EP3230594B1 - Assembly having two compressors, method for retrofitting - Google Patents

Description

The invention relates to an arrangement with a first compressor train and a second compressor train for compressing a process fluid, wherein the first compressor train comprises a first drive and a first compressor, wherein the second compressor train comprises a second drive and a second compressor, wherein the first compressor train does not torque transmitting mechanically coupled to rotating parts of the second compressor train, wherein the two compressors of the different compressor strands are connected by a connecting fluid line directly fluid-conductively, such that the first compressor is arranged upstream of the second compressor. In addition, the invention relates to a method for retrofitting a first compressor to an existing system comprising a second compressor to obtain from an existing system in the course of retrofitting an arrangement according to the invention.

The invention is essentially concerned with increasing the performance of compressor systems. Two decisive parameters of the performance are the volume flow and the pressure ratio of the outlet pressure to the inlet pressure of a corresponding compressor unit. In order to further increase the power of the compressor system for a given number of compressor stages, essentially the two possibilities arise of raising the diameter of blade rings or impellers or of increasing the rotational speed. These two design options are largely exhausted, since the available materials have already reached the limits of their strength characteristics and accordingly can not bear higher peripheral speeds or diameters in terms of power. Larger diameters also mean additional problems in the manufacture of the rotors and further challenges in the field of rotor dynamics.

A preferred field of application of the invention lies in the area of the air compressors designed as gear compressors, which suck in substantially atmospherically - if necessary with the interposition of a filter so that a pressure below the atmospheric pressure results at the compressor inlet connection - and the aspirated volume flow by means of a plurality of radial compressor stages to a final pressure from about 3 to 200 bar. In a gear compressor is essentially a - relatively large - gear housing, on the outside of different spiral housing are mounted, in which the wheels of the centrifugal compressor are driven by gear siding. In each case an intermediate cooling can be provided between the individual compression stages. The largest diameter of wheels of radial compressor stages are yet to increase below two meters and due to the above-indicated problems only with major design hurdles using expensive materials and special manufacturing.

From the pamphlets US 2012/260693 A1 .
DE 20 2012 101190 U1 . WO 03/040567 A1 . GB 1 551 454 A .
EP 0 811 770 A1 . WO 2009/095097 A1 Various multi-stage compression arrangements are already known.

On the basis of the above-described problem field, the object of the invention is to make available a compressor system which provides a higher power with relatively little effort. In addition, it is an object of the invention to provide a method for retrofitting existing compressor systems, so that the respectively retrofitted compressor system provides a higher power, in particular a higher volume flow. These two tasks are to be accompanied by the fact that it is not absolutely necessary to further restrict the loading of components or materials to corresponding limit values or to use more expensive materials.

To solve the object of the invention, an arrangement of the type mentioned is proposed with the additional features of claim 1. Furthermore, the invention proposes a method for retrofitting an existing plant according to the method claim. The respective dependent claims contain advantageous developments of the invention.

An essential feature of the invention is to increase the power of a compressor unit in that the process fluid sucked in by the second compressor has already been lifted by a factor of 1.1 to 1.6 in the pressure upstream of the inflow. This type of pre-compression or supercharging of the second compressor may result in a standard volume flow increase or mass flow increase of between 10% and 40% compared to a non-supercharged arrangement, assuming a substantially constant pressure ratio of the outlet pressure to the inlet pressure of the overall system. The cost of a charge according to the invention here is relatively low, since the pressure ratio of the first compressor is small. For such a pressure ratio, for example, it is sufficient to provide or retrofit a blower in the inflow to the second compressor, which according to the invention has its own drive and accordingly can be operated largely independently of the first compressor. The solution according to the invention is particularly interesting as a retrofit for existing systems which are integrated in a process which can be increased in productivity, in particular by an increase in the volume flow.

An advantageous development provides that the second compressor with a pressure ratio between 3 to 60 compressed. The ratio of the pressure ratios between the second compressor and the first compressor may preferably be approximately between 2.3 to 56, more preferably the second compressor provides at least 3.8 times higher pressure ratio than the first compressor. For this reason, the first compressor due to the design much cheaper can be made as the second compressor and can be referred to as a fan (pressure ratio of 1 to 1.3) or blower (pressure ratio of 1.3 to 3.0).

