RU2783056C1 - Centrifugal freon compressor - Google Patents

Abstract

FIELD: refrigerating.

SUBSTANCE: invention can be used as a compressor of freon liquid media cooling systems, on-board equipment of helicopters, planes, aerial vehicles, and land-based vehicles subjected to multidirectional vibration loads, configured for work with gas, two-phase gas media, in the liquid pump mode, work in freon-filled systems for air conditioning and industrial and domestic refrigeration units. Centrifugal freon compressor comprises a tightly sealed body; two compressor stages with impellers, diffusers, prefabricated chambers, an inlet branch pipe to the first compressor stage, and an outlet branch pipe from the second compressor stage; a high-frequency electric engine placed between the compressor stages, with the rotor made on the same shaft as the impellers of the compressor stages; support assemblies at the ends of the shaft, preferably, with ceramic roller bearings, with ceramic balls perceiving the radial and axial load of the compressor shaft and the multidirectional vibration load at the installation site of the centrifugal freon compressor, secured in the body and cover of the compressor. The first stage of the compressor is made as a drag compressor and acts as a vacuum pump with a subsequent increase in the pressure before the second stage of the compressor with a centrifugal impeller. In order to ensure the maximum performance coefficient of the compressor stages when pumping media with different densities and during operation in the liquid pump mode, an electric engine with an adjustable speed is used. The body of the centrifugal freon compressor is composed of two parts, wherein an inlet branch pipe is located on one of the parts, and an outlet branch pipe is located on the other part, with a gasket sealing the gap between said parts, while all parts of the centrifugal freon compressor are arranged on the shaft in the increasing order of the diametrical overall dimensions.

EFFECT: creation of a new centrifugal freon compressor.

1 cl, 1 dwg

Description

The invention relates to the field of compressor engineering to refrigerant centrifugal low-flow compressors, and in particular to two-stage centrifugal compressors with a built-in high-speed electric drive without lubrication in the compressor rotor bearings and is intended for use in cooling systems for liquid media, on-board equipment of helicopters, aircraft, and ground wheeled and tracked vehicles means in which there are multidirectional vibration loads, with the ability to work with two-phase media, in liquid pump mode, with the possibility of using in systems filled with freon, air conditioning and refrigeration units for industrial and domestic purposes.

A two-stage centrifugal compressor is known with an electric motor built between the cantilever stages, having a housing consisting of an electric motor housing and attached to it on each side through intermediate flanges of the housings of one and the other stage, and the rotor is the same for the stages and the electric motor, installed in located between the stages and an electric motor of supporting and thrust magnetic bearings having stator and rotor elements, and inside the housing, the stator elements of the supporting and thrust magnetic bearings are made in the form of blocks installed in additional housings, each of which is fixed on the intermediate flange with its inner side facing the stage, moreover on the side of one stage, stator elements of the support magnetic bearing are installed in the additional housing, and on the side of the other stage, stator elements of the support and thrust magnetic bearings are installed (RF patent for PM No. 36709, F04D 25/06, publ. 20.03.2004).

The disadvantage of this design is the high cost and the need to use a special control system for electromagnetic bearings, as well as a special cooling system for the electric motor.

A two-stage centrifugal compressor is also known, comprising a housing with inlet and outlet pipes, suction and motor chambers, discharge chambers with diffusers, supporting baffles with gas-dynamic bearings and an electric motor stator integrated into the housing between the supporting baffles, located in the housing sleeve having peripheral grooves, placed in gas-dynamic bearings, the compressor rotor with the impellers of the first and second stages mounted on it and the rotor of the electric motor, which is installed with a gap relative to the stator, characterized in that the support partitions are provided with holes connecting the diffuser of the first stage discharge chamber and the second stage suction chamber with the motor chamber. (Description for utility model RU 143266 U1, IPC F04D 25/06 (2006.01), published on 20.07.2014, Bull. No. 20).

However, the disadvantage of this design is the high cost and the need to use a special pressurization system for gas-dynamic bearings. In addition, there are problems with the use of gas dynamic bearings due to their bearing capacity, which limits the permissible mass of the rotor.

