WO2013041452A1

WO2013041452A1 - Turbomachine train

Info

Publication number: WO2013041452A1
Application number: PCT/EP2012/068038
Authority: WO
Inventors: Rob Eelman; Volker Hütten; Tim Christian KRAUSE; Andreas Naumann
Original assignee: Siemens Aktiengesellschaft
Priority date: 2011-09-22
Filing date: 2012-09-14
Publication date: 2013-03-28
Also published as: DE102011083225A1

Abstract

The invention relates to a turbomachine train (20), having at least one turbo compressor (1) and one drive unit (2) for driving the at least one turbo compressor (1), a drive shaft (3) which is driven by the drive unit (2) and at least one output shaft (4) which drives the at least one turbo compressor (1), characterized in that a non-shifting clutch (5) is arranged between the drive shaft (3) and the at least one output shaft (4) which is designed to transfer a torque from the drive shaft (3) to the at least one output shaft (4), and in that at least one hydrodynamic torsion vibration dampener (6) is arranged between the drive unit (2) and the at least one turbo compressor (1).

Description

Turbo machinery train

The present invention relates to a

Turbomachinery, comprising at least one

A turbocompressor and a drive unit for driving the at least one turbocompressor, a drive shaft, which is driven by the drive unit, and at least one output shaft, which drives the at least one turbocompressor.

In turbomachinery strands there are a variety of

potential excitation sources of torsional vibrations. One of these excitation sources are, for example, inverter-driven drive units. Due to the repeated power conversion (AC-DC-AC) can harmonic and interharmonic

Excitation frequencies in the torsion systems of

Turbomachinery strands are initiated. Here the interharmonic excitation frequencies are of great importance. These interharmonic excitation frequencies often have resonances with the first torsional frequency within the driving range. Due to the low damping of the turbomachine strand or the torsion system of the steel structure, resonances can lead to significantly high oscillating torsional moments. These have a negative influence on the service life of the components in the turbomachine train of a turbomachine. Furthermore, in a turbomachine train having a transmission, the torsional vibrations are coupled to the flexural vibrations. In such turbomachinery strands can

Torsionspendelmomente cause increased bending vibrations in the transmission.

Furthermore, transient loads during a run-up of a drive unit of a turbomachine train,

for example, a synchronous motor or a

Asynchronous motor, at the network respectively

Short-circuit load cases, etc. negative impact on the Exercise turbomachinery strand. In this case, high dynamic moments can be generated for a short time

Components of the turbomachinery without damage

must be transferred to the same.

Regardless of the type of drive in the turbomachinery, there are a variety of other torsional excitation sources in a turbomachinery, which also increased

Can cause torsional loads.

Thus turbomachinery trains can be designed such that no torsional resonances in the operating speed range of

Turbomachinery strand occur. Furthermore, the

torque transmitting components are designed oversized in turbomachinery. It is also possible to block the operating speed ranges at which torsional resonances occur. Also minimizing the

Torsion excitation is conceivable. The usage of

Elastomeric couplings is another measure

Reduction of torsional loads. Also, by implementing a control loop within one

Inverter in the drive unit of a

Turbomachinery the torsional loads are reduced.

A disadvantage of such turbomachinery strands is the inflexibility of the turbomachine strand. This means that turbomachinery trains can not run at any speed

be driven. In particular, speeds with increased torsional vibrations are to be avoided. Furthermore, in particular the torque-transmitting components in

Turbomachinery to be sized large. This increases the costs. Accordingly, it is the object of the present invention to provide a turbomachinery, the previously

mentioned disadvantages of known turbomachinery strands avoids or improves. In particular, should Torsion load of a turbomachine strand can be reduced cost.

This object is achieved by a

Turbomachinery with the features of the independent claim 1 solved. Further features and details of the invention will become apparent from the dependent claims, the

Description and the drawings.