The belonging to the first compressor train first drive can be configured either as an electric motor, steam turbine or gas turbine. For maximum flexibility and investment, it is particularly useful to choose an electric motor as the first drive. The second drive may also be in the form of a turbine or in the form of an electric motor. If process steam is available, the operation by means of a steam turbine is particularly advantageous. The first compressor may be designed as an axial compressor or as a radial compressor, wherein due to the low pressure ratio of the first compressor, the term fan or blower can be used. In the following, the first compressor is usually used, regardless of any pressure ratio of the first compressor, depending on the pressure ratio in the strict sense may be a fan or a fan. In the terminology of this patent application, the term of the first compressor also includes the design of this first compressor as a fan or blower.

A particularly advantageous embodiment of the invention provides that the first compressor comprises at least two compressor stages and the first drive is arranged between a first group of compressor stages and a second group of compressor stages.

In an embodiment of the first compressor as at least double-flow, in particular double-flow centrifugal compressor, both radial impellers each having an axial intake side and an axial Radscheibenseite, it may be useful if the Radscheibenseite the first radial impeller axially the Radscheibenseite the second radial impeller is facing and the two radial impellers axially opposite Aspirate directions. Here, the drive can either be arranged axially between the two Radscheibenseiten or drive axially on one side of the two wheels. The two impellers of the centrifugal compressor can flow into a common diffuser. The double flush corresponds to a parallel arrangement of the radial impellers.

An expedient development of the invention provides that the arrangement has a filter upstream of the second compressor. It may be expedient here for the first compressor to be arranged upstream of this filter and for the process fluid to be introduced into the second compressor only after passage of the filter. In this case, the first compressor would prefer to suck in atmospherically directly without a filter, and in the event of retrofitting the subsequent system would possibly have to be adapted to a somewhat higher pressure in the filter and upstream of the second compressor in the intake line. Alternatively, the first compressor may also be provided between the filter and the second compressor so that the process fluid downstream of the first compressor is introduced directly into the second compressor without passage of a filter. It is expedient that the filter housing, especially in a retrofit, not to be upgraded to a slightly elevated pressure.

Another advantageous development provides that at least the first compressor or the entire first compressor train is arranged in a housing of a filter.

Frequently, corresponding filter with their own housing outside of a machine house, so that in an extension of such a filter to, for example, the first compressor or compressor train greater design freedom are given as within the machine house, where the second compressor train is arranged. This advantage also results in an arrangement of the first compressor upstream of the filter as already described above.

Particularly useful is the equipment of the arrangement with a pump protection device. The anti-pump device may be provided in particular for the protection of the first compressor before a pumping operation of the second compressor. Due to the much higher pressure ratio of the second compressor corresponding pumping operations on this unit are associated with a relatively higher destruction potential. Advantageously, this anti-pump device may have a delivery device which, in the case of pumping, delivers at least 80% of the flow cross section of the connecting fluid line between the first compressor and the second compressor. This delivery device can meaningfully have flaps which obstruct the cross-sectional area of the connecting fluid line in the event of a backflow. Such a configuration of these flaps is particularly expedient, so that the aerodynamics of the flaps, driven by the backflowing process fluid, move the flaps into a closed position during a return flow of the process fluid in the direction of the first compressor. For movement from the closed position back to the open position, damping may be provided so that the flaps do not periodically go on and off with the surge. Particularly useful is a design of the flaps such that they are each rotatable or pivotable about an axis. These axes preferably extend perpendicular to a longitudinal axis of the fluid-conducting connection or perpendicular to the main flow direction through the fluid-conducting connection. Particularly preferably, these flaps are arranged like a lamella next to each other, so that in an open position of these flaps, the process fluid flows through the fluid line through a grid formed by the axes of rotation of the flaps. In a closed position, the spaces between the Drehachsengittern be closed by the louver-like or lammellenartigen flaps. Alternatively or in addition to the delivery device of the anti-pump device it is useful if a relief device is provided, which in the case of pumping the first compressor and / or the second compressor, a pressure relief of the connecting fluid line between the first compressor and the second compressor or at least the portion of the fluid line between the delivery device and the second Compressor by means of an opening in a pressure sink - for example, the environment - relieved of pressure and / or pressure surges. Such a relief device and / or delivery device is particularly useful when the first compressor is an axial compressor, because the usually freestanding blades of an axial compressor are sensitive to pressure surges from pumping operations. In a first compressor, which is designed as a radial compressor, it may be justifiable, especially for reasons of cost, not to provide a surge protection device upstream of the second compressor, since a trained as a radial compressor compressor can be made sufficiently strong.

