Centrifugal compressing device

FIELD: non-positive-displacement pumps.

SUBSTANCE: centrifugal compressing device comprises engine (50) that set rotor (52) in rotation and at least one compressor that has housing of the stator and a set of wheels provided with blades (56) mounted on the driven shaft that is set in rotation inside the housing of the stator. The motor is mounted in pressure-tight crank case (86). The compressing device additionally has a set of active guiding axial and radial bearings (60), (62), (64), (66), and (67) of the rotor and driven shaft and means for cooling engine and guiding bearings by means of sucking gas supplied by the compressor at the outlet of the first compression stage. The cooling means have a set of inner pipelines (80-1), (80-2), (80-3), (80-4), (80-5) and (80-6) that supply cooling gas to the engine and bearings. The flow rate of the cooling gas supplied to the engine differs from that of the cooling gas supplied to the bearings and flow together upstream of the first compression stage .

EFFECT: enhanced reliability.

 

The invention relates to a centrifugal compressor Assembly.

In particular, the invention relates to a centrifugal compressor unit integrated type, i.e. the type in which the compressor and the drive motor of the compressor are installed in a common gas-tight crankcase driven compressor.

According to figure 1, the standard integrated pump unit includes a motor, typically representing a driving electric motor, with a General numerical designation 10, a centrifugal compressor 12 having, for example, multiple stages of compression, the entire Assembly is mounted in a common gas-tight crankcase driven compressor.

As can be seen from figure 1, the engine 10 causes the rotation of the rotor 16, which in turn causes the driven shaft 18 on which is mounted the wheel with vanes to provide compression 20,22, 24 and 26.

According to the example of the compressor Assembly shown in figure 1, the compressor has four stages of compression, which together provide compression of the gas sucked through the supply line 28, to supply at the output 30 after passing through the snail 32.

The rotor 16 and the driven shaft 18 connected through a flexible coupling 34. In this case, as the rotor 16 and the driven shaft 18 are guided in radial bearings 36, 38, 40 and 42. The aperture 44, the implementation is hydrated in the crankcase 14, closed by a plug 46 provides access to a flexible coupling 34 for mounting the compressor.

Figure 1 shows that the axial stop 48 limits the axial displacement of the driven shaft 18, while balancing piston 49 makes it possible to align the axial pressure is transmitted to driven shaft during operation of the compressor unit.

Implementation compressor unit in engine and compressor located in a common sealed crankcase pressure, eliminates the use of the seals of the compressor, which are elements that can compromise the reliability of the compressor Assembly and to be a source of leakage of gas into the atmosphere. In this case, the engine is located in the environment of gas supplied by a compressor. In order to avoid a significant increase of the mechanical losses in the motor due to ventilation, the engine is designed so that it is under suction pressure of the compressor. It is also necessary to provide for the circulation of gas in the engine exhaust losses, i.e. in the stator to prevent losses due to the Joule heat release in the coils and in the air gap between the rotor and stator, to avoid losses due to ventilation and losses due to induce eddy currents in the rotor.

Therefore, the centrifugal compressor units, as a rule, are equipped with the tools and engine cooling and guide bearings by taking gas at the outlet of the first compression stage for cooling the motor and bearings. In this regard, please refer to the patents EP-a - 1 069 313 and US 6,390,789, which describes the various types of compressors, in which the cooling of the motor and bearings carried by selection of the cooling gas at the outlet of the first stage of compression.

However, such cooling methods have a number of disadvantages, in particular, due to the fact that they do not provide optimum cooling of the motor and bearings.

Object of the invention is the partial elimination of this disadvantage and the development of a Central unit with improved cooling means.

Thus, the invention has the task to provide a centrifugal compressor unit of the type which includes a rotary drive motor, a rotor and at least a compressor having a stator housing and a system of wheels with blades mounted on driven in rotational movement of the driven shaft rotor and the stator housing, the system includes a motor and compressor are placed in a common gas-tight crankcase in the environment of gas supplied by a compressor, or compressor unit provides for a system of active guides axial and radial bearing of the rotor and the driven shaft, means for cooling the motor and the guide bearings by taking gas fed compressor the output of the first stage of compression, circulation above gas through the engine and through the bearings and back to the inlet of the gas at the inlet of the compressor.

In accordance with the General characteristic of this centrifugal compressor unit, means for cooling the system of internal pipelines supply the cooling gas to the motor and bearings; the flow rate of the cooling gas in the engine differs from the flow of the cooling gas in the bearings, both consumption converge before the first stage of compression.