It is also known a device for dynamic gas compression, containing a fixed housing with mechanical and radial labyrinth seals, inlet guide vanes of a diagonal compression stage, a bladed impeller of a diagonal stage of preliminary centrifugal-axial compression, outlet guide vanes of a diagonal compression stage, a main axial compression stage, outlet guides blades of the axial compression stage, the drive of the diagonal and axial compression stages, which is made with additional volumetric compression of the gas and represents a rotor with longitudinal spiral-helicoid channels in the amount of 6 to 24 pieces, located circumferentially around a common axis, simultaneously initially twisted by 2.6 ...4.2 turns along the entire length around the hyperbolic surface, and each of the spiral compression channels in cross section has the shape of a helicoid with a ratio of minor and major axes of 0.47 ... of the helicoid, and the inner smooth protrusion is secondarily twisted around the longitudinal axis of the helicoid with a step of 0.4 ... from 3 to 6 small smooth protrusions of the tertiary twist, twisted around the longitudinal axis of the helicoid with a step of 0.2 ... around a common axis is opposite to the direction of the primary swirl of each of the helicoids, and the cross-sectional area of the helicoid in the first section of the helicoid swirl along the hyperbolic surface is reduced to 0.3 ... major axes and maintaining the proportions of the internal main and additional smooth protrusions and the directions of their twist with a gradual increase in the pitch of the primary winding of the helicoids by 1.5 times and with a further decrease in the second section of the helicoid twist along the hyperbolic surface of the helicoid cross-sectional area to 0.15 ... 0.3 of the initial cross-sectional area of the helicoid with a smooth increase in the twist pitch by 3 ... 4 times, the diagonal and axial stages have separate drives with different speeds, (description of the utility model RU 163651 U1, IPC F04D 17/06 (2006.01) published on 27.07.2016, Bull. No. 21).

However, the known device for dynamic gas compression has the following disadvantages: the complexity of the design, the complexity of manufacturing a helicoid with projections, the complexity of balancing the bladed impeller of the diagonal stage of preliminary centrifugal-axial compression, located on the same axis as the rotor, on which longitudinal spiral-helicoid channels are located, the complexity of separate drives with different speeds, high cost and the need to use a special drive motor control system.

Of the known technical solutions, the closest in technical essence to the claimed object is the description of the patent "Centrifugal turbocompressor unit and electric motor" RU 2150609 C1, IPC F04D 17/12, H02K 21/12 according to application 99103171/06, 18.02.1999.

Turbocharger, which includes a sealed container with an internal cavity and separate inlets on both sides, the first bearing seat and the second bearing seat installed on the left and right sides inside the inner cavity of the sealed container at a certain interval and contain through holes in the central part. The drive motor is installed between the first and second bearing seats. The drive shaft, both ends of which are individually passed through the through holes of the first and second bearing seats, is combined with the drive motor. The sealing element inserted by means of the drive shaft is fixedly connected to the first bearing seat. The radial support means is separately inserted between the drive shaft and the first bearing seat and between the drive shaft and the second bearing seat. The first impeller is fixedly connected to the end of the drive shaft. The second impeller is fixedly connected to the other end of the drive shaft. The first diffuser element is fixedly connected to the sealing element by placing the first impeller along the outer circumference. The second diffuser element is fixedly connected to the second bearing seat by placing the second impeller along the outer circumference.

The disadvantage of this centrifugal turbocompressor unit is that the bearing assemblies are located between the impellers of the compressor stages and the rotor of the electric motor, which is cooled by freon, and they are gas-dynamic, it is necessary to provide a certain gas flow for each bearing assembly, which predetermines the constancy of the rotation of the electric motor and a narrow control range performance.

Since the petal gas-dynamic bearings cannot provide the bearing capacity in two mutually perpendicular directions, it is necessary to install a thrust gas-dynamic bearing on a cardan suspension.

The presence of a cardan suspension complicates the design and leads to an increase in the weight of the compressor.

The thrust bearing comb prevents the passage of freon to cool the stator and rotor of the electric motor, as a result of which the hydraulic resistance of the freon passage path increases, it becomes necessary to connect the collection chamber of the first stage with the inlet of the second stage through a separate pipeline, the thrust comb itself has significant restrictions on the size and diameter of the disk.

The location of the impellers of the compressor stages at the ends of the shaft and the direction of suction from the outer end side of the compressor, as well as the location of the load-bearing gas-dynamic bearings and the presence of a thrust bearing increase the overall length of the shaft and the overall length of the centrifugal compressor and require good balancing of the shaft with the impellers and thrust comb.

The bearing capacity of gas-dynamic bearings and the system of gas supply channels requires a complex calculation, and, depending on the properties of the refrigerant used, it may vary.