The turbomachinery has at least one

A turbocompressor and a drive unit for driving the at least one turbocompressor, a drive shaft which is driven by the drive unit, and at least one output shaft which drives the at least one turbocompressor on. Further, between the drive shaft and the at least one output shaft, at least one clutch, in particular at least one non-shiftable clutch, arranged for transmitting a torque from the drive shaft to the at least one output shaft

is formed, and between the drive unit and the at least one turbocompressor is at least one

arranged hydrodynamic torsional vibration damper. In this case, the at least one hydrodynamic

Torsional vibration damper depending on a

vibration-technical need to be arranged at any position and number in the turbomachinery.

Such a trained turbomachinery allows a reduction of the torsional load, especially in the torque-transmitting strand components. The integration of at least one hydrodynamic torsional vibration damper between the drive unit and the at least one

Turbo compressor increases the torsional damping in the

Turbomachinery train. The at least one hydrodynamic torsional vibration damper or at least one

hydrodynamic torsional vibration damper is preferably arranged on the drive shaft of the drive unit and rotates during operation of the turbomachine strand with the Drive shaft with. Therefore, the hydrodynamic learns

Torsionsschwingungsdämpfer in a rotation of the

Drive shaft of the turbomachine strand a

Torsional stress. In this case, the at least one hydrodynamic torsional vibration damper converts part of the kinetic vibration energy into heat energy. As a result, the torsional stresses in the turbomachinery can be reduced. That is, by the damping property of the at least one additionally arranged hydrodynamic torsional vibration damper, the dynamic

Torsion load of the turbomachinery strand can be reduced. By reducing the torsion load of the

Turbomachinery trains can increase the life of the components of the turbomachine train. Furthermore, by the arrangement of at least one hydrodynamic

Torsionsschwingungsdämpfers between the drive unit and the at least one turbocompressor

torque transmitting components in the turbomachinery strand smaller and lighter and thus cost-effective dimensions. The use of at least one hydrodynamic torsional vibration damper increases the flexibility with regard to the rotational speed range of the

Turbomachinery train. Speeds at which increased torsional vibrations are normally to be expected need not be avoided. The at least one, additionally provided hydrodynamic torsional vibration damper provides a possibility for natural frequency tuning of the

Turbomachinery strand or the Torsionssystems the turbomachine strand. By a

Natural frequency tuning of the turbomachine string can be done via the torsional stiffness of the hydrodynamic

Torsionsschwingungsdämpfers made a greater rotational speed distance to resonance states and thereby additionally occurring torsional vibrations can be reduced.

The at least one clutch, which is designed in particular as a non-shiftable clutch, transmits

unchanged torque in the turbomachinery, in particular from the drive shaft to the at least one output shaft of the turbomachine train. The purpose of the clutch is in addition to the transmission of a rotational movement or torque, the damping of torque surges.

Hydrodynamic torsional vibration dampers are also called hydrodynamic torsional dampers, as hydrodynamic

Torsional vibration damper or as hydrodynamic

Torsional coupling called.

The at least one hydrodynamic

Torsional vibration damper can be on the drive shaft

be arranged. According to a preferred alternative

Further development of the invention can at a

Turbomachinery be provided that the at least one hydrodynamic torsional vibration damper on the at least one clutch, in particular non-shiftable clutch, is arranged, in particular part of at least one clutch. The at least one clutch and at least one hydrodynamic torsional vibration damper can be arranged in a functional series connection. The at least one hydrodynamic torsional vibration damper may comprise a flywheel ring and a hub ring. These can be part of a clutch, in particular a non-shiftable clutch. In this case, the at least one hydrodynamic torsional vibration damper and the coupling are advantageously matched to one another such that torsional vibrations of the drive shaft of the

Turbomachinery strings are effectively damped. The at least one hydrodynamic torsional vibration damper can be a non-shiftable clutch driver disk, which is arranged as overload protection on the clutch, in particular the non-shiftable clutch, in particular on the flywheel of the clutch.

Furthermore, according to another preferred

Further development of the invention in one

Turbomachinery may be provided that the at least a hydrodynamic torsional vibration damper is arranged on the at least one output shaft. If several output shafts are provided in one of

Output shafts to be arranged in several or all output shafts at least one hydrodynamic torsional vibration damper.