Particularly useful is an embodiment of a surge protection device with a relief device having a slide valve and is mechanically connected to a feed device. The sliding valve may in this case have an axial displaceability in the longitudinal direction of the connecting fluid line, which is displaced axially as a result of a backflow of the process fluid to the delivery device such that a pressure-relieving opening is created in the connecting fluid line due to the slide valve open with it.

The arrangement according to the invention is particularly well suited for retrofitting a first compressor train to a second compressor train of a system inventory, so that an arrangement according to at least one embodiment of the invention described above arises. It is particularly expedient to retrofit the first compressor to the existing as a second compressor, the second compressor is aerodynamically changed such that the pressure ratio of the second compressor is reduced compared to the state before retrofitting. In this way, the result of retrofitting total arrangement of first compressor and second compressor have a higher flow rate than the second compressor alone with the same pressure ratio to the atmosphere. In the retrofit case, a largely constant pressure ratio or the same final pressure is often desired and possibly an increased volumetric flow, since the integration into the already existing process requires the already predetermined final pressure from the total compression.

An advantageous development of the invention provides that the arrangement according to the invention is part of a gas turbine, such that the second compressor with a compressor housing is a direct component of the gas turbine. It is expedient here if the first compressor can optionally be switched on in the flow path of the fresh air intake, so that, for example, depending on the ambient conditions, the first compressor can assume the function of a supercharger for the gas turbine.

A special refinement of this arrangement with a first compressor which can be switched into the flow path provides a shut-off device, for example a flap and a bypass, in addition to a direct intake of the second compressor past the first compressor. In the bypass, the first compressor is arranged so that the front sealer is used only when needed (eg during seasonal fluctuations) and otherwise the second compressor sucks directly through the opened flap. When the flap is open, an inlet guide of the supercharger may be closed so that no uncontrolled flowing bypass to the open flap occurs

An advantageous development of the invention provides that the first compressor has a Eintrittsleitapparat that adapts the inlet cross section to the required absorption capacity. Particularly preferred is the drive of the first compressor not regulated as a function of the set volume flow, so that the regulation of the volume flow through the first compressor at approximately constant speed takes place exclusively by means of Eintrittsleitappartes.

Figur 1

eine schematische Prozessübersicht über eine Anordnung nach der Erfindung,

Figur 2

eine dreidimensionale schematische Darstellung einer Anordnung nach der Erfindung,

Figur 3

eine schematische Wiedergabe im Längsschnitt einer Kombination aus einem Filter mit einem ersten Verdichterstrang,

Figur 4

eine andere Ausführung eines ersten Verdichterstrangs,

Figur 5

eine schematische Darstellung im Querschnitt eines ersten Verdichterstrangs in modularer Ausführung,

Figur 6

ein schematischer Längsschnitt durch eine erfindungsgemäße Anordnung mit einem ersten Verdichterstrang, dessen erster Verdichter als Radialgebläse ausgebildet ist,

Figur 7

eine schematische Darstellung eines ersten Verdichterstrangs als Radialgebläse im Längsschnitt durch den ersten Verdichter,

Figur 8

eine alternative Ausbildung zu der Darstellung der Figur 7

Figur 9

ein Ausführungsbeispiel eines Pumpschutzes stromabwärts eines als Radialgebläse ausgebildeten ersten Verdichters mit einem anschließenden Filter,

Figur 10

eine Zustellvorrichtung eines Pumpschutzes,

Figur 11

einen Pumpschutz, mit einer kombinierten Zustellvorrichtung und Entlastungsvorrichtung in einer ersten Betriebsposition in Geschlossenstellung der Entlastungsvorrichtung,

Figur 12

die Pumpschutzvorrichtung nach Figur 11 in einer zweiten Betriebsposition in einer Offenstellung der Entlastungsvorrichtung.

