SK9206Y2 - 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

Technical field

The technical solution relates to a reciprocating rotary pump, a compressor or a vacuum pump, in general 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. 4,723,895.

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 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 in more detail the properties of the described rotary pump. In the case of the pumps described in the said documents, it is essential that the central, axial opening in the cylinder be continuously covered by the pistons and that it never be exposed, so that 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 diameter of the piston to allow the drive shaft to rotate to the correct alignment of 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 opening of such a size that the reciprocating pistons will not continuously overlap 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 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 diameter of the cam is reduced without changing the eccentricity of the cam by placing a portion of the cam of the opposite cam projection in a position closer to the center of the shaft than its outer circular surface and on the outer circular surface of the shaft. the cam parts of the opposite cam projection are provided with reliefs for assembling the pistons with the shaft.

Said shaft reliefs are important in order to reduce the diameter of the holes formed in the pistons into which the cam is inserted, and in order 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 constructional complexity, which results in particular from the use of roller bearings.

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

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 hole on the pump, compressor or pump shaft and at least two angularly offset transversely to the rotor axis. chambers, where in each chamber a piston is slidably mounted, which is formed with an opening for a circular cam on the shaft of a pump, compressor or pump, the shaft being mounted eccentrically against the rotor, the housing being provided with removable faces with shaft mounting and tight sealing of the cylinder. a rotor hole, and the housing further includes at least one fluid inlet port for the piston chamber and at least one fluid outlet port of the piston chamber, the eccentricity of the axis of rotation of the shaft from the axis of the cylindrical rotor 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 detachably fixed on the shaft.

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 shaft bearing of the cam is a tongue-and-groove joint. The cam stop on the shaft can advantageously be formed by a shoulder shoulder.

It is advantageous if 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 a single cylindrical rotor can have the minimum possible diameter, i.e. only such a diameter is sufficient to allow trouble-free rotation of an eccentric shaft mounted against the rotor, and also such as to be possible when folding a pump, compressor or pumps the cams through the hole on the shaft. 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 the cesium, as in the construction described in the prior art. This bore 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 has the disadvantages described in the prior art. The pump, compressor or pump according to this technical solution can thus be formed in different ratios of rotor diameter and piston stroke, without it being necessary for certain values of these ratios to assemble, for example, a rotor from several parts as stated in the prior art, and the rotor can be always created as a 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 along the longitudinal edge of the outer edge. the housing extends 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 use of the pump or compressor, where these bearings ensure that the geometry of the circular eccentric mechanism required for the operation of 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 simultaneously by the pistons and the pump or compressor shaft.

For a reciprocating rotary compressor, it is advantageous if the shaft comprises lubrication lines and / or openings on the lubricant distributor under pressure to the friction surfaces of the moving parts of the compressor, where the lubrication lines and / or openings on the shaft are connected to the lubrication 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 connected to the lubricant inlet and the lubricant lines and / or openings.

Preferably, the lubricant pump is a vane pump having at least one vane, the vane being housed 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 rotary piston 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 the lubrication 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 openings.

Preferably, the lubricant pump for the reciprocating rotary pump is a vane pump having at least one vane, the vane being housed 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.

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 sectional view of a pump, compressor or pump according to this technical solution in the assembled state;

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 shows a cross-section 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 a cylindrical rotor 4. The housing 1 is provided with removable faces 2 with bearings 21 on the shaft 7 and for sealing the cylindrical hole 11.

The rotor 4 comprises an axial bore 41 on 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 may also be other than cylindrical. The piston 5 may 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 eccentrically against 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 mounted on the shaft 7. This means that there is a connection between the cam 8 and the shaft which allows the cam 8 to be fitted or removed from the shaft and at the same time the cam 8 mounted on the shaft in the desired position does not move against the shaft 7, i.e. it cannot rotate freely on the shaft 7. shaft 7 scroll. 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 illustrated embodiments, both 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 so that it already contains one a cam 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 in case of more than two cylinders. 7 closest to the center of the rotor 4.

In the illustrated embodiment, the detachable connection of the cam 8 and the shaft 7 is formed by a tongue-and-groove shaft bearing. A groove 71 for the tongue 6 is formed in the shaft 7 in a conventional manner in the bearing 7 of the cam 8, and a hole 81 is then formed in the camshaft in a conventional manner for the shaft 7 with a tongue groove 6. This detachable connection can also be formed by other known shaft bearings in the purpose, such as grooving, pin connection, etc. The tongue-and-groove connection used appears to be the most advantageous from the point of view of the manufacture and assembly of the pump, compressor or pump.

