RU2821717C1 - Two-stage rotary plate supercharger - Google Patents

Abstract

FIELD: machine building.

SUBSTANCE: invention relates to positive displacement units. Two-stage rotary plate supercharger comprises cylindrical housings of the first and second compression stages with openings on the wall, end covers of the cylindrical housing of the first compression stage, a rotor with a drive shaft which is eccentrically located inside the cylindrical housing of the first compression stage, which is mounted on bearings in the hub of the end cover, rotor plates, inlet and outlet branch pipes of the first and second compression stages, intermediate cooler. Rotor consists of a shell in the form of a polyhedron and an end wall connected to the drive shaft. On outer and inner surfaces of rotor shell wall hinges are installed, with which the rotor plates are connected by one of their edges with the possibility of their rotation around the hinge axes. Springs are installed between the rotor plates and the rotor shell wall. Cylindrical housing of the second compression stage is located eccentrically inside the rotor, has inlet openings and is rigidly connected by one of its end edges with the end cover, and on the other end side is closed with a blind wall. Inlet and outlet branch pipes of the second compression stage are installed on the end cover.

EFFECT: invention is aimed at simplifying the design and improving operating reliability of the two-stage rotary plate supercharger.

1 cl, 2 dwg

Description

The invention relates to positive displacement installations, in particular to compressors, and can be used to create increased pressure in a moving gaseous medium or as a vacuum pump.

There are known superchargers with reciprocating movement of the working body - a piston or diaphragm [1]. Their disadvantages include dynamic imbalance of moving masses, structural complexity and the presence of valves.

In relation to piston ones, more compact, having less weight and not requiring a special foundation, are valveless superchargers with rotational movement of the working body, which include, in particular, a rotary vane compressor [2], which ensures a uniform supply of the moved medium. The device [2] is compact, dynamically balanced, and has relatively high performance. The absence of working valves in the device [2] makes it possible to use a high-speed drive of the working body. The disadvantage is the intense wear of the rotor plates and the possibility of them getting pinched in the rotor grooves.

In the known rotary compressor [3], to reduce wear on the rotor plates, an additional rotating bushing with longitudinal windows is installed between the cylindrical stator and the rotor eccentrically located in it with radial grooves and plates placed in the grooves. The presence of an additional rotating bushing in the known device [3] complicates the design and reduces its reliability. During operation of the device, the gap between the rubbing surfaces of the rotating bushing and the stationary stator increases due to their wear, which leads to an increase in uncontrolled flows of the moved medium between the discharge and suction zones.

In the known rotary vane supercharger [4], the plates in the grooves of the rotor are inclined in the direction of rotation of the drive shaft, which somewhat reduces the risk of pinching the plates during their radial movements due to the more favorable direction of the resulting force acting on each plate in relation to the radial arrangement of the plates in rotor slots. The disadvantages of the device [4] and devices [2, 3] include the massiveness of the rotor, which, along with the increased material consumption for its manufacture, leads to an increased starting current in the drive motor, since when putting the devices into operation it is necessary to overcome the significant static inertia force of the massive rotor, as well as limiting the rotor speed by preventing the peripheral speed of the ends of the plates from exceeding approximately 13 m/s. Exceeding this speed value leads to rapid wear of the plates. A common disadvantage of single-stage rotary vane blowers [2, 3, 4] is the limitation of the generated pressure of the moving medium to approximately 1 MPa, which narrows the range of their application.

The created pressure in a rotary vane supercharger can be increased by using several compression stages.

In the known two-stage rotary vane supercharger [5] (prototype), containing cylindrical housings of the first and second compression stages with windows on the walls, end covers of the cylindrical housing of the first compression stage, a rotor eccentrically located inside the cylindrical housing of the first compression stage with a drive shaft, which is mounted on bearings in the end cap hub, rotor plates, inlet and outlet pipes of the first and second compression stages, an intermediate cooler, the presence of a second compression stage, which in its design principle repeats the first stage, allows you to expand the range of the generated pressure to 1.5 MPa. The design of the supercharger [5] is complex, it is labor-intensive to manufacture and has a high specific material consumption. There remains a danger of pinching of the plates in the grooves of the rotors of the first and second compression stages and high wear of the plates.

The technical problem is to simplify the design and increase the reliability of the two-stage rotary vane supercharger.