The turbomachine train may have more than one turbocompressor, wherein the one or more further turbocompressors is / are driven by the drive unit. That is, one or more second output shaft (s) drives the other turbo-compressor (s). In particular, between the drive shaft and the at least one other

Output shaft may be arranged a second clutch, preferably non-shiftable clutch, which is designed to transmit a torque from the drive shaft to the at least one further output shaft. Furthermore, between the drive unit and the at least one

further coupling also be arranged at least one hydrodynamic torsional vibration damper. At a

thus formed turbomachinery strand are driven by a common drive shaft a plurality of turbocompressors. In such a turbomachine strand is between the

Drive shaft and the respective turbocompressor arranged at least one clutch. Due to the arrangement of

hydrodynamic torsional vibration dampers in the range of each clutch, the torsional load in all couplings of the turbomachine strand can be reduced. For example, a first non-shiftable clutch and a first hydrodynamic torsional vibration damper, and a second non-shiftable clutch and a second hydrodynamic torsional vibration damper each increase the torsional damping in the turbomachine train and the torsional vibration system, respectively. In the design calculation of the turbomachinery assembly within the torsional analysis are the hydrodynamic

Torsional vibration damper so to position and

to agree that they are mechanically relevant

Maximum attenuation of vibration forms. One hydrodynamic torsional vibration damper can be arranged on the one hand on the drive shaft of the drive unit and co-rotate with the drive shaft during operation of the turbomachine train. Due to the damping property of the

Torsional vibration damper can be the dynamic

Torsion load in the torque transmitting

Strand components are reduced. This allows the

Life of the turbomachine strand or the components of the turbomachine strand can be increased. Furthermore, the torque-transmitted components in the turbomachinery can be made smaller and lighter and thus more cost-effective.

The at least one further hydrodynamic

Torsionsschwingungsdämpfer can be arranged on another coupling, in particular a further non-switchable coupling, or part of another coupling,

in particular further non-switchable coupling be. Here, the same advantages apply, as explained above, in the arrangement of a first torsional vibration damper on a first clutch.

The hydrodynamic torsional vibration damper (s) convert a part of the torsional vibrations or the

kinetic vibration energy into heat energy. The

Torsion stresses in the strand components of the

Turbomachinery trains are thereby reduced. To dissipate this heat energy may be advantageous that in a turbomachinery strand at least one heat removal device for removal of the at least one

Torsional vibration damper generated heat energy is provided. At least one heat removal device may preferably be designed to remove the at least one heat removal device

Torsional vibration damper generated heat energy over

Convection be formed. Alternatively or additionally, at least one heat removal device for removing the generated by the at least one torsional vibration damper

Heat energy to be formed via a cooling circuit. Such heat removal devices allow effective removal of the through the at least one hydrodynamic

Torsional vibration damper generated heat energy. According to a further preferred development of

Invention may be provided in a turbomachinery that in the at least one output shaft

Intermediate transmission is provided. Intermediate gearboxes are required in particular when between the

Drive unit and the one or more turbocompressor (s)

different operating speeds prevail.

Also preferred is a turbomachine train, in which the drive unit is a turboexpander, in particular a

Gas turbine or a steam turbine, and / or a synchronous motor or an asynchronous motor. In synchronous motors, the rotor runs exactly with the specified by the mains frequency rotating field synchronously around, while in asynchronous motors, the rotor after the rotating field in engine operation nach- and leading in generator mode. In contrast to asynchronous motors, a field of excitation is required for the operation of synchronous motors.

Asynchronous motors and synchronous motors are variable in their speed. For example, an asynchronous motor or

Synchronous motor infinitely variable in speed to be able to use a power electronics, such as a frequency converter, often used.

According to a further preferred development of the present invention, it may be provided in a turbomachine train that the at least one turbocompressor is of radial and / or axial design. So can one or more turbocompressors in turbomachinery strand as

Radial turbocompressor be designed as Axialturboverdichter or as axial-radial turbocompressors.