These bearings cannot operate on “wet” refrigerant or when a liquid refrigerant phase appears. Inevitable water hammer can crush the petals of gas dynamic bearings. To prevent this phenomenon, it is necessary to have a separate effective dehumidifier system.

When such a turbocompressor unit is installed on a helicopter, aircraft and ground vehicle, where multidirectional vibration loads are present, these gas dynamic bearings lose their bearing capacity.

The use of gas dynamic bearings requires a high-speed electric motor whose speed may not match the speed range of the compressor impeller in order to achieve high efficiency.

To achieve high efficiency, different speeds of rotation of the impellers of the same constructive device are required.

Since the discharge zones of the first stage of the compressor and the second stage of the compressor are connected through the gap of gas-dynamic bearings, in order to prevent overflow or ensure a minimum overflow of refrigerant, labyrinth seals are provided, made at the end sections of the shaft and sealing the working cavities of the compressor stages, which complicates the design and increases the cost of manufacturing turbocharger parts. unit.

The gaps cannot be kept to a minimum due to the movement of the shaft when starting and stopping. Consequently, the efficiency of labyrinth seals will be low, which will lead to the overflow of freon, a decrease in discharge pressure and energy efficiency of the compressor stages.

The disadvantage is also the communication of the collection chamber of the first compressor stage with the inlet of the second stage through a separate pipeline, which leads to additional hydraulic losses, complicates the design and reduces reliability due to loss of tightness due to thermal expansion of the compressor parts, increases the cost of manufacture.

For example: the range of change in freon density is very large and the maximum value can exceed the minimum value by tens of times, depending on the shaft speed and pressure, which entails the need to perform a complex calculation and, depending on the speed of the electric motor, calculate the dimensions and performance of the impellers. In this case, the first compressor stage must have good suction characteristics, and the second compressor stage works with a backwater and has a higher efficiency. With the same diametrical dimensions of the impellers, in order to achieve the highest efficiency, the speed of the first stage impeller may not coincide with the speed range of the second stage impeller due to the difference in mass flow rates.

As a result, the compressor shaft speed must be constant or change slightly. Centrifugal impellers are very small due to the presence of gas dynamic bearings and high rotation speed and therefore low efficiency, resulting in the need to increase the compressor shaft speed even more to increase the pressure and flow rate of the compressor. An increase in the speed and power of the electric motor leads to an increase in the length of the rotor, stator and the overall length of the compressor.

This is due to the fact that at low capacities, due to small geometric dimensions, the negative effect of the scale factor and high conditional Mach numbers on the gas-dynamic characteristics of centrifugal stages is most pronounced. In addition, due to the high required rotor speed in the refrigerant (freon) medium, friction losses (ventilation losses) increase significantly.

Due to losses, the energy efficiency of a centrifugal compressor decreases in the region of low cooling capacities up to 100 kW.

In view of the foregoing, the purpose of the invention is to expand the functionality of using a centrifugal freon compressor for compressing freons, gases, wet gases and freons, multi-phase gas environments, as well as for supplying liquids, with a low speed, with a high efficiency, with the ability to work , where there are versatile vibration loads on the centrifugal refrigerant compressor itself.

EFFECT: possibility of efficient operation of a centrifugal freon compressor with wet multi-phase gaseous media, with liquids, reduction of energy costs due to high efficiency of compressor stages at a low identical, constant rotor speed, reduction in weight and size characteristics due to simplification of the design of the rotor supports and increase in the life of the compressor under the influence of versatile vibration loads on the centrifugal freon compressor itself, the creation of a centrifugal freon compressor having a simple manufacturable design in manufacture and assembly, providing low manufacturing cost and low operating costs.

