DE1426265C

DE1426265C -

Info

Publication number: DE1426265C
Authority: DE

Description

1 21 2

. Die Erfindung bezieht sich auf eine Gasturbinen- geschwindigkeit der Leitschaufeln nun deren Ananlage mit einem Gaserzeuger, bestehend aus einem Strömverhältnisse gegenüber dem Ruhezustand des Verdichter, einer Verdichterturbine und einer Brenn- Leitrades ebenso, wie dies auch bei der bekannten kammer, und mit einer Nutzleistungsturbine, die ein Leitschaufelverstellung der Fall ist, doch ändern sich drehbares Leitrad besitzt, das bremsbar ist und über S die Anströmverhältnisse am Leitrad nicht in so stareine Übertragungseinrichtung mit dem Laufrad der kern Maße, wie dies anderenfalls bei dem Laufrad Nutzleistungsturbine in Verbindung steht. der Fall wäre. Zudem gelingt es aber durch die Er-Es sind bereits die verschiedenartigsten Gas- findung, bei Inbetriebsetzung der Turbine und bei turbinenanlagen bekanntgeworden, bei denen Ver- niedriger Drehzahl eine beträchtlich erhöhte Drehdichter, Verdichterturbine und gegebenenfalls Nutz- io momentübersetzung zu erhalten. Die einstellbaren leistungsturbine oder Teile derselben durch Differen- drei Betriebszustände ergeben zudem einen hohen tialgetriebe, Freilaufkupplungen u. dgl. miteinander Wirkungsgrad innerhalb eines weiten Drehzahlin Verbindung stehen bzw. zu bringen sind. Insbe- bereichs, so daß sich das mechanische Zusatzgetriebe sondere ist bereits eine Gasturbinenanlage bekannt- erübrigt oder zumindest stark vereinfachen läßt, geworden, die außer einer Verdichterturbine eine 15 Zum weiteren Verständnis der Erfindung dient die Nutzleistungsturbine mit gegenläufig drehbaren Leit- folgende Beschreibung eines Ausführungsbeispiels in und Laufschaufelkränzen besitzt, die miteinander Zusammenhang mit den Figuren, über ein Additionsgetriebe verbunden sind, von dem F i g. 1 ist ein schematischer Längsschnitt einer die Nutzleistung abgeleitet wird. Vorzugsweise be- erfindungsgemäßen Gasturbinenanlage, bei dem nur steht dieses Additionsgetriebe in einem Planeten- ao die oberhalb der Mittelachse liegende Hälfte dargetriebe, dessen Sonnenrad bzw. Außenzahnkranz gestellt ist;. The invention relates to a gas turbine speed of the guide vanes now their attachment with a gas generator, consisting of a flow ratio compared to the idle state of the Compressor, a compressor turbine and a combustion stator as well, as is the case with the known chamber, and with a power turbine, which is a guide vane adjustment, but change has a rotatable stator that can be braked and the flow conditions at the stare wheel are not so stareine via S Transmission device with the impeller of the core dimensions, as is otherwise the case with the impeller Power turbine is connected. would be the case. But it also succeeds through the He-It are already the most varied of gas detection, when the turbine is started up and when turbine systems became known, in which low speed a considerably increased rotary density, To obtain compressor turbine and possibly useful torque translation. The adjustable Power turbine or parts thereof due to differences in three operating states also result in a high tial gear, overrunning clutches and the like. Efficiency with one another within a wide speedin Are connected or are to be brought. Insbe- area, so that the mechanical additional gear In particular, a gas turbine system is already known - unnecessary or at least greatly simplified, become, which apart from a compressor turbine a 15 For a further understanding of the invention is used Power turbine with counter-rotating guide following description of an embodiment in and rotor blade rings, which are related to the figures, are connected via an addition gear, from which F i g. 1 is a schematic longitudinal section of a the useful power is derived. Preferably in the gas turbine system according to the invention in which only If this addition gear is in a planetary gear ao the half lying above the central axis, whose sun gear or outer ring gear is set;

mit den beiden Schaufelkränzen und dessen die Pia- Fig. 2 zeigt die Geschwindigkeitsdiagramme fürwith the two blade rings and their pia- Fig. 2 shows the speed diagrams for

netenräder tragender Steg mit der Abtriebswelle ver- den Austritt des Leitrades entsprechend verschiede-The web carrying the center gears with the output shaft displaces the outlet of the stator according to different

bunden ist. Der eine oder der andere der beiden nen Betriebszuständen;is bound. One or the other of the two operating modes;