In the following the invention with reference to some embodiments with reference to drawings is described in more detail. Show it:

FIG. 1

a schematic process overview of an arrangement according to the invention,

FIG. 2

a three-dimensional schematic representation of an arrangement according to the invention,

FIG. 3

3 is a schematic representation in longitudinal section of a combination of a filter with a first compressor train;

FIG. 4

another embodiment of a first compressor train,

FIG. 5

a schematic representation in the cross section of a first compressor train in a modular design,

FIG. 6

a schematic longitudinal section through an inventive arrangement with a first compressor train, the first compressor is designed as a radial fan,

FIG. 7

a schematic representation of a first compressor train as a radial fan in longitudinal section through the first compressor,

FIG. 8

an alternative training to the presentation of the FIG. 7

FIG. 9

an embodiment of a surge protection downstream of a radial blower designed as a first compressor with a subsequent filter,

FIG. 10

a delivery device of a pump protection,

FIG. 11

a surge protection, with a combined delivery device and discharge device in a first operating position in the closed position of the discharge device,

FIG. 12

the anti-pump device after FIG. 11 in a second operating position in an open position of the relief device.

An arrangement according to the invention with a first compressor line CT1 and a second compressor line CT2 is shown schematically in a plan view of the longitudinal axis of the overall arrangement already in FIG FIG. 1 played. A process fluid PF is sucked in through a filter FIT, FIT 'and conveyed to a higher pressure level in a first compressor CO1 of a first compressor line CT1 designed as a fan. The FIG. 1 shows two alternative embodiments of the filter FIT, FIT '. In a first possibility, the filter FIT is located in a housing separate from the first compressor line CT1. In the second embodiment, the filter FIT 'is located in a common housing with the first compressor train CT1.

After exiting the first compressor CO1 of the first compressor line CT1, the process fluid PF passes into a downstream connecting fluid line CFC and further downstream to a second compressor line CT2. The second compressor train CT2 has a second compressor CO2, which is designed as a transmission compressor, so that a first compressor stage CO21 of the second compressor CO2 is driven by means of a first transmission GR1 and a second downstream compressor stage CO22 of the second Compressor CO2 is driven by means of a second transmission GR2. The first transmission GR1 and the second transmission GR2 are driven by means of a second drive DR2, wherein in a manner not shown the two transmissions GR1, GR2 are components of a common transmission of the transmission compressor.

Basically, such transmission compressor are known. These are gearboxes - which are relatively large - to which the outside volute casing of the individual compressor stages are flanged. As a rule, a large wheel is arranged in the transmission, which is driven by a common drive for the individual compressor stages. In most cases, this drive outside the transmission housing by means of a coupling to the transmission housing connected torque transmitting. The individual compressor stages are driven by means of pinion shafts, of which at least one shaft end, usually both shaft ends, protrude from the transmission housing. At the outstanding shaft ends, the wheels of the individual compressor stages - usually mounted over-mounted. Between the individual compressor stages of the gear compressor, the process fluid can be supplied to other processes or simply undergo cooling. Alternatively, the process fluid can also be transferred from a compressor stage directly to the next compressor stage by means of a connecting fluid line. In the FIG. 1 is shown an intermediate cooling ICL between the two compressor stages CO21, CO22 of the second compressor CO2. After compression in the second compressor CO2 of the second compressor line CT2, the process fluid PF is fed to further processes PRO.

The compression in the first compressor train CT1 takes place at a pressure ratio of between 1.1 and 1.6. The second compressor train CT2 compresses the process fluid PF to a final pressure of about 3 to 60 bar. The first compressor train CT1 sucks in almost atmospheric, the process fluid in the present case is air. The application as air compressor is the embodiment preferred for the invention. The first compressor train CT1 sucks slightly below the atmospheric pressure because the upstream filter FIT causes a pressure loss.

FIG. 2 shows a perspective view of a possible embodiment of the inventive arrangement. A filter FIT is disposed in a filter housing upstream of the first compressor train CT1. The first compressor line CT1 is integrated in the connecting fluid line CFC, which extends substantially from the filter FIT to the second compressor line CT2. Possible embodiments of such a first compressor CO1 and the first compressor line CT1 are in the FIGS. 3, 4, 5 shown. Downstream of the connecting fluid line CFC, a second compressor CO2 of the second compressor line CT2 designed as a transmission compressor is reproduced. The second transmission of the gear compressor is referred to as GR2, wherein the second transmission for each compressor stage has its own gear components, which are not specifically identified here. The design of this transmission compressor corresponds to the basic design of transmission compressors described above. According to the second compressor is designed as a transmission compressor. In the axial extension of the flow of the process fluid PF through the connecting fluid line CFC, the second drive DR2 of the second compressor line CT2 is located behind the second compressor CO2. The first drive DR1 of the first compressor line CT1 is not visibly integrated in the connecting fluid line CFC.