Such turbomachinery trains are used, for example, in the oil and gas industry and in the process industry

Commitment. These include refineries, chemical and petrochemical plants. Furthermore, turbomachinery trains are used for natural gas transport and storage or for air decomposition. As a drive unit at

Turbomachinery trains can be used in addition to electric drives 5, in particular steam turbine drives or gas turbine drives.

The invention and its developments and their advantages will be explained in more detail by way of example with reference to the drawings 10 by means of typical turbomachinery configurations. Each shows schematically: ig. 1 shows a first turbomachine train, which is in accordance with the

design principle according to the invention is formed,

15

ig. FIG. 2 shows a second turbomachine train, which is designed according to the

according to the invention design principle is formed, ig. FIG. 3 shows a third turbomachine train, which according to the

20 design principle according to the invention is designed, and ig. 4 shows a fourth turbomachine train, which is designed according to the

inventive design principle is formed.

25 elements with the same function and mode of operation are each provided with the same reference symbols in FIGS. 1 to 4,

Fig. 1 shows a typical turbomachine strand 20, which is formed according to the construction principle according to the invention

30 is. The turbomachine 20 has a turbocompressor 1 and a drive unit 2 for driving the

Turbo compressor 1 on. A drive shaft 3 is driven by the drive unit 2. Further, the first one

Turbo compressor 1 connected to an output shaft 4.

Between the drive shaft 3 and the first output shaft 4, a clutch 5, in particular a non-shiftable clutch, is arranged. The clutch 5 is for transmitting a torque from the drive shaft 3 to the Output shaft 4 is formed. Between the drive unit 2 and the clutch 5 is a hydrodynamic

Torsional vibration damper 6 is arranged. Alternatively, the hydrodynamic torsional vibration damper 6 may be disposed at another position in the turbomachine string 20.

Furthermore, further hydrodynamic

Torsional vibration damper 6 may be arranged in the turbomachine 20 strand. Such a trained

Turbomachinery 20 enables a reduction of

Torsion stress in the torque transmitting components. The integration of the torsional vibration damper 6 between the drive unit 2 and the clutch 5, in particular the non-shiftable clutch 5, increases the torsional damping within the turbomachine strand 20. The hydrodynamic torsional vibration damper 6 can for example be arranged directly on the drive shaft 3 of the drive unit 2, so that he Operation of the turbomachine strand 20 with the drive shaft 3 co-rotated. At the rotation of

Drive shaft 3 of the turbomachine strand 20 experiences the hydrodynamic torsional vibration damper 6 a

Torsional stress. Part of the kinetic

Vibration energy converts the hydrodynamic

Torsionsschwingungsdämpfer 6 in heat energy. Due to the arrangement of the torsional vibration damper 6 in

Turbomachinery 20 can torsional loads in

Turbomachinery 20 can be reduced. By the

Reducing the torsional load can increase the life of the components of the turbomachine string 20.

Furthermore, by the arrangement of the hydrodynamic

Torsional vibration damper 6 between the drive unit 2 and the clutch 5, the torque transmitting components in the turbomachine 20 are made smaller, lighter and more cost effective. Likewise, the flexibility increases within the operating speed range of

Turbomachinery 20 by the use of

hydrodynamic torsional vibration damper 6. Previously locked speeds no longer have to be avoided. The hydrodynamic torsional vibration damper 6 can be arranged directly on the drive shaft 3. However, the hydrodynamic torsional vibration damper 6 is preferably arranged on the coupling 5 or is part of the coupling 5, which is preferably designed as a non-switchable coupling 5. For example, the clutch 5 and the hydrodynamic torsional vibration damper 6 can be arranged in a functional series connection to one another. In particular, the hydrodynamic torsional vibration damper 6 and the coupling 5 are advantageously matched to one another such that torsional vibrations within the

Turbomachinery 20 can be effectively damped. Of course, a hydrodynamic

Torsional vibration damper 6 may be arranged at any point in the turbomachine 20 strand. For example, a hydrodynamic torsional vibration damper 6 may also be arranged on the output shaft 4. In particular, in a turbomachine 20, a plurality of hydrodynamic

Torsional vibration damper 6 may be provided.

