. j. position at the end of the path of the piston 5 in the chamber 42. This initial position is in the upper row at the position 0 °. The lower row is then the corresponding positions of the expensive piston 5 at the perpendicular arrangement of the two pistons. In the starting position according to FIG. 3 the cam 8 is in the extreme position of greatest eccentricity, the piston 5 is thus in the extreme position at the end of the piston path 5. One end 51 of the piston 5 is closest to the wall of the cylinder hole 11 for the rotor 4. The end surface 51, 52 of the piston 5 of the cylindrical hole 11 for the rotor 4 and at this extreme position the surface of the end 51 of the piston 5 is aligned with and almost touches the inner surface of the hole 11 for the rotor 4. However, the actual contact of these areas must not occur. The expensive end 52 of the piston 5 is then furthest from the wall of the cylindrical hole 11 for the rotor 4. In this position, the rotor body 4 in this position, preferably with an overlap, closes the inlet 12 for the medium, liquid or gas supply and the outlet 13 for the medium. Likewise, the chamber 42 is also closed with an overlap by the housing body 1 of the pump or compressor. These overlaps ensure a sufficiently tight closure of the chambers 42 and the openings 12, 13 in this extreme position against undesired backflow of the medium through the pump, compressor or pump, thus replacing the non-return valves. At this stage, on one side of the end 51 of the piston 5, the medium is substantially completely expelled from the chamber 42 and on the opposite end 52 of the piston 5 is sucked into the maximum working volume of the chamber 42 defined by the chamber wall 42. 4.

By rotating the shaft 7, shown at 90 °, on one side the rotor body 4 passes beyond the edge of the inlet opening 12, opening the chamber 42 into the inlet opening 12 and at the same time on the expensive side the rotor body 4 passes beyond the edge of the outlet opening 13, opening the chamber 42 into the outlet opening 13. In the case of a pump, i.e. when pumping liquids, due to their incompressibility, the opening of the chamber 42 into the openings 12, 13 must take place simultaneously. In addition, in the case of compressors, the edge of the outlet opening 13 can be shifted according to the output pressure so that the rotor body 4 opens the outlet opening 13 later, thereby compressing the gas as the working volume of the chamber 42 thus closed relative to the outlet opening 13 closes with the rotor body 4. rotation of the shaft 7 decreases the volume of the chamber 42 above the piston 5 at one end 52 of the piston 5 and increases the volume of the chamber 42 above the piston 5 at the expensive end 51 of the piston 5, whereby the medium is forced into the outlet 13 on one side and sucked on the expensive side. through the inlet 12.

At the 180 ° position in FIG. 3 the piston 5 is in the middle position. In the example shown, complete openness occurs

The chamber 42 at both ends 51, 52 of the piston 5, respectively, into the inlet opening 12 and the outlet opening 13, i.e. the rotor body 4 in the example shown does not interfere in any way with the openings 12, 13.

By further rotation of the shaft 7, which is shown at 270 °, the volume of the chamber 42 at one end 52 of the piston decreases, continuing to expel the medium from the piston chamber 42 and increasing the volume of the chamber 42 at the other end 51 of the piston 5. 42.

At the end of the whole cycle, in one rotation of the shaft 7, shown at 360 °, the piston 5 at one end 52 is closest to the wall of the cylinder hole 11 for the rotor 4 and at the other end 51 furthest from the wall of the cylinder hole 11 for the rotor 4. in this position it closes again the inlet opening 12 for the supply of medium, liquid or gas, and the outlet opening 13 for the outlet of this medium, so that no backflow of the medium can occur.

When carrying out a rotary reciprocating compressor or a pump according to this technical solution, it is also advantageous to provide lubrication of the moving parts. An exemplary embodiment of a compressor or pump according to this technical solution with lubrication is shown in FIG. 4 to FIG. 6.