The shaft 7 and the cams 8 must also be secured within the pump, compressor or pump against axial movement, i.e. against axial movement against 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 on 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.

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 forms a very good support of the shaft 7 especially for high pressure pump or compressor use. 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, thereby blocking the rotational movement and interrupting the operation of the pump, compressor or pump. The delimiting element 3 can also, if desired, be formed as a separate element, e.g. in the form of a ring or case 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 in the face 2 is limited. This can be advantageous at lower working loads and the face 2 can then be a simple workpiece.

Although in the above description there are means for securing the cam 8 and the shaft 7 against axial movement, i. j. the stop 72 and the delimiting element 3, described at one cam at one end of the housing 1, these means are analogous to the other 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 case 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 outlet 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 opening 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 simplest illustration 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 are then the corresponding positions of the expensive piston 5 at the perpendicular arrangement of the two pistons. In the initial 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 cylindrical hole 11 on the rotor 4. The end surface 51, 52 of the piston 5 copies the inner surface. of the cylindrical hole 11 to 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 of the rotor 4. However, these surfaces must not actually come into contact. The second end 52 of the piston 5 is then furthest from the wall of the cylindrical hole 11 on 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 outlet. 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 by the end 52 surface of the piston 5 and the cylinder bore 11 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 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 requirement so that the rotor body 4 opens the outlet opening 13 later, thereby compressing the gas while reducing the working volume of the chamber 42 thus closed against the outlet opening 13 by the rotor body 4. Further rotation of the shaft 7, at one end 52 of the piston 5 the volume of the chamber 42 above the piston 5 decreases and at the other end 51 of the piston 5 the volume of the chamber 42 above the piston 5 increases, whereby on one side the medium is forced into the outlet 13 and sucked through inlet 12.

In the 180 ° position in FIG. 3, the piston 5 is in the middle position. In the example shown, the chamber 42 is fully opened at both ends 51, 52 of the piston 5 into the inlet opening 12 and the outlet opening 13, respectively, i.e. the rotor body 4 in the example shown does not interfere with the openings 12, 13 in any way.

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 as it continues to expel media from the piston chamber 42 and the volume of the chamber 42 at the expensive end 51 of the piston 5 increases, continuing to suck media into the chamber. 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 cylindrical hole 11 for the rotor 4 and at the other end 51 furthest from the wall of the cylindrical hole 11 for the rotor 4. in this position, it again closes 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 piston compressor or 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 with reference to FIG. 1 and 2. In the case of a compressor or a 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, the cams 8, the pistons 5, the faces 2, the housing 1 or the rotor 4, contain guides and / or openings 9. lubricants for distributing the lubricant under pressure to the friction surfaces of the moving parts of the compressor or pump, and also then discharging 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, and lubricant lines and / or openings 9 to the respective friction. surfaces of compressor or pump parts. In the example shown, the house 101 is fastened by means of shortcuts 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 on the vanes 103 of the lubricant pump 10. A spring 104 is arranged between the vanes 103, which presses the vanes 103 against the wall of the chamber 102. Depending on the required lubricant pressure, e.g. with 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 movable 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 circular 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 cylindrical hole 11 in the housing 1. After passing through the lubrication system, the lubricant then exits the lubricant outlet 92, in the example shown on the faces 2. In general, the lubricant inlet 91 as well as the lubricant outlet 92 can also 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. The lubricant inlet 91 and the lubricant outlet 92 may be formed by both a single lubricant inlet 91a and a lubricant outlet 92 and a plurality of lubricant inlets 91a depending on the lubrication needs, design, 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, etc., but the lubricant is actually forced into the medium outlet 13 around the pistons 5. The lubricant is then separated from the gaseous medium in a known manner and supplies lubricant to the inlet 91. In this case, for efficient lubrication, 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, so that no compressed gas is 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 connected to the outer sides of the housing 1, face 2, shaft 7, etc., 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 supply is formed. lubricants supplemented 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 the supply of gaseous medium and the outlet of compressed medium.

In addition to lubrication, the lubricant also fulfills 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 under sufficient pressure the centering function of the rotating parts, such as the shaft 7 in the bearings 21a, the circular cam 8 in the cam hole 53. This 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 starting the compressor or pump. 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 starting the compressor or the pump, the external pump is disconnected and further lubrication is provided either by the lubricant pump 10 itself or also by the mentioned lubrication methods, i. j. by pressure through the medium outlet 13. In this case, the external pump can advantageously use its own supply of lubricant from the compressor or the pump.