Such a type of integrated design of the first compressor train CT1 is in the FIG. 3 played. Downstream of a filter FIT, the process fluid PF is conveyed from the first compressor line CT1 to a higher pressure level, wherein both the first compressor CO1 and the first drive DR1 in the connecting fluid line CFC between the filter FIT and the not shown downstream second compressor train CT2 are integrated. The first compressor CO1 is designed here as an axial compressor. The two illustrated compressor stages CO11, CO12 of the first compressor CO1 can in this case be driven in opposite directions with the saving of guide vanes, with corresponding gear measures for the drive not being reproduced here. The first drive DR1 can also be located radially outside this axial blading. For the integral formation of the first compressor CO1 in extension of the connecting fluid line or as an integral part of the connecting fluid line CFC, the formation of the first compressor as axial compressor is preferred. An alternative embodiment of an axial compressor as the first compressor CO1 shows the FIG. 4 in which four compressor stages CO11, CO12, CO13, CO14 are arranged axially one behind the other, reference being made to an axis of rotation X which extends along the main flow direction of the process fluid PF. This rotation axis X is also in the FIG. 3 played. While in the FIG. 3 the first drive DR1 is located on an axial side of the entire first compressor CO1 is in the FIG. 4 the first drive DR1 is disposed axially between upstream and downstream compressor stages CO11 to CO14. This axial order has the advantage that the axis of the rotor does not protrude particularly far from the drive DR1 and in this way the inherent storage of the engine is sufficient to control the rotor dynamics of the overall arrangement of the first compressor. A comparable consideration included the FIGS. 7 and 8 with regard to the execution of the first compressor line CT1 or of the first compressor CO1 as a radial compressor.

A special modularity of the first compressor line CT1 shows FIG. 5 , Perpendicular to the axis X is here the connecting fluid line CFC cut and the individual compressor stages CO11 to CO14 are shown schematically. The cross-section of the connecting fluid line CFC is divided into four segments, one in each segment Compressor is arranged CO11 to CO14, so that there is no serial compressor stage arrangement, but a parallel. In this way, smaller blower can be used side by side to pre-compact the process fluid PF before entering the second compressor CO2.

FIG. 6 shows a Schamtische representation of an inventive arrangement, wherein the first compressor CO1 of the first compressor line CT1 is formed as a radial fan and compressed atmospheric intake air before entering the filter FIT. The filter FIT and the first compressor CO1 are in this case arranged outside a machine house for the second compressor line CT2 - or on the other side of a house wall BW of the machine house MH. The housing of the filter FIT is in this case subjected to an outlet pressure which is above the pressure of the atmosphere and must therefore be reinforced in relation to an atmospheric intake. This is particularly important in the case of retrofitting the first compressor line CT1, since it may be necessary to replace the entire filter Fit with an improved model.

The FIGS. 7 and 8 show a possible embodiment of the first compressor CO1, as in FIG. 6 is shown. Comparable with the axial compressors of FIGS. 3 and 4 is here in the FIG. 7 the first drive DR1 axially adjacent to the compressor stages CO11, CO11 'and arranged in the FIG. 8 the first drive DR1 is located axially between the two compressor stages CO11, CO11 '. The difference to the representation of the FIGS. 3 and 4 The axial compressor is essentially in that the radial blower design of the FIGS. 7 and 8 suck axially and eject radially, and in that the radial compressor stages do not work serially to each other but in parallel.

The FIGS. 9, 10 . 11 and 12 deal with a PPC anti-surge device for the arrangement. FIG. 9 shows the first compressor CO1 as a radial fan in arrangement upstream of the filter FIT. The downstream connecting fluid conduit CFC is equipped with the anti-surge device PPC. The anti-surge device PPC is a pressure relief device PRL, wherein spring-biased valves open at positive pressure in the connecting fluid line CFC. In this way, the radial fan of the first compressor CO1 is protected from surges on the downstream second compressor CO2, not shown.