This technical result is achieved by the fact that a centrifugal refrigerant compressor containing a hermetically sealed housing, two compressor stages with impellers, diffusers, collection chambers, an inlet pipe to the first compressor stage and an outlet pipe from the second compressor stage, a high-frequency electric motor located between the compressor stages, the rotor of which is made on the same shaft with the impellers of the compressor stages, the shaft support units fixed to the unit housing and seals sealing the working cavities of the compressor stages, while for cooling the drive motor there is a working gap between the rotor and the stator, and flow cooling channels on the outside stator, wherein the rotor is formed by at least one permanent magnet with a bandage of a material that prevents the flow of eddy currents, and the stator is made in the form of a laminated magnetic circuit with a winding, characterized in that at the same speed in as a compressor of the first stage, a vortex compressor is used as a vacuum pump and as a compressor to increase the pressure in front of the impeller of the second centrifugal stage of the compressor; perceive radial and axial load during shaft rotation and multidirectional vibration load at the installation site of the compressor impellers, and which are not blown through by the working fluid (freon), for which the first stage rolling bearing is installed in front of the first stage impeller, and the second stage bearing is installed after the impeller of the second stage of the centrifugal freon compressor, while the centrifugal freon compressor housing is made of only two parts, on one of which there is an inlet pipe, and on the second outlet pipe, the gap between which is sealed by a gasket, and all parts are centered of the refrigerant compressor are located on the shaft in a sequence of increasing diametrical overall dimensions.

In a two-stage centrifugal freon compressor, containing a housing with inlet and outlet pipes, suction and motor chambers, discharge chambers with diffusers, support baffles with gas-dynamic bearings and an electric motor stator integrated into the housing between the support baffles, located in the housing sleeve having peripheral grooves, located in gas-dynamic bearings, the compressor rotor with the impellers of the first and second stages mounted on it and the rotor of the electric motor, which is installed with a gap relative to the stator, the support partitions are provided with holes connecting the diffuser of the first stage discharge chamber and the second stage suction chamber with the motor chamber, the shaft placed in the bearing supports with the rotor of the compressor electric motor with installed impellers of the first and second stages, while the pressure part of the first stage compressor through the gaps between the rotor, stator and compressor housing connects with a chamber in front of the second stage of the compressor, characterized in that the rotational speed of the compressor rotor and shaft is reduced, bearing units with gas-dynamic bearings are replaced with rolling bearings with ceramic balls that perceive axial and radial loads, as a result of which there is no need to use a thrust bearing and it becomes possible to use a compressor on helicopters, airplanes and ground vehicles.

The use of support-thrust, preferably ceramic, rolling bearings with ceramic balls that perceive radial and axial loads during shaft rotation and multidirectional vibrational loads at the installation site of a centrifugal freon compressor, which is especially important for helicopters, aircraft and ground wheeled and tracked vehicles moving over rough terrain. Bearing supports are less prone to clogging, since they are not blown through by the working fluid (freon). To do this, the first stage rolling bearing is installed in front of the first stage impeller, and the second stage bearing is installed after the second stage impeller of the centrifugal compressor, which improves the reliability of this unit and the entire compressor as a whole.

Since the overall efficiency of the compressor is determined only by the efficiency of the stages, the compressor stages at the same rotor shaft speed should have the maximum efficiency. In this case, the first stage must have good suction parameters, since freon gas or gas at low temperature has a low pressure. Due to the fact that the dimensions of the impeller of the second stage of the centrifugal compressor, installed inside the sealed housing, are small and, accordingly, the area of the suction inlet is small, for efficient operation it is necessary to create pressure in front of the centrifugal compressor impeller.

Based on this, a vortex compressor is used as the first stage compressor, which acts as a vacuum pump and is simultaneously used to increase the pressure before the second centrifugal stage of the compressor.

The main advantages of vortex compressors are: high head pressure, simple design, low manufacturing cost, as well as higher reliability compared to centrifugal and rotary compressors with the same parameters. The characteristics of a vortex compressor are practically stable over the entire range of modes at different rotation speeds. In the stage of a vortex compressor, at equal circumferential speeds, several times more pressure can be obtained than, for example, in a stage of a centrifugal compressor. In this regard, it is advisable to connect the vortex stage directly to the motor shaft without using a multiplier. The monobloc construction scheme is most typical for vortex compressors. The use of such a scheme reduces the weight and size indicators, the cost of the compressor, simplifies the choice of supports and, if necessary, sealing the compressor.

To reduce the mass of a centrifugal freon compressor, the parts of the casing of the vortex compressor of the first stage, which form zones of low suction pressure and high discharge pressure, can be made of non-metallic materials, such as plastics and plastics, which is especially important when pumping aggressive gas and liquid media.