The arrangement of the individual parts of the compressor or pump is the same as in the example described above with reference to FIG. 1 and 2. In the case of a compressor or pump, the faces 2 of the housing 1 are preferably provided with seals 14, e.g. known sealing rings. To ensure lubrication, a pump 10 of lubricant, usually oil, is then connected to the compressor or pump, and the individual parts of the compressor or pump, i.e. the shaft 7, cams 8, pistons 5, faces 2, housing 1 or rotor 4, contain guides and / or holes 9. lubricants We distribute the lubricants under pressure to the friction surfaces of the moving parts of the compressor or pump, and also then we discharge the lubricants from said parts. The lubricant pump 10 in the exemplary embodiment shown in FIG. 4 to 6, a single vane pump driven directly by the shaft 7 of a compressor or a pump according to this technical solution. The lubricant pump 10 is formed by a housing 101 with a chamber 102 in which the vanes 103 move. The lubricant housing 101 is provided with a lubricant inlet 91 to the compressor or pump, which in this case opens into the chamber 102, surfaces of compressor or pump parts. In the example shown, the housing 101 is fastened by means of screws 106 to one face 2 of the housing 1 of the compressor or pump. The shaft 7 passes through the face 2 into the chamber 102 of the lubricant pump 10. The shaft 7 is provided at this end with a groove 105 for the blades 103 of the lubricant pump 10. A spring 104 is arranged between the lamellae 103, which presses the lamellae 103 against the wall of the chamber 102. Depending on the required lubricant pressure, e.g. at the required small lubricant discharge volume, the lubricant pump 10 can have only one vane 103 in the groove 105 of the shaft 7. Of course, it is also possible to form such a vane pump with a different number of vane than known from vane pump designs.

The lubricant is guided from the pump 10 by lines and / or lubricant openings 9 formed in the shaft 7 and also in other moving and / or fixed parts of the compressor or pump to the respective friction surfaces of the compressor or pump parts, in particular to the sliding bearing of the piston 5 and the cams 8, the sliding flat piston 5 and the piston chamber 42, the sliding bearings of the shaft 7 in the faces 2, and the sliding bearing of the rotor 4 in the cylinder hole 11 in the housing 1. After passing through the lubrication system, the lubricant lubricants on the faces 2. In general, the lubricant inlet 91 as well as the lubricant outlet 92 can be formed on other parts of the compressor or pump as described in the examples shown. These are practically all externally accessible parts of the compressor or pump, such as the housing 1, any of the faces 2, the shaft 7 and the like. It is understood that the lubricant inlet 91 and the lubricant outlet 92 may be formed by a single lubricant inlet 91a and a lubricant inlet 92a, depending on the lubrication needs, construction, compressor or pump housing, and the like. It is also possible to make a compressor where the lubricant outlet 92 is not discharged on the outer sides of the housing 1, face 2, shaft 7 and below, but the lubricant is actually forced into the medium outlet 13 around the pistons 5. The lubricant is then separated from the gaseous medium by known and supplies lubricant to the inlet 91. In this case, it is necessary to maintain the condition that the outlet pressure of the lubricant pump 10 is equal to or greater than the outlet pressure of the compressor for efficient lubrication, so that the compressed gas is not forced into the lubricant.

It is also possible to make the lubrication compressor without a lubricant pump 10. The lubricant outlet 92 is also not discharged on the outer sides of the housing 1, face 2, shaft 7 and below, but the lubricant is forced into the medium outlet 13 around the pistons 5. The outlet 13 is then connected to a lubricant separator in which a lubricant supply is formed. replenished with lubricant separated from the compressed gas. Compressed gas then leaves the separates after separation, and at the same time the compressor outlet pressure acts on the level of the lubricant supply. The lubricant is then fed from the separator to the lubricant inlet 91, into which it is forced by the gas pressure in the separator. Said lubrication can also be performed in such a way that the entire compressor is in a closed pressure vessel, in which there is at the same time a lubricant separator and a lubricant supply. The part of the compressor with the lubricant inlet 91 is then preferably immersed in said lubricant supply. From the outside of said pressure vessel there is then only an inlet of gaseous medium and an outlet of compressed medium.

