Method for barring a rotor of a turbomachine and barring apparatus for conducting such method

Abstract

A method for barring a rotor of a thermally loaded turbomachine includes stopping normal operation of the turbomachine; providing a barring device for rotating the rotor about a machine axis; coupling the barring device to the rotor; letting the rotor cool down during cool down of the rotor rotating the rotor by means of the barring device. A damage of the machine due to thermally induced buckling during the barring process is avoided by consecutively determining the force or torque applied to the rotor by the barring device for rotating the rotor and/or the circumferential speed of the rotor during barring. The rotation of the rotor is controlled by means of the barring device in dependence of the determined force or torque and/or circumferential speed in order to reduce a bending or imbalance of the rotor, which is due to a nonuniform temperature distribution on the rotor during cool down.

Claims

1. A method for barring a rotor of a thermally loaded turbomachine, comprising: stopping normal operation of said turbomachine; providing a barring device for rotating said rotor about a machine axis; coupling said barring device to said rotor; and providing cool down of said rotor; wherein during cool down of said rotor: rotating said rotor by means of said barring device; determining consecutively by measurement, a force or torque applied to said rotor by said barring device for rotating said rotor and/or the circumferential speed of the rotor during barring; identifying a position of a bending or imbalance of said rotor based on the force or torque applied to said rotor and/or the circumferential speed of the rotor; and controlling the rotation of said rotor by means of said barring device in dependence of said determined force or torque and/or circumferential speed in order to reduce a bending or imbalance of said rotor, which is due to a nonuniform temperature distribution on said rotor during cool down, wherein said barring device includes a shaft, a pin, and a piston, the barring device initiating a barring action on the rotor by generating, via the pin, a reciprocating movement of rotation of the shaft to drive the piston for engagement of the rotor.

2. The method according to claim 1, wherein the bending or imbalance of said rotor is caused by a nonuniform circumferential temperature profile outside of said rotor, and that said rotor is rotated by said barring device such that said nonuniform temperature distribution on said rotor is reduced by said nonuniform circumferential temperature profile outside of said rotor.

3. The method according to claim 2, wherein said rotor is continuously rotated by said barring device, and that the circumferential speed is varied in dependence of said determined force or torque and/or circumferential speed.

4. The method according to claim 1, wherein said rotor is rotated by said barring device in an incremental fashion.

5. The method according to claim 4, wherein said rotor is rotated by said barring device using a ratchet and pawl mechanism, wherein said pawl mechanism is engaged by said piston.

6. The method according to claim 1, wherein said barring device is driven by an electric motor, and that the current of said motor is measured to determine said force or torque applied to said rotor.

7. The method according to claim 1, wherein said barring device is driven by a hydraulic pressure, and that said hydraulic pressure is measured to determine said force or torque applied to said rotor.

8. The method according to claim 1, wherein said turbomachine is a stationary gas turbine.

9. A barring apparatus for conducting the method according to claim 1, said barring apparatus comprising a barring device with a barring drive coupled to the rotor of said turbomachine, and a control unit provided for controlling said barring device, wherein said control unit receives signals from a speed sensor and/or said barring drive of said barring device.

10. The barring apparatus according to claim 9, wherein the speed sensor provided is configured to sense the circumferential speed of said rotor.

11. The barring apparatus according to claim 9, wherein said barring drive comprises an electric motor, and that said control unit receives signals, which are related to the electric current flowing through said electric motor.

12. The barring apparatus according to claim 11, wherein said electric motor is a servo motor.

13. The barring apparatus according to claim 9, wherein said barring device comprises a barring mechanism with a pawl, which is designed to interact in a reciprocating manner with a ratchet wheel on said rotor.

14. A gas turbine comprising a barring apparatus according to claim 9.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) The present invention is now to be explained more closely by means of different embodiments and with reference to the attached drawings.

(2) FIG. 1 shows a perspective view of a stationary gas turbine with sequential combustion known in the art;

(3) FIG. 2 shows in a perspective view a barring device as part of a ratchet and pawl mechanism;

(4) FIG. 3 shows the integration of a barring device according to FIG. 2 into a gas turbine;

(5) FIG. 4 shows the ratchet and pawl mechanism involving a barring device according to FIG. 2; and

(6) FIG. 5 shows e control scheme of a barring apparatus according to an embodiment of the invention.

DETAILED DESCRIPTION

(7) FIG. 1 shows a perspective view of a stationary gas turbine with sequential combustion known in the art. The gas turbine 10 of FIG. 1, which is of the well-known type GT26, comprises a rotor 11, which rotates about a machine axis (37 in FIG. 5) and is concentrically surrounded by a casing 12. Between the casing 12 and the rotor 11 an annular hot gas channel runs from an air inlet 13 to an exhaust gas outlet 19. A compressor 14 downstream of the air inlet 13 sucks in and compresses air, which is delivered to a first combustor 15, where a first combustion of an injected fuel generates hot gas for a high pressure turbine 16 downstream of said first combustor 15.

(8) After having passed the high pressure turbine 16, the hot gas, which still contains combustion air, is used in a second combustor 17 to burn a second fuel and thereby reheat the hot gas. The hot gas leaving the second combustor 17 drives a low pressure turbine 18 and flows to the exhaust gas outlet 19 to be released either to a stack or a heat recovery steam generator in case of a combined cycle power plant CCPP.

(9) When such a gas turbine 10 is switched off after normal operation, a nonuniform circumferential temperature distribution in the hot gas channel leads to a nonuniform circumferential temperature distribution in the rotor, which tends to bend the rotor with respect to its axis due to the different thermal expansion at the different temperatures, even when the rotor is barred with a constant rotation speed during cool down.