FIG. 2 schematically shows a further turbomachine strand 20, which is designed according to the construction principle according to the invention. In addition to the turbomachine strand 20 according to FIG. 1, an intermediate gear 11 is arranged in the turbomachine strand 20 according to FIG. 2 in the turbomachine strand 20. The intermediate gear 11 is arranged between the clutch 5, which connects the drive shaft 3 to the output shaft 4, and the turbo-compressor 1. In addition, a further clutch 5 is provided between the intermediate gear 11 and the turbo compressor 1. In such a turbomachine train 20, the turbocompressor 1 can be operated at different rotational speeds than specified by the drive unit 2. This allows the arrangement of the intermediate gear 11 between the turbo-compressor 1 and the drive unit. 2

Fig. 3 shows schematically a further turbomachine strand 20, according to the construction principle of the invention is trained. In contrast to the turbomachine strand 20 according to FIG. 2, in the case of that shown in FIG

Turbomachinery 20 additionally provided a second shaft end of the drive shaft 3 of the drive unit 2. That is, starting from the drive unit 2 is a first

Turbomachinery Teilstrang 21 and a second

Turbomachinery sub-strand 22 is provided. Both

Turbomachine sub-strands 21, 22 are on the

Drive shaft 3 of the drive unit 2 driven. The

Drive unit 2 of the first turbomachine sub-string 21 is connected via a drive shaft 3, an output shaft 4 and a first, preferably non-shiftable clutch 5 and a first torsional vibration damper 6 with a

Turbo compressor 1 coupled. Further, between the first non-shiftable clutch 5 and the turbo compressor 1 a

Intermediate gear 11 and a further clutch 5 is arranged. The second turbomachine sub-string 22 is over the

Drive shaft 3 of the drive unit 2, coupled via a first, preferably non-shiftable clutch 5 and a second torsional vibration damper 6 with an output shaft 4. In the output shaft 4 of the second

Turbomachine sub-strings 22 are also one

Intermediate gear 11 and a further clutch 5 arranged in front of the second turbocompressor 7. Such a thing

trained turbomachinery 20 allows a

optimal tuning of a torsional vibration reduced system.

4 schematically shows a further turbomachine strand 20, which is designed according to the construction principle according to the invention. Also in this turbomachine 20, two turbomachinery sections 21, 22 are provided. Both the first turbomachine sub-string 21, and the second

Turbomachinery sub-strand 22 are driven via the drive shaft 3 of the drive unit 2. At the first

Turbomachinery Teilstrang 21 is provided as a turbo compressor / expander 14 a Getriebeturboverdichter or a Getriebeturboexpander. Between this gear turbo compressor 14 and the drive unit 2, a clutch 5 and a hydrodynamic torsional vibration damper 6 is provided, which couple the drive shaft 3 with the output shaft 4. Also in the second turbomachine sub-strand 22 is the

Turbo compressor 1 in the design of a

Getriebeturboverdichters or a Getriebeturboexpander 14 executed. The gear turbo compressor or

Getriebeturboexpander 14 is driven by an output shaft 4, wherein the output shaft 4 via a preferably non-shiftable clutch 5 and a hydrodynamic

Torsional vibration damper 6 is coupled to the drive shaft 3 of the drive unit 2. The Getriebeturboverdichter or a Getriebeturboexpander 14 are a bearing block 16 and a turbine 18 connected downstream. Between the

Getriebeturboverdichter or the Getriebeturboexpander 14 and the bearing block 16 is a further clutch 5 is provided.

Likewise, a further coupling 5 is provided between the bearing block 16 and the turbine 18. All turbomachinery strands 20 according to FIGS. 1 to 4 have in common that the torsional loads can be reduced by the use of hydrodynamic torsional vibration dampers 6. By integrating at least one

hydrodynamic torsional vibration damper 6 between the drive unit 2 and a turbocompressor 1, the

Torsion damping within the torsion system of

considered strands 20 are increased. The one of the

at least one hydrodynamic torsional vibration damper 6 generated thermal energy can by appropriate

Heat removal devices, which are not shown in FIGS. 1 to 4, are discharged. It can the