The problem posed is solved by the fact that a two-stage rotary vane supercharger containing cylindrical housings of the first and second compression stages with windows on the wall, end covers of the cylindrical housing of the first compression stage, a rotor eccentrically located inside the cylindrical housing of the first compression stage with a drive shaft, which is mounted on bearings in end cap hub, rotor plates, inlet and outlet pipes of the first and second compression stages, an intermediate cooler, has a rotor consisting of a polyhedron-shaped shell and an end wall connected to the drive shaft, hinges are installed on the outer and inner surfaces of the rotor shell wall, with with which the rotor plates are connected by one edge with the possibility of their rotation around the hinge axes, springs are installed between the rotor plates and the wall of the rotor shell, the cylindrical body of the second compression stage is located eccentrically inside the rotor, has inlet windows and is rigidly connected by one of its end edges to the end cover, and on the other end side it is closed with a blank wall; the inlet and outlet pipes of the second compression stage are installed on the end cover.

The set of distinctive features makes it possible to simplify the design and increase the reliability of the two-stage rotary vane supercharger in relation to the prototype [5]. The design of the rotor from a shell in the shape of a polyhedron and an end wall connected to the drive shaft helps to reduce the specific material consumption of the supercharger. The presence of hinges on the outer and inner surfaces of the rotor shell wall, to which the rotor plates are connected by one edge with the possibility of their rotation around the hinge axes, placement of springs between the rotor plates and the rotor shell wall, eliminates the risk of pinching the plates and reduces their wear. The eccentric arrangement inside the rotor of the cylindrical housing of the second compression stage, which has inlet windows and is rigidly connected by one of its end edges to the end cover, and on the other end side is closed by a blank wall, the placement of the inlet and outlet pipes of the second compression stage on the end cover ensures high compactness of the device, simplifies its design and helps reduce specific material consumption.

Thus, the set of distinctive features of the invention allows us to solve the problem posed.

A comparative analysis of the claimed technical solution with the prototype shows that the claimed device meets the invention criterion of “novelty”.

Known single-stage devices [2, 3, 4], operating on the same principle of operation, create a lower pressure, are structurally more complex, less efficient and reliable in operation.

All this allows us to conclude that the proposed technical solution meets the invention criterion of “significant differences”.

In fig. 1 is a schematic cross-section of the proposed two-stage rotary vane blower; in fig. 2 - section A-A in Fig. 1.

A two-stage rotary vane supercharger contains a cylindrical housing 1 of the first compression stage with 2 inlet and 3 outlet windows. Connected to the cylindrical body 1 are the inlet 4 and outlet 5 pipes of the first compression stage, the end cover 6 with the inlet 7 and outlet 8 pipes of the second compression stage installed on it, and the flanged end cover 9 with the hub 10. Inside the cylindrical body 1 of the first compression stage, eccentrically with there is a rotor 11, consisting of a shell 12 having the shape of a polyhedron, and an end wall 13 connected to a drive shaft 14, which is mounted on bearings 15 in the hub 10. On the outer and inner surfaces of the wall of the shell 12 of the rotor 11, hinges 16 are installed. hinges 16 are connected by one edge of the plate 17 of the rotor 11, having the ability to rotate around the axes of the hinges 16. Springs 18 are installed between the plates 17 and the wall of the shell 12. Inside the rotor 11, eccentrically with it, there is a cylindrical housing 19 of the second compression stage, having inlet windows 20 The cylindrical housing 19 of the second compression stage is rigidly connected at one end edge to the end cover 6, and at the other end it is closed by a blank wall 21. In the dissection of the channel 22 for the moved medium connecting the outlet pipe 5 of the first compression stage and the inlet pipe 7 of the second compression stage. Intermediate refrigerator 23 is installed.

A two-stage rotary vane blower operates as follows.