(10) According to the idea of the present invention, rotor barring operation varies the actuator speed around the circumference to keep or to bring back the rotor of large turbomachines in straight and coaxial condition.

(11) A bending of the rotor during cool down will lead to a buckle of the rotor, to which the gravity force is acting. The gravity force on the buckle will lead to uneven rotor barring/turning actuators force around the circumferential direction. In addition, the rotation speed around the circumference of the rotor will vary.

(12) Consequently, a continuous monitoring and evaluation of the actuator force and/or the turbomachine rotor speed around the circumference shall be introduced. By this evaluation the location of the rotor buckle or the circumferential disturbance is determined. The circumferential speed will be varied. By the variation of rotational speed the available (nonuniform) surrounding circumferential temperature profile will be used to straighten the rotor back to the coaxial condition.

(13) FIG. 2 shows in a perspective view a barring device, which may be used as part of a ratchet and pawl mechanism similar to the one of document U.S. Pat. No. 4,267,740 A cited before. The barring device 20 of FIG. 2 comprises an eccentric shaft 2A, which is rotatable supported by a U-bracket angle 21 and U-bracket plate 22 of a U-bracket. The eccentric shaft is driven by a servo motor 29, which is connected to the shaft via a gear box 26 and coupling case 25. On the eccentric shaft 24 a rod 23 is arranged, which converts the rotation of the shaft 24 into a reciprocating movement driving a barring piston 31 via a rod end bearing 30. The reciprocating movement of the barring piston 31 in the barring case 32 leads to a respective movement of a pawl 33 arranged at the free end of the piston in the interior of bracket 36. As shown in detail in FIG. 4, the pawl 33, which is loaded by a spring 35, engages the teeth of a ratchet wheel 34 on the rotor during the barring action. A barring device 20 according to FIG. 2 can be integrated into the gas turbine as for example shown in FIG. 3.

(14) The servo motor 29 is equipped with a power connector 28 for being supplied with electric power, and with a signal connector 27 for receiving control signals and sending signals with regard to the actual power or current used during the barring process (see FIG. 5).

(15) Other kinds of barring devices may be used instead of the ratchet and pawl mechanism shown in FIGS. 2 to 4.

(16) To get information about the unbalance or bending of the rotor caused by the nonuniform temperature distribution the force, which is necessary for the barring process, can be measured. This actuator force or torque can be either directly measured by e.g. a force sensor arranged at the pawl, or the like, or indirectly evaluated. Indirect evaluation methods comprise measuring the current of the electrical actuator motor or the actuation medium pressure of a pneumatic or hydraulic actuator.

(17) In addition or alternatively, the circumferential speed of the rotor may be measured or determined.

(18) As said before, a continuous monitoring and evaluation of the actuator force and/or the turbomachine rotor speed around the circumference gives the necessary information of the location of a rotor buckle or a circumferential disturbance.

(19) During the cool down process the circumferential speed will be varied. By the variation of the rotational speed the available (nonuniform) surrounding circumferential temperature profile will be used to straighten the rotor back to the coaxial condition.

(20) FIG. 5 shows a simplified scheme of a respective barring arrangement. The rotor 11, the bending of which is represented by the slashed lines, rotates about the machine axis 37. The circumferential speed may be measured by speed sensors 40 and/or 41, which are positioned at parts of the rotor with different radius, thereby providing a different sensitivity due to the different circumferential speed. The signals from the speed sensors 40, 41 are fed to a control unit 42, which controls the action of the barring device 20. In this example, the barring device is of the ratchet and pawl type and has a barring mechanism 38 co-operating with ratchet wheel 34 in a manner explained before.

(21) The barring drive 39 receives control signals from the control unit 42 over a control line 44 and sends information about the electric power used over a signal line 45 back to the control unit 42. The control unit 42 may be connected to a display/control console 43 for displaying various parameters during the barring process and getting input commands at the various stages of the process.

(22) During cool down of a gas turbine as shown in FIG. 1, a temperature difference of about 80 C. may exist between upper and lower side of the turbine casing. If the rotor stood still, its upper side would be warmer resulting in buckling at the upper side.

(23) In case of such a buckling the respective side should be kept in the lower and cooler region of the gas turbine for a longer time.

(24) When the barring torque is measured or determined, this can be done by: determining the torque of an electric drive, for example via a measurement of the drive current or voltage; measuring directly the applied force, e.g. by means of a strain gauge, or the like; measuring the hydraulic pressure in a hydraulic barring drive.

(25) If the barring torque to be supplied is high, the position of the rotor buckle is on the side, where the barring torque is applied. Accordingly, this side is rotated with elevated speed through the (hotter) upper part of the casing (after a rotation of about 90), and is rotated with reduced speed through the (cooler) lower part of the casing (after a rotation of about 270).

(26) Rotation can be a continuous turning. However, the rotor turning can be accomplished by said barring device in an incremental fashion. An incremental turning is for example accomplished if said rotor is rotated by said barring device using a ratchet and pawl mechanism. For such a system the turning speed is determined by the time interval between engaging and/or pushing cycles of the ratchet and pawl mechanism, i.e. the time interval is reduced between two pushing or bearing actions is reduced to increase the turning speed. Continuous supervision or measurement for such a bearing device can mean that the force, respectively momentum is determined during the times of interaction of the ratchet and pawl mechanism.

(27) In special cases the rotor can be stopped with the buckle positioned at the lower part of the casing. The actual rotation speed during barring and a possible resting time at a certain position depend on the determined magnitude of the buckling effect, and are approximately proportional to the variation of the torque.

(28) The barring mechanism can engage the rotor shaft at any place. However, it is advantageous to place the mechanism at the cool end of the gas turbine, i.e. at the compressor side.

(29) By practicing the invention the availability of the turbomachine is increased, since rotor blockages are avoided.