All parts of the centrifugal freon compressor are arranged in sequence of increasing overall diametrical dimensions, which allows, to simplify the design, increase reliability, by reducing the leakage of freon (working fluid), and to reduce the weight of the centrifugal freon compressor, the housing is made of only two parts: housing with an outlet pipe containing a centrifugal compressor of the second stage with a drive electric motor and a cover of the first stage compressor with an inlet pipe, into which parts of the first stage vortex compressor housing are inserted, while the gap between the housing and the cover is additionally sealed with a gasket. This makes it possible to simplify the design and assembly of the compressor, reduce the cost of manufacturing and ensure high reliability, by reducing the likelihood of freon (working fluid) leakage through the joints of the compressor parts,

The invention is illustrated by the accompanying drawing, where in Fig. 1 - design of a centrifugal freon compressor.

According to the drawing, the centrifugal freon compressor includes the following elements:

- housing of the drive motor 1;

- the cover of the compressor of the first stage 2;

- low pressure inlet 3

- housing of the vortex compressor of the first stage at suction 4;

- low pressure chamber of the compressor of the first stage 5;

- housing of the vortex compressor of the first stage at the discharge 6;

- the impeller of the vortex compressor 7;

- separator blades 8;

- pressure chamber of the first stage 9

- chamber in front of the compressor of the second stage 10

- inlet diffuser of the impeller of the second stage 11;

- impeller of the second stage of the centrifugal compressor 12;

- diffuser blades of the centrifugal compressor of the second stage 13;

- discharge chamber of the centrifugal compressor of the second stage 14;

- high pressure outlet pipe 15;

- shaft 16;

- electric motor rotor 17;

- motor stator 18;

- windings of the stator of the electric motor 19;

- bearing unit in the cover of the compressor of the first stage 20;

- bearing assembly in the housing of the drive motor 21;

- pressurized input of contacts of stator windings 22;

- gasket 23;

I - the first stage of the centrifugal freon compressor;

II - the second stage of the centrifugal freon compressor.

The proposed centrifugal refrigerant compressor (Fig. 1) is made in the form of two stages with a drive motor between them, located in the same housing of the drive motor 1.

The first stage of the centrifugal freon compressor I is made in the form of a single-stage vortex compressor, which contains: the cover of the first stage compressor 2, the low pressure inlet pipe 3, the housing of the vortex compressor of the first stage on suction 4, the housing of the vortex compressor of the first stage on the discharge 6, the impeller of the vortex compressor 7, while the annular recess on the housing of the first stage vortex compressor at suction 4, together with the cover of the first stage compressor 2, forms a low pressure chamber of the first stage compressor 5, and the separator blades 8 on the housing of the first stage vortex compressor at suction 4 and discharge 6 separate the cavity suction connected to the low-pressure chamber of the first stage compressor 5 and the discharge cavity of the first stage discharge chamber 9 connected by an opening in the housing of the first stage vortex compressor at the discharge 6.

The second stage II of the centrifugal freon compressor is made in the form of a single-stage centrifugal compressor, which contains: an inlet diffuser of the second stage impeller 11, a drive motor housing 1 with a high pressure outlet pipe 15, an impeller of the second stage of the centrifugal compressor 12, diffuser blades of the centrifugal compressor of the second stage 13 after which the discharge chamber of the centrifugal compressor of the second stage located in a circle 14.

To reduce the mass of the centrifugal freon compressor, the housing of the first stage vortex compressor at suction 4, the housing of the first stage vortex compressor at discharge 6 and the inlet diffuser of the second stage impeller 11 are made of plastic.

All parts of the centrifugal freon compressor are located on the shaft 16 in the sequence of increasing overall diametrical dimensions of the parts, which allows the case of the centrifugal freon compressor to be made of only two parts: the drive motor housing 1 and the cover of the first stage compressor 2, the gap between which is additionally sealed by the gasket 23.

The housing of the drive motor 1 contains: a sealed lead-in of the contacts of the stator windings 22, the stator of the electric motor 18 with the stator windings of the electric motor 19.

The casing flange of the drive motor 1 is docked with the cover flange of the first stage compressor 2 through a gasket 23 for tightness, while the inlet diffuser of the second stage impeller 11 forms a chamber in front of the second stage compressor 10 and the discharge chamber of the second stage centrifugal compressor 14 together with the casing of the drive motor 1.

The impeller of the vortex compressor 7 and the impeller of the second stage of the centrifugal compressor 12, the rotor of the electric motor 17 are located on the shaft 16, which at the ends has a bearing assembly in the cover of the first stage compressor 20 and a bearing assembly in the housing of the drive motor 21 with ceramic rolling bearings and ceramic balls.