It was found that such an arrangement can significantly improve the cooling inside the compressor unit. Essentially, it was found that the size of the air gap in the magnetic bearings relative to the size of the air gap in the motor has a negative effect on cooling when using the same flow rate for cooling the bearings and the motor and prevents the proper circulation of the cooling gas. Essentially in the engine are more significant losses than in the bearings, so it requires greater consumption. In addition, the temperature of the cooling gas at the outlet of the engine has a negative effect on cooling the bearings when using the flow rate of the cooling gas at the outlet of the engine for cooling the bearings.

According to another characteristic of the invention, the medium is air cooling, in addition, there are external channels for receiving gas at the outlet of the first compression stage and for supplying gas to the internal piping in parallel.

According to another method of implementation, the internal supply pipe of the cooling gas to the engine is laid in parallel with the internal supply pipe of the cooling gas to the bearings.

Preferably the cooling means are filtering gas supplied by a compressor.

According to another characteristic of the compressor unit according to the invention, the driven shaft of the compressor rests with its ends on two radial bearing, cooling means have axial pipeline, which runs from one bearing to the other bearing, and in which one of these ends of the gas is fed through the outer pipes; the above axial pipeline passes in the longitudinal direction on the outer side of the compressor.

For example, the inner feed lines to the bearings have a set of pipes, rotated in the outer radial direction from the compressor, and provide the gas flow to each bearing.

According to another characteristic of the invention, the cooling gas is fed into the engine through the hole provided in the end cap and connected with the outer pipe.

The cooling ha is or may be mixed with a flow rate of the cooling gas at the outlet of the cooled bearings due to mixing with the gas outlet of the internal pipelines.

For example, the compressor unit has means controlling the flow supplied to the cooling, on the one hand, of the engine and, on the other hand, each of the bearing.

According to another characteristic of the invention, the compressor unit has means for collecting refrigerant gas flow coming from the mechanisms located on the side of the balancing piston.

Other aims, characteristics and advantages of the invention will be apparent from the following description which is given solely as a non-limiting example with reference to the drawings, in which:

figure 1 depicts the General design standard integrated compressor Assembly;

figure 2 - block diagram of the centrifugal compressor Assembly in accordance with the invention;

figure 3 illustrates how the implementation of the centrifugal compressor Assembly in accordance with the invention;

figure 4 - way implementation compressor Assembly made in accordance with the invention;

5 is another way of implementing compressor Assembly made in accordance with the invention; and

6 is another example implementation of a compressor Assembly in accordance with the invention.

With reference to figure 2 below is a description of the General principle of the compressor AG is Agata in accordance with the invention. In figure 2 for clarity shows one stage of compression, while the other compression stage is not shown. However, it is assumed that provision may be made for any number of compression stages, as it will be further noted with reference to figure 3-6.

Compressor unit shown in figure 2, has the engine 50, representing, for example, an electric motor with a large variable speed driving the rotor 52, which leads with the same speed of the driven shaft 54, on which the wheel with vanes 56. The rotor 52 and the driven shaft 54 connected by a flexible coupling 58. Thus, as the rotor 52 and the driven shaft 54 with their ends supported by two radial bearings, respectively 60, 62 and 64, 66. Emphasis 67 limits the axial displacement of the rotor 54 during operation of the compressor, which is influenced by the axial forces occurring when the differential pressure on either side of the wheel with vanes 56.

Wheel with vanes 56 draws the compressed gas supplied from the feed pipe 68 thus, in order to increase its static pressure, and increase its kinetic energy. The diffuser 70 (figure 3) slows the gas flow at the exit of the wheel with vanes 56, increasing its pressure. Behind the wheel discharge pipe 72 directs the gas in the compression stage 76 74...located behind the wheel.

As shown in figure 2 and 3, for which hladiny of the engine 50, as well as the bearings 60, 62, 64 and 66 and the stop 67 limits the axial movement of the rotor 50 of the gas at the outlet of the first compression stage 56 is selected and is used as a cooling gas.

These different elements, namely the motor, bearings and emphasis, are cooled with different cooling gas, i.e. parallel flow provided by pipelines 80-1, 80-2,...,80-6, included in the system external piping, collecting the gas at the outlet of the first compression stage 56 after the gas passes through a set of filter elements, such as 82. In accordance with the design, in this arrangement in the engine, on the one hand, and bearing, on the other hand, is provided parallel to the separate flow of cooling gas, which allows to overcome the limitations associated with the size of the air gap in the magnetic bearings, on the one hand, and on the engine, on the other hand.

