JP2012092653A5 - - Google Patents

Description

Power generation system

  The present invention relates to a power generation system that drives a generator by the rotational force of a turbine, and more particularly, to a power generation system that includes a plurality of turbines and that may be partially stopped when the system is operating.

  Large ships are equipped with a power generation system that generates the power required during operation. In general, a marine power generation system drives a generator by the rotational force of a turbine. For the turbine, both a steam turbine that extracts rotational power from waste heat around the main engine that is a propulsion motor and a power turbine that extracts rotational power from a part of the exhaust gas of the main engine may be applied. In this case, a waste heat recovery system for recovering waste heat around the main engine mainly including the heat of exhaust gas is added to the power generation system (see, for example, Patent Document 1).

  When the propulsion load is low, the flow rate of the exhaust gas from the main engine becomes small, and there is a possibility that the power turbine cannot operate satisfactorily. Therefore, a power generation system has been proposed in which a steam turbine is always operated in principle when operating the system, and the power turbine is operated or stopped depending on the situation even when the system is operating (for example, Patent Documents). 2).

  Patent Document 1 discloses a power generation system including one steam turbine, one power turbine, and two generators provided corresponding to each turbine. Patent Document 2 discloses a power generation system including one steam turbine, one power turbine, and one generator, and the rotational power of two turbines can be input to one generator. A plurality of examples of power transmission systems are disclosed.

Special table 2009-532614 JP 2010-133284 A

  However, according to the power generation system of Patent Document 1, since the two power generators are provided, the entire system becomes very large. Then, the narrow engine room in the ship is greatly pressed. In particular, in the design of cargo handling vessels such as container ships, the space for cargo loading, which is the original purpose of cargo handling carriers, is primarily secured, so the space given as an engine room is extremely limited. It becomes extremely difficult to install a large system.

  According to the first power transmission system (FIG. 1) of Patent Document 2, the output shaft of the steam turbine is connected to the input shaft of the generator via a reduction gear train composed of two external gears. The output shaft is connected to the drive gear of the reduction gear train via an SSS clutch (Synchro-Self-Shifting clutch). The steam turbine and the power turbine are disposed on opposite sides in the axial direction with respect to the drive gear, and the power turbine and the generator are disposed on the same side in the axial direction with respect to the reduction gear train. According to this configuration, the entire system is enlarged in the axial direction. Moreover, since the generator is close to the power turbine in the radial direction, it is necessary to let the generator escape from the power turbine and the SSS clutch in the axial direction. For this reason, the input shaft of a generator becomes long and a shaft support structure becomes complicated.

  According to the second power transmission system of Patent Document 2 (FIG. 2), a reduction gear train composed of three external gears is provided, and the input shaft of the generator is connected to the central large-diameter gear and remains. The output shaft of the steam turbine is connected to one of the two small-diameter gears, and the output shaft of the power turbine is connected to the other via a clutch and a reduction gear train. The steam turbine and the power turbine are arranged on the same side in the axial direction with respect to the reduction gear train, and the steam turbine and the generator are arranged on the opposite sides in the axial direction on the basis of the reduction gear train. According to this configuration, when the power turbine is stopped, the gear connected to the power turbine rotates idly by the rotational force transmitted from the steam turbine even though the rotational force from the power turbine is not transmitted. When idling occurs, hammering is likely to occur in the gear, and the gear may be damaged. Moreover, since the rotational force of the steam turbine is wasted because it drives a gear that does not contribute to power transmission to the generator, the power generation efficiency of the system is deteriorated.

  The third power transmission system (FIG. 3) of Patent Document 2 is a so-called skewer type, and the output shaft of the power turbine is connected to the output shaft of the steam turbine via a clutch. When the skewering type is adopted, the dimension in the axial direction from the generator to the power turbine becomes very large.

  Therefore, the present invention prevents hammering and improves power generation efficiency in a power generation system in which the rotational force of a plurality of turbines is transmitted to a generator via a gear train and may partially stop the turbine during system operation. And it aims at suppressing the enlargement of the whole system.