Schaufelkränze kann dabei gebremst werden. Diese 35 Fig. 3 stellt eine.dazugehörige Verlustkurve dar.Bucket rings can be braked. This Fig. 3 represents a corresponding loss curve.

und weitere der bekannten Anlagen erlauben es, die Die in Fig. 1 dargestellte Gasturbinenanlage be-and other known systems allow the gas turbine system shown in FIG.

Drehrichtung der Abtriebswelle zu verändern und/ sitzt einen Verdichter K, eine Brennkammer BK undTo change the direction of rotation of the output shaft and / sits a compressor K, a combustion chamber and BK

oder das Anfahrdrehmoment bzw. den Anfahrwir- eine Verdichterturbine KT, welche zusammen denor the starting torque or the starting we a compressor turbine KT, which together the

kungsgrad der Turbine zu erhöhen. Gaserzeuger der Anlage bilden. Das die Turbine KT Aufgabe der Erfindung ist es hingegen, über einen 30 verlassende Gas tritt in eine Nutzleistungsturbine mitto increase the efficiency of the turbine. Form the plant's gas generator. The task of the invention, however, is for the turbine KT to enter a power turbine via a gas that leaves it

weiten Drehzahlbereich einen wirtschaftlichen Be- einem drehbaren Leitrad D und einem Laufrad T ein. A rotatable stator D and an impeller T are economically viable in a wide speed range.

trieb der Anlage und ein hohes Drehmoment dadurch Das Leitrad D wird von einer Hohlwelle 1 getragen,drive the system and a high torque thereby The stator D is carried by a hollow shaft 1,

zu erzielen, daß vor allem die Anströmverhältnisse und das Laufrad T ist auf einer Welle 2 angeordnet,to achieve that above all the flow conditions and the impeller T is arranged on a shaft 2,

des Laufrades der Nutzleistungsturbine bei praktisch die durch die Hohlwelle 1 geführt ist. Bei dem darallen vorkommenden Drehzahlen desselben günstig 35 gestellten Ausführungsbeispiel ist die Anlage mitof the impeller of the power turbine which is practically guided through the hollow shaft 1. With that one Occurring speeds of the same favorable 35 provided embodiment is the system with

gestaltet werden, d. h., daß der Anströmwinkel in Anzapfschlitzen SP zum Abblasen von Luft und Gasbe designed, ie that the angle of incidence in tapping slots SP for blowing off air and gas

relativ engen Grenzen konstant gehalten wird. ausgerüstet, die unter bestimmten Betriebsbedingun-relatively narrow limits is kept constant. equipped, which under certain operating conditions

Es ist bereits bekannt, zu diesem Zweck den gen dazu Verwendung finden, ein »Pumpen« desIt is already known that the gene can be used for this purpose, a "pumping" of the

Schaufelwinkel eines ruhenden Leitrades verstellbar Verdichters zu vermeiden.Avoid blade angle of a stationary stator adjustable compressor.

zu machen, doch erfordern solche Turbinen immer 40 Die Hohlwelle 1 des Leitrades ist über einen Frei-to make, but such turbines always require 40 The hollow shaft 1 of the stator is via a free

noch das übliche verhältnismäßig aufwendige mecha- lauf F mit einem ersten Ritzel 3 und die Welle 2 desnor the usual, relatively complex mechanism F with a first pinion 3 and the shaft 2 of the

nische Zusatzgetriebe, um unter tragbarem Wirkungs- Laufrades ist unmittelbar mit einem zweiten Ritzel 4 |niche additional gear to be able to work under portable impeller is directly with a second pinion 4 |

grad einen verhältnismäßig weiten Drehzahlbereich verbunden, das einen kleineren Durchmesser besitztgrad connected a relatively wide speed range, which has a smaller diameter

an der Abtriebswelle erreichen zu können — von als das erste Ritzel 3. Die beiden Ritzel bilden Teileon the output shaft - from than the first pinion 3. The two pinions form parts

der Umschaltmöglichkeit für Vorwärts- und Rück- 45 eines Zahnradgetriebes, das weiter zwei Zahn- ,the switching option for forward and reverse 45 of a gear transmission, which also has two tooth,

wärtsfahrt ganz abgesehen. kränze 5 und 6, ein Zwischenrad 7 und ein Zahnrad- :not to mention going upwards. wreaths 5 and 6, an intermediate gear 7 and a gear wheel-:

Die gestellte Aufgabe wird erfindungsgemäß in- paar 8 besitzt, die auf einem gemeinsamen, festdessen dadurch gelöst, daß insgesamt drei Betriebs- stehenden Steg gelagert sind. Das Zahnradpaar 8 zustände zur Auswahl stehen, bei deren jedem gün- besteht aus zwei fest miteinander verbundenen Zahnstigste Anströmverhältnisse des Turbinenlaufrades 50 rädern 8a und 8b mit unterschiedlichem Durchmes- , vorliegen. Die erfindungsgemäße Gasturbinenanlage ser, wobei das Zahnrad 8a mit dem größeren Durchist dadurch gekennzeichnet, daß mit der Übertra- messer sowohl mit dem zweiten Ritzel 4 als auch gungseinrichtung bzw. mit dem Leitrad der Nutz- mit dem Zwischenrad 7 kämmt. Das Zwischenrad 7 leistungsturbine ein Freilauf, eine Bremse und eine steht weiterhin mit dem ersten Ritzel 3 im Eingriff Kupplung verbunden sind, welche drei Elemente in 55 und besitzt zu diesem Zweck eine größere Breite. Abhängigkeit von der Drehzahl der mit dem Laufrad Das Zahnrad 8 b kleineren Durchmessers des Zahnder Nutzleistungsturbine starr gekoppelten Abtriebs- radpaares 8 kämmt mit dem Zahnkranz 6, der auf welle so steuerbar sind, daß drei Betriebszustände der Abtriebswelle 9 der Anlage angeordnet ist. \ erreicht werden, bei deren erstem entsprechend dem Die Hohlwelle I des Leitrades D trägt ferner eine niedrigsten Drehzahlbereich der Abtriebswelle das 60 Bremstrommel 10, die mit einem Bremsband B in ; Leitrad sich gegenläufig zu dem Laufrad dreht, bei der Weise zusammenwirkt, daß durch sie die Hohl- j derem zweitem entsprechend einem mittleren Dreh- welle 1 festgehalten werden kann. Ferner ist die j zahlbereicli der Abtriebswelle das Leitrad stillgesetzt Bremstrommel 10 mit einer Reibungskupplung L j ist und bei deren drittem entsprechend dem höchsten verbunden, mittels derer die Bremstrommel 10 und Drchzahlbereich der Abtriebswelle das Leitrad von 65 damit die Hohlwelle 1 mit dem mit dem breiten dem Laufrad mit gegenüber diesem verminderter Zwischenrad 7 kämmenden Zahnkranz 5 verbunden Geschwindigkeit gleichsinnig mitgeführt wird. werden kann. Zwar verschlechtern sich infolge der U in fangs- Die beschriebene Anordnung findet besondersAccording to the invention, the problem posed is achieved in pairs of 8, which are achieved on a common, fixed bridge in that a total of three stationary webs are supported. The gear pair 8 states are available for selection, each of which consists of two permanently connected toothed flow conditions of the turbine runner 50, wheels 8a and 8b with different diameters. The gas turbine system according to the invention, wherein the gear wheel 8a with the larger diameter is characterized in that the utility gear meshes with the intermediate gear 7 with the transmission both with the second pinion 4 and the transmission device or with the stator. The intermediate gear 7 power turbine has a freewheel, a brake and a clutch is still connected to the first pinion 3 in engagement, which three elements in 55 and has a greater width for this purpose. Depending on the speed of the gear wheel 8 b smaller diameter of the Zahnder power turbine rigidly coupled output wheel pair 8 meshes with the ring gear 6, which are controllable on the shaft so that three operating states of the output shaft 9 of the system is arranged. \ are achieved in the first according to the The hollow shaft I of the stator D also carries a lowest speed range of the output shaft the 60 brake drum 10, which is connected to a brake band B in; The stator rotates in the opposite direction to the impeller, cooperating in such a way that it can hold the hollow of the second corresponding to a central rotating shaft 1. Furthermore, the j number range of the output shaft is stopped, the idler brake drum 10 is connected to a friction clutch L j and the third is connected to the highest, by means of which the brake drum 10 and the idler range of the output shaft, the idler wheel of 65 so that the hollow shaft 1 with the one with the wide one Impeller with opposite this reduced intermediate wheel 7 meshing ring gear 5 connected speed is carried along in the same direction. can be. Although deteriorate as a result of the U in catch- The described arrangement takes place particularly