As can be seen in figure 3, in accordance with an example implementation of the stator of the compressor has a branch pipe 84, which meets Wednesday, arriving at the exit of the diffuser 70, which passes through the casing 86 of the compressor. To ensure proper cooling of the motor and bearings of the compressor unit has a set of internal feed lines, in which the gas is fed respectively from the external piping 8-1,...,80-6. After passing through the motor and bearing cooling gas flows into the Central channel 88, performed in the longitudinal direction and connected with the feed pipe 68, which is located before the first stage 56 compression.

For cooling of the engine 50 and the end bearings 60 and 62 which supports the rotor 52, the end cap 90, the cover 86 has a hole 92 that is associated with the corresponding outer pipe 80-1. Part of this cooling flow is used for cooling of the bearing 60. Then this flow is fed to the cooling of the engine, passing through the air gap of the motor. Another part of this consumption is directly used for cooling the engine.

In other internal piping 94 gas is supplied from the external channels intended for cooling of the second bearing 62 of the engine.

Further, the flow rate of the cooling gas, intended for cooling of the bearings 60 and 62 and the motor 60, is fed into the cavity 85 in which is placed a flexible coupling 58, which is sealed closed by a plug 96.

Further, as shown by the arrows F, the gas is extracted inner pipe 88 and served before the first stage compression 56.

In addition, the bearings and the emphasis is cooled by the cooling gas supplied through the end cap 98, closing the corresponding edge of the casing 86. On codestone this figure shows the cover 98 has a hole 100, which is associated with the corresponding outer pipe 80-6. This flow of cooling gas, on the one hand, cools end bearing 66 located next to the cover 98, and end bearing 64, located on the opposite side, through the axial pipe 104, which is laid in the longitudinal direction on the outside radially between the bearings 64 and 66, through the elements of the stator of the compressor. This axial pipe for cooling the stop 78. After that, the gas flow is again fed into the pipe 88.

It should also be noted that the selection of the cooling gas at the outlet of the first stage compression produces less hot gas than if it were taken at the outlet of the compressor, which provides more efficient cooling, limiting the power required for compression, which need to be developed to increase the pressure of the gas.

In addition, this selection provides an independent source of supply since the start of the engine, so to limit the load losses at acceptable levels and to control external channels provides means 105 controlling the flow of cooling of the engine, on the one hand, and on cooling the bearings, on the other hand. These controls can be active, type regulating valve, is whether passive, type fixed flow washers.

It should also be noted that in the example implementation shown in figure 3, the suction gas into the compressor is located on the motor side. The principle of cooling described above, can also be used for layout, in which the pressure of the compressor is provided on the engine side. In this case, the flow rate of the cooling gas at the outlet of the engine or in General mechanisms located near balanced piston 107, peremeshivayte with the gas flow at the outlet of this balancing piston 107, and then is supplied to the supply pipe 68 by balancing the channel 108.

For maintenance provides a hermetic cap 96, through which access is provided to the flexible coupling 58. Removing the rotor from the engine by removing the end cap 90, which, for example, is attached to the casing by bolts. Removing the inner part of the compressor is carried out by removing the cover 98, which, for example, is attached to the housing with the terminal pins 110. Mainly the whole installation is performed so that the node of the rotor-aperture, i.e. the Assembly of the entire compressor could be removed from the housing simultaneously with the cover 98 without removing the casing from the base, and pipelines, as well as ohlord the affected channels. It should also be noted that the steps of mounting and dismantling the rotor rely on their bearing, which facilitates the operation of the connection-disconnection without the risk of damaging the rotating parts and parts of the stator, which would under other circumstances have contact with the rotors during these operations.

Finally, it should be noted that the invention is not limited to the methods of implementation in accordance with the above description.

Essentially, despite the fact that in figure 2 and 3 shows a centrifugal pump unit with integrated single-stage compressor, made in line with one section compression with multiple steps, the invention also applies to other types of pumping units, for example, with two sections S1 and S2 in the line, for example, each of which has two levels, each provides compression of the gas in accordance with the method shown in figure 4 and 5.

In this case, the example implementation shown in figure 4, the casing provides two inputs E'1 and E'2 and two outputs S'1 and S'2 such that log E'2 of the second section is located next to the output S'1 of the first section. Thus, in this case, as shown in figure 4, the first stage of compression of one of the sections S2 is opposite to the second compression stage another section S1.

And Vice versa, as shown in figure 5, for a configuration known n the title "Back to Back", the first stage of compression of each of the sections S1 and S2 can be placed side by side. In this case, the outputs S'1 and S'2 of these compression stages are placed side by side, and inputs E'1 and E'2 are located opposite each other.