In addition to lubrication, the lubricant also performs a sealing function, when sealing the working space defined by the end 51, 52 of the piston 5, the wall of the piston chamber 42 by the housing wall 1. Due to the fact that the lubricant is supplied to the lubrication system of the compressor or pump the centering function of the rotating parts such as the shaft 7 in the bearings 21, and the circular cam 8 in the cam hole 53. Toto do

SK 50057-2019 U1 helps to maintain the exact geometric arrangement of the parts, which is important for the smooth operation of the compressor or pump according to this technical solution.

In the case of large compressors or pumps, it is advantageous to connect an external lubricant pump to the lubricant inlet 91 and to push the lubricant into the lubrication system of the compressor or pump before the compressor or pump starts up. This prevents "dry" starting, and also due to the pressure of the lubricant, the relevant parts of the compressor or pump are centered, which ensures a smooth start of the compressor or pump. After the compressor or pump has started, the external pump is disconnected and further lubrication is provided either by the lubricant pump 10 itself or also by the lubrication methods mentioned above, i. j. by pressure through the medium outlet 13. The external pump can advantageously use its own supply of compressor or pump lubricant.

The compressor or pump with the described lubrication system operates in the same way as described above with reference to FIG. 3.

In the case of a pump, without a lubrication system, the lubrication and the above functions are usually provided directly by the pumped medium.

The compressor according to this technical solution can also be formed without the described lubrication system, i.e. as described with reference to FIG. 1 and 2. Materials which do not require lubrication can then be used for the respective friction parts, or the lubricant can be injected in small quantities or sucked into the compressed gaseous medium. In oil-free compressors, water can also be advantageously used as a lubricant.

A reciprocating rotary pump, compressor or pump according to this technical solution as described in the above-mentioned exemplary embodiments and shown in the figures, as well as in other embodiments in accordance with the essence of this technical solution, can be assembled as described below.

In the first step, all, in the example shown, both pistons 5 without circular cams 8 are inserted into the rotor 4, so that the holes 53 in the pistons 5 are passable for the shaft 7. In the next step, the shaft 7 is inserted into the rotor 4 on one side. with one cam 8 mounted, releasably fixed or only fixed, the shaft 7 being inserted into the rotor 4 with the end without the cam 8. In this way, the shaft 7 is inserted into the opening 53 of the further piston 5.

In the case of a number of pistons of more than two, a cam 8 is first mounted on the shaft 7, which will be in the middle, resp. closest to the center of the rotor 4. This cam 8 may optionally be fixed, i. j. formed as part of the shaft 7. Further cams 8 are then inserted from the side of the respective ends of the shaft 7.

In the next step, the piston 5 in which the cam 8 is already mounted is moved to the extreme position. The piston 5, where the cam 8 is not fitted, is moved to the central position, i.e. so that the outer diameter of the cam 8 and the inner diameter of the rotor 4 are coaxial, on one axis. In the next step, on the other side of the rotor 4, the second, resp. another cam 8 in a row.

The rotor assembly 4 thus assembled with the pistons 5, the cams 8 and the shaft 7 is inserted into the cylindrical hole 11 in the housing 1. The faces 2 are then slid onto the shaft 7 on each side, which closes the pump or compressor housing 1.

It is then possible to connect a drive (not shown) to the shaft 7, to the inlet opening (s) 12 for the medium supply and to the outlet opening (s) 13 for the outlet of the medium, e.g. pipes, tubes, ports, etc. to the inlet and outlet of the pumped or compressed medium, in the case of a compressor or a lubricated pump then to the lubricant inlet 91 and the lubricant outlet 92 e.g. pipes, tubes, ports, etc. for the supply and output of lubricant to and from the compressor or pump.