Claims

! 3 4! 3 4

ι-! advantageous for driving motor vehicles Ver of the impeller, in which when stationary

-sj turn. The way in which they work is described below: Guide wheel D the maximum efficiency is achieved,

η! wrote. In Fig. 2 under the letters A, B, C are the

■ h \ While the motor vehicle is starting, there are three different operating states which, as the running wheel grows - "-; the brake B and the clutch L are disengaged.

• dj and the stator D and the impeller T rotate given. The speed diagrams correspond

r- j in opposite directions, with the accordingly opposite rotation of the stator and

-Ί \ torques of the two shafts 1 and 2 via the stationary stator in Figs. 2A and 2B,

ι- j gear pair 8 transmitted to the output shaft 9 while Fig. 2C that operating state ann ' will. Due to the fact that the gears are io, in which the stator through the impeller in with

η! 8 "and 86 have different diameters, this is driven in the same direction.

1- \ place at the same time a reduction in the overall speaking Fig. 2A turn the two wheels in

> e speed instead. During acceleration in the opposite direction of rotation with a circumferential

In this operating state, the efficiency grows at a speed that is half as great as the above j increasing speed until a peripheral speed U ₇ * mentioned is reached. How yourself

in j maximum. With a further increase in the speed, the relative speed W _{7 of} the gas is constant

On the other hand, efficiency begins to decrease. when entering the impeller perpendicular to the

2r j If the maximum efficiency under the direction of movement of the turbine blades. 2 B

ir! speed corresponding to the opposite rotation, the stator D stands still, and the impeller T rotates r- ι speed is exceeded, the stator D through so with the peripheral speed U ₇ *. Also in

; Engaging the brake B braked. From then on, the relative speed W _{7 is available in this case}

Jr; the power turbine works as a simple one perpendicular to the direction of movement of the blades.

1- I-wheeled turbine, with the efficiency initially. In the third case, C, the peripheral speed j increases again with increasing speed, the impeller T is equal to 2 U ₇ *, while the peripheral speed

r. to then exceed a maximum value. Now the speed of the stator D is equal to U ₇ * . In spite of

2- the brake B is released and the clutch L is brought into engagement at the high peripheral speed of the impeller d j, so that the stator D through the gas hits the turbine blades at right angles- ■ n j impeller T in the same direction as the latter Hg whose direction of movement is driven due to the T. This becomes a further operational fact that the stator reaches state in the same direction during which the operating device rotates as the impeller of the turbine.

n. degree in the same way again with increasing Fig. 3 gives a loss curve for a turbine

n, speed increases. Blading according to FIG. 2 at. f _{m (lx} denotes

; t, It follows from the above that three lines are the maximum permissible flow loss and / ₀

r- \ different operating states occur, which result in the minimal flow loss of the blading,

it is permissible to select the operating state that 35 In the example shown, the loss

at the momentary load and speed its lowest value at an entry angle ß ₀

efficiency brings with it the highest degree of efficiency. To about 90 °, while the loss

Setting of the various operating states of the permissible values with entry angles of less

System can be provided with automatic means when ß _t or more than ß exceeds,

-i- For example, a hydraulic 40 known per se. A comparison of FIGS. 2 and 3 shows