Heat energy to be dissipated by convection cooling and / or by means of a coolant circuit. By the

Damping properties of the at least one arranged hydrodynamic torsional vibration damper 6 within the turbomachinery strands 20, the dynamic

Torsion load of each turbomachine strand 20 are reduced. This in turn increases the life of the Components of the respective turbomachinery strands 20. By the arrangement of at least one hydrodynamic

Torsionsschwingungsdämpfers 6 in a turbo compressor train 20, the torque-transmitting clutches 5 and the shaft ends can be made smaller, lighter and thus more cost-effective. The arrangement of a hydrodynamic torsional vibration damper 6 within a

Turbomachine string 20 increases flexibility during operation within the operating range of the engine

Turbomachinery string 20. That is, the

Turbomachinery trains 20 can also be operated at higher speeds. The hydrodynamic

Torsional vibration damper 6 in combination with the

Couplings 5 allow their own frequency and

Attenuation of the turbomachinery strands 20 and the Torsionssystems. By means of a natural frequency tuning of a turbomachine strand 20, a greater rotational speed distance to resonance states can be produced via the torsional rigidity of the hydrodynamic torsional vibration damper 6 and / or the clutches 5 used, thereby additionally reducing the occurring torsional vibrations.

The string configurations of turbomachinery trains with drives on turbo expanders, gas and / or steam turbines and asynchronous and synchronous motors and their combinations, with different types of turbocompressors radial and / or axial design, are extremely diverse. Therefore, the turbomachine strands listed here in FIGS. 1 to 4 should be regarded as typical application examples.

Claims

claims

Turbomachine strand (20), comprising at least one turbo compressor (1) and a drive unit (2) for

Driving the at least one turbocompressor (1), a drive shaft (3) which is driven by the drive unit (2)

is driven, and at least one output shaft (4) which drives the at least one turbocompressor (1), characterized in that between the drive shaft (3) and the at least one output shaft (4) at least one clutch (5) is arranged, which Transmission of a

Torque of the drive shaft (3) to the at least one output shaft (4) is formed, and that between the drive unit (2) and the at least one

Turbo compressor (1) at least one hydrodynamic

Torsional vibration damper (6) is arranged.

2. turbomachine string (20) according to claim 1,

characterized in that

at least one hydrodynamic torsional vibration damper (6) is arranged on the drive shaft (3).

3. turbomachine strand (20) according to claim 1 or 2, characterized in that

at least one hydrodynamic torsional vibration damper (6) is arranged on the first clutch (5), in particular being part of the first clutch (5).

4. turbomachine strand (20) according to any one of the preceding claims,

characterized in that

at least one hydrodynamic torsional vibration damper (6) is arranged on the at least one output shaft (4).

5. turbomachine string (20) according to any one of the preceding claims,

characterized in that

the drive unit (2) a turboexpander, in particular a gas turbine or a

Steam turbine, and / or an asynchronous or synchronous motor is.

6. turbomachine strand (20) according to any one of the preceding claims,

characterized in that

the at least one turbocompressor (1) is of radial and / or axial design.

7. turbomachine strand (20) according to any one of the preceding claims,

characterized in that

at least one heat removal device is provided for removing the heat energy generated by the at least one torsional vibration damper (6).

8. turbomachine strand (20) according to claim 7,

characterized in that

at least one of the at least one heat removal device for removal of the hydrodynamic

Torsional vibration damper (6) generated thermal energy is formed by convection.

9. turbomachine strand (2 0) according to any one of the preceding claims 7 or 8,

characterized in that

Torsional vibration damper (6) generated heat energy is formed via a cooling circuit.

10. turbomachinery (20) according to any one of the preceding claims,

characterized in that

in the at least one output shaft (4)

Intermediate gear (11) is provided.

11. turbomachine string (20) according to claim 10,

characterized in that

between the intermediate gear (11) and the at least one turbocompressor (1) at least one clutch (5) in the at least one output shaft (4) is provided.

12. turbomachine strand (20) according to any one of the preceding claims,

characterized in that

the at least one clutch (5) is designed as a non-shiftable or shiftable clutch.