The described exemplary embodiments with reference to the accompanying drawings serve only to explain the essence of the technical solution, and are examples of specific embodiments of a pump, compressor or pump according to this technical solution, which in no way limit this technical solution to the specific examples shown in the drawings.

Other embodiments of pumps, compressors or pumps are also possible, which may have a different number of pistons 5, different angular displacement of pistons 5, different shape of ends 51, 52 pistons 5, different shape of chambers 42 for pistons 5 than cylindrical, other types of connecting means used such as screws, etc. Embodiments are also possible, with different sizes of pistons 5 and correspondingly chambers 42 for pistons. Such an arrangement is advantageous, for example, in the construction of a multistage compressor, where the size of the pistons 5 and thus also of the chambers 42 gradually decreases, e.g. to the high-pressure outlet, and thus the medium outlet 13 from one chamber 42 is then connected to the medium inlet 12 to another chamber 42 in the respective row of chambers 42 with pistons 5.

In view of the tightness of the pump, compressor or pump according to this technical solution, it is also possible to use other sealing means of the respective parts than those described, e.g. known shaft seals, sealing rings, etc. However, it should be noted that even in the described and illustrated embodiments, the pump, compressor or pump is a very efficient rotary machine with smooth balanced and quiet operation, with a simple construction with low production and operating costs.

The pump, compressor or pump according to this technical solution can be manufactured with commonly available and used technological procedures and with common materials. The use of special materials before

SK 50057-2019 U1 only applies to special applications such as oil-free compressors, pumps or compressors for extreme loads, etc.

The use of rolling bearings, which could be considered for larger pumps or compressors, is also not excluded, but plain bearings are completely sufficient for the widest practical use.

Industrial applicability

The reciprocating rotary pump according to this technical solution can be used for practically all known pump applications.

The reciprocating rotary compressor according to this technical solution 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.

The reciprocating rotary pump according to this technical solution can be used as an efficient vacuum pump to create a vacuum, as well as a multi-stage pump to achieve a high vacuum. The pump is simply formed by connecting the inlet opening 12 as the pump inlet without any further structural modifications.

Claims (6)

SK 50057-2019 U1 PROTECTION REQUIREMENTS A reciprocating rotary pump, compressor or pump comprising a housing in which there is a cylindrical hole for a cylindrical rotor, the rotor comprising an axial bore for a pump, compressor or pump shaft and at least two angularly offset chambers transversely to the rotor axis, wherein in each chamber is a sliding reciprocating piston which is formed with a hole for a circular cam on the shaft of a pump, compressor or pump, the shaft being mounted eccentric to the rotor, the housing being provided with removable faces with bearings for the shaft and rotor and for tightly closing the cylinder hole for the rotor, and the housing further comprises at least one fluid inlet to the piston chamber and at least one fluid outlet from the piston chamber, wherein the eccentricity of the axis of rotation of the shaft from the axis of the cylindrical rotor is equal to the eccentricity of the axis of the circular cam from the axis of rotation of the shaft. that at least one cam (8) is detachably fixed on the shaft (7). Piston rotary pump, compressor or pump according to claim 1, characterized in that the detachable fixed bearing of the cam (8) on the shaft (7) is formed by a detachable shaft connection and the axial position of the cams (8) and the shaft (7) is secured by a stop (72) cams (8) on the shaft (7) and a delimiting element (3) arranged between the cam (8) and the face (2) of the housing (1) of the pump, compressor or pump. Piston rotary pump, compressor or pump according to claim 2, characterized in that the detachable shaft connection is a tongue-and-groove connection and the cam stop (72) on the shaft (7) is formed by a shaft shoulder (7). Piston rotary pump, compressor or pump according to claim 2 or 3, characterized in that the boundary element (3) is formed integrally with the face (2). A reciprocating rotary pump, compressor or pump according to any one of claims 2 to 4, characterized in that the delimiting element (3) comprises a bearing for the rotor (4). 6 drawings