The operation of the compressor is carried out as follows.

Freon (working fluid) is first compressed in stage I of the centrifugal freon compressor, for which it is first sucked in and enters through the low pressure inlet pipe 3 into the low pressure chamber of the first stage compressor 5. After the compression process, when the impeller of the vortex compressor 7 rotates between the vortex compressor housing compressor of the first stage at suction 4 and the housing of the vortex compressor of the first stage at the discharge 6, while the separator blades 8 located on the housing of the vortex compressor of the first stage at the suction 4 and discharge 6 separate the suction zone from the discharge zone.

When the blades of the impeller 7 rotate, the freon enters the peripheral-side channel of the first-stage vortex compressor housing at suction 4 and at the discharge 6, where it acquires a spiral character due to the periodic transfer of energy from the blades, and then, being decelerated by the separator blades 8, it is directed through the channel into housing of the vortex compressor of the first stage at the discharge 6 further into the discharge chamber of the first stage 9. In this case, a small part of the refrigerant flows from the peripheral-side channels of the housings 4 and 6 of the discharge zone in front of the blades of the separator 8 into the area of reduced pressure, i.e. into the suction area.

From the injection zone, freon through an opening in the housing of the vortex compressor of the first stage at discharge 6 is fed into the discharge chamber of the first stage 9 and further into the gap between the rotor of the electric motor 17 and the stator of the electric motor 18. Flowing through the gap and removing excess heat from the rotor 17 and stator 18 of the electric motor, freon flows further into the chamber before the compressor of the second stage 10.

Further compression of freon occurs in the second stage compressor, which is formed by the inlet diffuser of the second stage impeller 11 and the impeller of the centrifugal compressor 12 mounted on the shaft 16, during the rotation of which the compression process occurs. Freon from the chamber in front of the compressor of the second stage 10 through the inlet diffuser of the impeller of the second stage 11 enters the blades of the impeller of the centrifugal compressor 12, from which it receives additional kinetic energy and in which it is compressed and enters the diffuser blades of the compressor of the second stage 13, where it is braked and the conversion of the kinetic energy of the flow into the potential energy of pressure, and leaving the diffuser blades, the freon enters the discharge chamber of the centrifugal compressor of the second stage 14. Through the outlet pipe 15, the freon with high pressure leaves the compressor housing 1.

In view of the foregoing, we can conclude that the goal is realizable, and the technical result is achievable.

The centrifugal freon compressors according to the present invention can suitably be used in refrigeration applications. More specifically for use in avionics cooling systems of helicopters, aircraft and ground vehicles that have multi-directional vibration loads, with the ability to work with two-phase media, in liquid pump mode, with the possibility of use in halon-filled systems for cooling air , liquid media, in air conditioning systems and refrigeration plants for industrial and domestic purposes.

Claims (1)

Centrifugal refrigerant compressor containing a hermetically sealed housing, two compressor stages with impellers, diffusers, collection chambers, an inlet pipe to the first compressor stage and an outlet pipe from the second compressor stage, a high-frequency electric motor located between the compressor stages, the rotor of which is made on the same shaft with compressor stages impellers, shaft support units fixed in the unit housing and seals sealing the working cavities of the compressor stages, while for cooling the drive motor there is a working gap between the rotor and the stator, and flow cooling channels on the outside of the stator, while the rotor is formed along at least one permanent magnet with a bandage made of a material that prevents the flow of eddy currents, and the stator is made in the form of a laminated magnetic circuit with a winding, characterized in that at the same speed, an eddy current is used as the first stage compressor roar compressor as a vacuum pump and as a compressor for increasing pressure in front of the impeller of the second centrifugal stage of the compressor, in the support bearing units at the ends of the shaft with the impellers, support-thrust, preferably ceramic, rolling bearings with ceramic balls are used, which perceive the radial and axial load at shaft rotation and multidirectional vibration load at the installation site of the compressor impellers, and which are not blown through by the working fluid (freon), for which the first stage rolling bearing is installed in front of the first stage impeller, and the second stage bearing is installed after the second stage impeller of the centrifugal freon compressor, at the same time, the housing of the centrifugal freon compressor is made of only two parts, on one of which there is an inlet pipe, and on the second outlet pipe, the gap between which is sealed by a gasket, and all parts of the centrifugal freon compressor are located on the shaft in sequence of increasing diametrical overall dimensions.

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