The FIG. 10 shows a delivery device BLO, which may be provided in the connecting fluid line CFC, the first compressor CO1 to protect against surges from the second compressor CO2. In principle, this delivery device BLO can be part of every pump protection device PPC or otherwise be provided as a non-return flap to prevent backflow. The delivery device BLO is the left FIG. 10 represented in a view in the axial direction of an axis X. The axis X corresponds to the main flow direction of the process fluid PF. The delivery device BLO comprises a plurality of flaps arranged side by side flaps, which can deliver the flow cross-section of the connecting fluid line CFC to at least 80%. A total tightness is not sought, but high differential pressures from pressure surges should be prevented or shielded. In the action sequence reproduced to the right of the cross-sectional illustration, a plurality of flaps FLP-viewed in the direction of rotation axis perpendicular to the main flow direction-are initially arranged side by side in the open position. A process fluid PF flows along the normal flow direction. Upon reversal of the flow direction-that is to say in the case of a backflow-of the process fluid PF, the middle pair of flaps FLP initially closes as a result of the aerodynamic design of the flaps in which the return flow catches and in this way closes the flaps FLP. Similar to a domino effect, the adjacent flaps also become sequential by the collapse and / or flow redirection of the flaps that are first closed FLP closed. In this way, in the fourth image of the sequence-like representation, the complete delivery device BLO is in a closed position. Preferably, the flaps FLP are provided with a working in one direction damping, so that it does not come as a result of pump surges to a permanent opening and closing of the delivery device BLO. The damped direction of movement is in this case preferably the movement into the opening position.

The FIGS. 11 and 12 show the execution of a surge protection device PPC, which combines a delivery device BLO and a pressure relief device PRL together. Here is the anti-pump device PPC in the FIG. 11 in a normal open operating position and in FIG. 12 in an operating position closed to the normal flow of the process fluid PF. The connecting fluid line CFC is in this case equipped with a slide valve SLV, which is axially displaceable in the direction of an axis X. This slide valve SLV is part of the pressure relief device PRL. Fixedly connected to the slide valve SLV is the feed device BLO, which closes the flow cross-section of the connecting fluid line CFC to at least 80% in an axial back flow of the process fluid PF. Against the force of a return spring EEL and a damper DMP the differential pressure via the delivery device BLO of the process fluid PF trying to flow back drives the slide valve SLV to an axial position in both upstream and downstream of the delivery device BLO a radial outlet of the pressure relief device PRL is open, so that a pressure relief of the process fluid PF takes place. In this way, both the upstream and downstream of the anti-surge device PPC, the first compressor train CT1 and the second compressor train CT2 are protected from surges.

Claims (19)