It should also be noted, as seen in Fig.6 that the invention also applies to the arrangement in which in the General case are the engine 50 and two compressor units G1 and G2, each of which has a corresponding compression stage S3, S4, S5, S6 and S'3, S'4, S'5, S'6, each of which is mounted on a driven shaft 54 and 54', respectively, these shafts are mounted to two opposite ends of the rotor 52 via a flexible coupling 58 and 58'.

Such placement of two compressor units may be provided in accordance with one or another scheme described with reference to figure 4 and 5.

When these different ways of implementing the use of cooling of the engine and bearings using a parallel flow of the cooling gas.

The present invention does not require separate cooling fluid motor and bearings. In addition, provides for independent cooling of the motor, bearings and magnetic lock with the distribution of the flow rate required for each of them; then this different consumption is collected for re-submission to the WMO is in the first stage of compression.

These characteristics allow to reduce the size of the machine and to simplify its installation. In addition, the performance of the internal piping allows you to restrict the dimensions of the outer channels.

It should also be noted that the invention described above allows to limit gas leakage to the outside. In addition, the reliability increases to the extent, which provides internal filtration of the gas supplied to the cooling of the engine. In addition, the use of multiple filter inserts placed in parallel and connected with one set of valves, allows for the replacement of liners without stopping the machine.

Finally, the invention is not limited to the methods of implementation in accordance with the above description.

Essentially, in the above description, filtering is presented in the form of inserts that are installed on the exterior piping. Alternatively, you can also install the liners inside the crankcase of the compressor unit in a location that provides convenient access to them, for example, in the area of the cavity 95 thus, in order to provide access to the coupling preferably under cover.

1. Centrifugal compressor unit comprising a motor (50), resulting in rotational movement of the rotor (52), and at least one compressor, a part of which the CSOs including a stator and a set of wheels with blades (56), installed on the driven shaft, driven in rotational movement of the rotor in the stator housing, the apparatus consists of a motor and compressor mounted in a common gas-tight casing (86)through which the gas is fed to compressor unit; compressor unit has a set of active axial and radial guide bearings(60, 62, 64, 66, 67) rotor and the driven shaft, means for cooling the motor and the guide bearings by taking gas supplied by a compressor on the output of the first stage (56) compression, while above the gas passes through the engine (50) and the bearings and re is input to the compressor, wherein the cooling medium has a set of internal pipes(88, 92, 94, 104), feeding a cooling gas to the engine and the bearing, and the flow rate of the cooling gas in the engine (50) is different from the flow of the cooling gas bearings (60, 62, 64, 66) and converges before the first stage of compression.

2. Centrifugal compressor unit according to claim 1, characterized in that the cooling means also include a set of external channels (80-1, 80-2, 80-3, 80-4, 80-5, 80-6), which collect the gas at the outlet of the first compression stage and serve it in a parallel piping.

3. Centrifugal compressor unit according to claim 2, characterized in that in the internal trubor the water (80-1, 80-2), the feed gas to the engine, the gas flows in parallel through the internal piping (80-3, 80-4, 80-5, 80-6, supplying cooling gas to the bearings.

4. Centrifugal compressor unit according to any one of claims 1 to 3, characterized in that the cooling means include filtering (82) gas supplied by a compressor.

5. Centrifugal compressor unit according to claim 1, characterized in that the driven shaft of the compressor based on the two end radial bearing (64, 66), with cooling means include axial piping (104), which runs from one bearing to the other bearing, and in which the gas is fed from one of these ends of the outer channels, and the above-mentioned axial pipeline, in General, takes place in the longitudinal direction radially outside of the compressor.

6. Centrifugal compressor unit according to claim 1, characterized in that the inner pipes, the feed gas to the bearings contain a set of pipes (94), rotated radially outward from the compressor and the feed gas to each bearing.

7. Centrifugal compressor unit according to claim 1, characterized in that the cooling gas is fed to the engine through the hole (92)made in the outer cover (90)associated with the outer channel.

8. Centrifugal compressor unit according to claim 7, characterized in that the cooling gas peremeshivaete flow of the cooling gas at the outlet of the bearings, the cooled gas from the internal pipelines.

9. Centrifugal compressor unit according to claim 1, characterized in that it includes means for controlling the flow of cooling (105), on the one hand, for the engine, and, on the other hand, for each bearing.

10. Centrifugal compressor unit according to claim 1, characterized in that it contains means (108) collection of flow of the cooling gas supplied to the mechanisms located next to the balancing piston (107).



 

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