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

In the case of a pump, without a lubrication system, 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 amounts or sucked into the compressed gaseous medium. In the case of 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, detachably or firmly mounted, 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, closing the housing 1 of the pump or compressor.

A drive (not shown) can then be connected to the assembled pump, compressor or pump for use to the shaft 7, to the inlet / outlet 12 for the medium supply and to the outlet / opening 13 for the outlet, 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 do not limit this technical solution in any way, only 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 of pistons 5, different shape of chambers 42 for pistons 5 than cylindrical, other types of connecting means used. such as screws, etc. Embodiments with different sizes of pistons 5 and corresponding piston chambers 42 are also possible. Such an arrangement is advantageous, for example, in the construction of a multi-stage compressor, where the size of the pistons 5, and thus also of the chambers 42, is gradually reduced, 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 a respective row of chambers 42 with pistons 5.

From the point of 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 as 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 by commonly available and used technological procedures and with common materials. The use of special materials is only contemplated for special applications, such as oil-free compressors, pumps or extreme load compressors, and the like.

The use of roller bearings, which could be considered for pumps or compressors of larger dimensions, 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 applications of pumps.

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 inlet of the pump without any further structural modifications.

Claims (12)

CLAIMS FOR PROTECTION 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 the pump, compressor or pump shaft and at least two angularly offset chambers transversely to the rotor axis, wherein in each chamber is a sliding and 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 eccentrically against the rotor, the housing being provided with removable faces with bearings on the shaft and rotor and for tightly closing a cylindrical hole on the rotor, and the housing further comprising at least one inlet for supplying medium to the piston chamber and at least one outlet for outleting medium from the piston chamber, the eccentricity of the axis of rotation of the shaft from the axis of the cylindrical rotor 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 mounted 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 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 stop (72) of the cam (8) 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 delimiting element (3) is formed integrally with the face (2). Piston 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). Reciprocating rotary pump, compressor or pump according to any one of the preceding claims, characterized in that the shaft (7) is kinically connected to the rotor (4). Reciprocating rotary compressor according to any one of the preceding claims, characterized in that the shaft (7) comprises lubrication lines and / or holes (9) for distributing lubricants under pressure to the friction surfaces of the moving parts of the compressor, where the lines and / or holes ( 9) for lubricant on the shaft (7) are connected to lubricant lines and / or openings (9) in the moving and / or fixed parts of the compressor, a lubricant inlet (91) to the compressor and a lubricant outlet (92) from the compressor. Piston rotary compressor according to Claim 7, characterized in that the lubricant outlet (92) is only in the space between the wall of the piston (5) and the wall of the chamber (42) of the piston (5). Reciprocating rotary compressor according to Claim 7 or 8, characterized in that a lubricant pump (10) is connected to the shaft (7) and is connected to the lubricant inlet (91) and the lubricant lines and / or openings (9). Reciprocating rotary compressor according to claim 9, characterized in that the lubricant pump (10) is a vane pump having at least one vane (103), the vane (103) being accommodated in a groove (105) at the end of the shaft (7). , wherein the end of the shaft (7) with the vane (103) is inserted in the chamber (102) of the lubricant pump (10) formed in the housing (101) of the lubricant pump (10) mounted on the front (2) of the compressor housing (1). Piston rotary pump according to any one of claims 1 to 6, characterized in that the shaft (7) comprises lubrication lines and / or openings (9) for distributing lubricants under pressure to the friction surfaces of the moving parts of the pump, where the lines and / or the lubricant openings (9) on the shaft (7) are connected to lubricant lines and / or openings (9) in the moving and / or fixed parts of the pump, the lubricant inlet (91) to the pump and the lubricant outlet (92) from the pump, where connected to the shaft (7) is a lubricant pump (10) connected to the lubricant inlet (91) and the lubricant lines and / or openings (9). Piston rotary pump according to claim 11, characterized in that the lubricant pump (10) is a vane pump having at least one vane (103), the vane (103) being accommodated in a groove (105) at the end of the shaft (7). , wherein the end of the shaft (7) with the vane (103) is inserted in the chamber (102) of the lubricant pump (10) formed in the housing (101) of the lubricant pump (10) mounted on the front (2) of the pump housing (1).