1. Arrangement having a first compressor train (CT1) and a second compressor train (CT2) for compressing a process fluid (PF),
   wherein the first compressor train (CT1) comprises a first drive (DR1) and a first compressor (CO1),
   wherein the second compressor train (CT2) comprises a second drive (DR2) and a second compressor (CO2),
   wherein the first compressor train (CT1) is not mechanically coupled in torque-transmitting fashion to rotating parts of the second compressor train (CT2), wherein the two compressors (CO1, CO2) of the different compressor trains (CT1, CT2) are directly connected in fluid-conducting fashion to one another by means of a connecting fluid line (CFC),
   in such a way that the first compressor (CO1) is arranged upstream of the second compressor (CO2), and wherein
   the first compressor (CO1) compresses with a pressure ratio between 1.1 and 1.6 before the process fluid (PF) is fed to the second compressor (CO2),
   characterized in that
   the second compressor (CO2) is in the form of a geared compressor.
2. Arrangement according to Claim 1,
   wherein the second compressor (CO2) compresses with a pressure ratio between 3 and 60.
3. Arrangement according to Claim 1,
   wherein the first drive (DR1) is either a gas turbine or a steam turbine or an electric motor.
4. Arrangement according to Claim 1,
   wherein the second drive (DR2) is either a gas turbine or a steam turbine or an electric motor.
5. Arrangement according to Claim 1 or 2,
   wherein the first compressor (CO1) is a radial compressor or an axial compressor or a cross-flow blower.
6. Arrangement according to at least one of the preceding Claims 1 to 3,
   wherein the first compressor (CO1) comprises at least one first compressor stage (CO11) and one second compressor stage (CO12),
   wherein the first drive (DR1) is arranged between the first compressor stage (CO11) and the second compressor stage (CO12).
7. Arrangement according to at least one of the preceding claims,
   wherein the first compressor (CO1) is in the form of an at least two-stage radial compressor,
   wherein at least the first and the second compressor stage (CO1, CO12) have an intake side (SS) and a wheel disk side (BS),
   wherein the wheel disk side (BS) of the first compressor stage (CO11) faces axially toward the wheel disk side (BS) of the second compressor stage (CO12) and the intake by the two compressor stages (CO11, CO12) occurs axially from opposite directions.
8. Arrangement according to Claim 5,
   wherein the first drive (DR1) is arranged axially between the two wheel disk sides (BS) of the first compressor stage (CO11) and the second compressor stage (CO12).
9. Arrangement according to at least one of the preceding Claims 1 to 6,
   wherein the first compressor train (CT1) is arranged upstream of a filter (FIT) and a process fluid (PF) is conducted into the second compressor (CO2) only after passing through the filter (FIT).
10. Arrangement according to at least one of the preceding Claims 1 to 6,
    wherein a filter (FIT) is arranged upstream of the first compressor (CO1), and the process fluid (PF) is, downstream, conducted directly into the second compressor (CO2) without passing through a filter (FIT).
11. Arrangement according to at least one of the preceding claims,
    wherein at least the first compressor (CO1) or the entire first compressor train (CT1) is arranged in a housing (FCS) of a filter (FIT).
12. Arrangement according to at least one of the preceding claims,
    wherein at least one surging protection device (PPC) is provided between the first compressor (CO1) and the second compressor (CO2),
    wherein the surging protection device (PPC) has a closing device (BLO),
    wherein, in the event of surging, the closing device (BLO) closes at least 80% of the flow cross section of the connecting fluid line (CFC) between the first compressor (CO1) and the second compressor (CO2).
13. Arrangement according to at least one of the preceding claims,
    wherein at least one surging protection device (PPC) is provided between the first compressor (CO1) and the second compressor (CO2), wherein the surging protection device (PPC) comprises a pressure relief device (PRL) which, in the event of surging of the first compressor (CO1) and/or of the second compressor (CO2), relieves a pressure relief of the connecting fluid line between the first compressor (CO1) and the second compressor (CO2), or on at least the section of the fluid line (CFC) between the closing device (BLO) and the second compressor (CO2), of pressure and/or pressure shocks through an opening into a pressure sink.
14. Arrangement according to at least the preceding Claim 12,
    wherein the first compressor (CO1) is an axial compressor.
15. Arrangement according to at least one of the preceding Claims 1 to 9,
    wherein the first compressor (CO1) is in the form of a radial compressor and no surging protection device (PPC) is provided upstream of the second compressor (CO2).
16. Arrangement according to at least Claim 12,
    wherein the closing device (BLO) is designed such that, in the event of a backflow of the process fluid (PF) from the second compressor train (CT2) to the first compressor train (CT1), the closing device (BLO), driven by the backflowing process fluid (PF), blocks the connecting fluid line over at least 80% of the cross-sectional area.
17. Arrangement according to at least Claim 14,
    wherein the closing device (BLO) is connected to a slide valve (SLV) and a mechanical thrust arising from the differential pressure of the closing body moves the slide valve (SLV) into an opening position, such that the connecting fluid line between the first compressor train (CT1) and the second compressor train (CT2) is connected to a pressure sink (PRL), such that a release of pressure from the connecting line occurs.
18. Method for retrofitting and/or adding a first compressor train (CT1) to a second compressor train (CT2) of an existing installation, such that an arrangement according to at least one of the preceding Claims 1 to 17 is realized, wherein the first compressor train (CT1), with a first drive (DR1) and a first compressor (CO1),
    is arranged upstream of a second compressor train (CT2) comprising a second drive (DR2) and a second compressor (CO2),
    wherein the first compressor train (CT1) is not mechanically coupled in torque-transmitting fashion to rotating parts of the second compressor train (CT2), wherein the two compressors (CO1) of the different compressor trains (CT1, CT2) are connected in fluid-conducting fashion to one another by means of a connecting fluid line (CFC),
    in such a way that the first compressor (CO1) is arranged upstream of the second compressor (CO2),
    wherein the first compressor (CO1) compresses with a pressure ratio between 1.1 - 1.6 before the process fluid is fed to the second compressor (CO2).
19. Method according to Claim 18, wherein, in a step of the retrofitting, the second compressor is aerodynamically modified such that the pressure ratio is reduced in relation to the state before the retrofitting.

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