The moved compressed gas enters through the inlet pipe 4 of the first compression stage and the inlet windows 2 into the internal space of the cylindrical housing 1 of the first compression stage, limited by the end cover 6, the flanged end cover 9, the shell 12 of the rotor 11, the outer plates 17 of the rotor 11, which are in a state with the largest angle of rotation around the axes of the hinges 16 under the action of external springs 18. When the drive shaft 14, mounted on bearings 15 in the hub 10 and connected to the end wall 13, and with it the rotor 11 rotates clockwise (see Fig. 1), with a decrease in the angle of rotation of the plates 17, the volume between the plates decreases and the transported gas is compressed. In the state of the outer plates 17 with the smallest angle of rotation around the axes of the hinges 16, the transported gas is compressed to the pressure of the first compression stage and passes through the outlet windows 3 into the outlet pipe 5, from where it enters the intermediate cooler 23 through the attached channel 22. The gas cooled in the intermediate cooler 23 is directed through the inlet pipe 7 into the internal space of the rotor 11, limited by its shell 12, end wall 13, end cover 6, cylindrical body 19 of the second compression stage and internal plates 17, which are in a state with the greatest angle of rotation around the axes of the hinges 16 under the action of internal springs 18 When rotor 11 rotates, the angle of rotation of the internal plates 17 changes and at the same time the volumes of gas contained between adjacent plates 17 and the gas pressure in these volumes change. In the state of the internal plates 17 with the smallest angle of rotation, the transported gas acquires the pressure of the second compression stage, passes through the inlet windows 20 into the space of the cylindrical housing 19 of the second compression stage with a blank wall 21, from where it is discharged from the device through the outlet pipe 8.

Tight abutment of the edges of the outer and inner plates 17 to the cylindrical housings 1 and 19 when the rotor 11 rotates and the angles of rotation of the plates 17 change is ensured by the action of springs 18, the rigidity of which increases with decreasing angles of rotation of the plates and vice versa - decreases with increasing angles. Changing the stiffness of the springs 18 in the range from its maximum value to its minimum at each half revolution of the rotating rotor 11 and, accordingly, the pressing force of the plates against the cylindrical bodies 1 and 19 helps to reduce wear of the plates 17 and effectively compress the moved gas to the required pressure. Reduces wear of the plates 17 and the presence of thin films of transported gas formed during the operation of the device between the edges of the plates and the surfaces of the walls of the cylindrical housings 1 and 19. These films serve as a kind of lubricant and reduce energy costs to overcome friction forces. Operation of the supercharger is possible with a high rotation speed of the rotor 11 without pinching the plates 17 and their active wear.

In order to bring the gas compression process closer to isothermal, cylindrical housings 1 and 19 can be equipped with water jackets.

The proposed two-stage rotary vane supercharger has the following advantages over similar devices:

- simple design;

- manufacturability and ease of maintenance;

- lower specific material consumption during manufacturing and energy consumption during operation;

- increased efficiency and reliability;

- low noise during operation;

- high efficiency;

- reduced wear of rubbing elements.

INFORMATION SOURCES

1. Kalinushkin M.P. Hydraulic machines and refrigeration units. M.: Higher School, 1973. P. 102 (Fig. V-2, V-3), p. 107 (Fig. V15).

2. Abdurashitov S.A., Tupenchenkov A.A., Vershinin I.M., Tenengolts S.M. Pumps and compressors. M.: Nedra, 1974. P. 269 (Fig. 12. 4).

3. Eurasian patent No. 005220, IPC F04C 18/344. Publ. 2004.12.30.

4. Kasyanov V.M. Hydraulic machines and compressors. M.: Nedra, 1979. P. 202 (Fig. 32.1).

5. Cherkassky V.M. Pumps, fans, compressors. M.: Energy, 1977. P. 383 (Fig. 14-4).

Claims (1)

A two-stage rotary vane supercharger containing cylindrical casings of the first and second compression stages with windows on the wall, end covers of the cylindrical casing of the first compression stage, a rotor with a drive shaft eccentrically located inside the cylindrical casing of the first compression stage, which is mounted on bearings in the hub of the end cap, rotor plates , inlet and outlet pipes of the first and second compression stages, an intermediate cooler, characterized in that the rotor consists of a shell in the shape of a polyhedron and an end wall connected to the drive shaft; hinges are installed on the outer and inner surfaces of the wall of the rotor shell, with which one of its edges the rotor plates are connected with the possibility of their rotation around the hinge axes, springs are installed between the rotor plates and the wall of the rotor shell, the cylindrical body of the second compression stage is located eccentrically inside the rotor, has inlet windows and is rigidly connected at one end edge to the end cover, and at the other end closed with a blank wall, the inlet and outlet pipes of the second compression stage are installed on the end cover.

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