Tax system. before that the loss is below its lowest value

4 In the transition from opposite rotation to the operating state corresponding to FIG. 2B,

nt standstill or rotation in the same direction, the guide at which the guide wheel D stands still. Would that

ie j rad D can be decelerated to a standstill. Will idler also according to the operating conditions

n- stand still between shaft 1 and the fixed door- 45 Fig. A2 and 2C, the entry

In the inner housing a hydrodynamic brake pre-angled the value ß _x or: ß. ₂ . Under these circumstances

t- J see, the main part of the kinetic energy, the loss in the impeller T would be very high. By doing

8 j of the stator D by filling this brake, the stator D can be turned in the opposite direction to

-i- \ be consumed. In this case, the friction or in the same direction with the impeller of

s- ι brake received considerably smaller dimensions than 50 turbine rotates, it is also among these two

n- if it were to be used alone, and only needs operating states possible, the gas under right

-H ! to be designed in such a way that they allow the impeller to come up to the fixed angle and on

7 \ stator D counter torque exerted to absorb the loss in the impeller T in this way

ff j inen is able. to bring its lowest value.
3rd! Is such a hydrodynamic brake available?
■>: see, it can also be used as an additional vehicle

uf brake can be used if the system is based on patent claims:

is in the third operating state, d. H. if the

ie the clutch L is engaged. 1. Gas turbine plant with a gas generator,

in j In Fig. 2 are speed diagrams of the 60 consisting of a compressor, a compressor

ύ- flow between the stator D and the running turbine and a combustion chamber, and with one

ie j rad T in the three different operating states power turbine, which has a rotating stator

L j of the system reproduced. The letter U has, which can be braked and via a transmission

id i records the circumferential speed, W and C transmission device with the impeller of the utility

-π j give the relative or absolute speed 65 power turbine is connected, thereby

'Λ \ of the gas, where the indices D and T denote the reference that with the transfer

on the stator or the impeller of the turbine device (3, 4, 5, 6, 7, 8) or with a di-in stator

rs put. U ₁ * gives that circumferential speed (D) of the Nutzlcistimgsturbinc a freewheel (F),

a brake (S) and a clutch (L) are connected, which three elements can be controlled depending on the speed of the output shaft (9) rigidly coupled to the impeller (T) of the power turbine so that three operating states are achieved the first of which, corresponding to the lowest speed range of the drive shaft, the stator (D) rotates in the opposite direction to the impeller (T) , in the second of which the stator (D) is stopped corresponding to a medium speed range of the output shaft, and the third of which corresponds to the highest speed range of the output shaft the stator (D) is carried along in the same direction by the impeller (T) at a speed that is reduced compared to this.

2. Gas turbine plant according to claim 1, characterized in that the transmission device (3, 4, 5, 6, 7, 8) has two pinions (3, 4) of different diameters, of which the ao one (3) with the hollow shaft (1 ) of the stator (D) and the other (4) is connected to the shaft (2) of the impeller (T) of the power turbine, so that the transmission device also has at least one intermediate wheel (7) and a pair of gears (8 ) and that the intermediate gear (7) is in engagement with the larger first pinion (3) and, moreover, lengthened, also meshes with the gear pair (8) which in turn meshes with the smaller, second pinion (4)

3. Plant according to claim 2, characterized in that each pair of gears (8) with his larger gear (8 a) with the second pinion (4) and the intermediate gear (7) and with his smaller gear (86) with an internal gear rim (6) arranged on the output shaft (9) or a spur gear is in mesh.

4. Plant according to claim 2 or 3, characterized in that the freewheel (F) between the first pinion (3) and the stator (D) is arranged through which a power transmission only from the stator to the transmission device (3, 4, 5, 6, 7,8) is possible.

5. Installation according to one of the preceding claims, characterized in that the drum (10) of the brake (B ) is in communication with the stator (D).

6. Plant according to claim 5, characterized in that the coupling (L) between the Idler wheel (D) and an external ring gear (5) is arranged, which is connected to each intermediate wheel (7) is in engagement, which meshes with the first pinion (3) assigned to the stator.

7. Installation according to one of the preceding claims, characterized in that the transmission device (3, 4, 5, 6, 7, 8) together with the freewheel (F), the brake (B) and the clutch (L) on the side of the Compressor (K) of the system is arranged and that the shaft (2) of the impeller (T) of the power turbine is passed through the shaft of the stator (D).

1 sheet of drawings