  A power generation system according to the present invention is a power generation system that drives a generator by the rotational force of a turbine, the main turbine operating during system operation, a main drive gear connected to the output shaft of the main turbine, and the power generation A main reduction gear having a main driven gear connected to the input shaft of the machine and transmitting the rotation of the main driving gear to the main driven gear; and one or more auxiliary turbines operating or stopping depending on the situation when the system is operating The main reduction device further includes one or more idle gears interposed between the main drive gear and the main driven gear to transmit the rotation of the main drive gear to the main driven gear. An output shaft of a first sub turbine included in the one or more sub turbines is connected to the main driven gear, and the first sub turbine and the main turbine are axis lines with respect to the main reduction gear. In each direction Flip disposed side, and the a main turbine and the generator are disposed opposite to each other in the axial direction with respect to the said main speed reducer.

  According to the above configuration, the rotational force of the main turbine is input to the generator via the main drive gear and the main driven gear, and the rotational force of the first sub turbine is input to the generator via the main driven gear. . The main driven gear contributes to power transmission to the generator even when the first sub turbine is stopped and the generator is driven only by the rotational force of the main turbine. That is, even if the first sub turbine is stopped, there is no idle gear in the main reduction gear. Therefore, it is possible to prevent occurrence of hammering in the gear constituting the main reduction gear, and it is possible to improve the power generation efficiency by preventing wasteful consumption of the rotational force of the steam turbine.

  In addition, the first sub turbine and the main turbine are arranged on the same side in the axial direction with respect to the main reduction gear. That is, they are arranged in the radial direction. Here, since one or more idle gears are interposed between the main drive gear and the main driven gear of the main reduction gear, the main drive gear and the main driven gear are separated from each other in the radial direction. For this reason, the main turbine and the first sub turbine can be arranged without difficulty in the radial direction. Then, it is not necessary to lengthen the output shaft of the first sub turbine in order to allow the first sub turbine to escape from the main turbine in the axial direction. In addition, since the two turbines and the generator are disposed on opposite sides in the axial direction with respect to the main reduction gear, it is not necessary to lengthen the input shaft of the generator. As a result, the entire system can be reduced in size, and the shaft support structure can be prevented from becoming complicated.

  Each center of the main drive gear, the idle gear, and the main driven gear may be located on the same straight line when viewed from the axial direction.

  According to the above configuration, the distance between the centers of the main drive gear and the main driven gear can be made as long as possible. That is, the distance between the centers is the length corresponding to the sum of the radius of the pitch circle of the main drive gear, the diameter of the pitch circle of the idle gear, and the radius of the pitch circle of the main driven gear. The main drive gear and the main driven gear can be separated from each other in the radial direction.

A clutch interposed between the output shaft of the first sub-turbine and the main driven gear; and a first sub-reduction gear interposed between the output shaft of the first sub-turbine and the clutch, The first sub-reduction gear has a first sub-drive gear connected to the output shaft of the first sub-turbine, and a first sub-driven gear connected to the clutch, and rotates the first sub-drive gear. transmitted to the first secondary driven gear, said first auxiliary drive gear, before Symbol viewed from the main driven gear and said first auxiliary driven gear, may be disposed away from the main drive gear.

  According to the above configuration, since the first sub-drive gear is disposed away from the main drive gear when viewed from the first sub-driven gear, the first sub-turbine can be disposed away from the main turbine in the radial direction. it can. Thereby, a 1st sub turbine and a main turbine can be arranged in a radial direction without difficulty. In addition, since the clutch is interposed between the sub-reduction gear and the main reduction device, the gear constituting the sub-reduction gear is idled by receiving the rotational force of the main turbine when the first sub-turbine is stopped. I don't have to.

  The one or more auxiliary turbines further include a second auxiliary turbine, and the input shaft of the generator has a first input shaft portion and a second input shaft portion that extend in opposite directions in the axial direction. The first input shaft portion may be connected to the main driven gear of the main reduction gear, and the output shaft of the second sub turbine may be connected to the second input shaft portion via a clutch. .

  According to the said structure, a 2nd subturbine is arrange | positioned on the opposite side to a main turbine and a 1st subturbine in an axial direction on the basis of a generator. Thereby, it can suppress that the whole system enlarges to radial direction. Further, since the clutch is interposed between the second sub turbine and the second input shaft portion, when the second sub turbine is stopped, the output shaft and the second input shaft portion of the second sub turbine are No idle rotation of the gear due to the rotational force of the main turbine occurs.

  The one or more auxiliary turbines further include a third auxiliary turbine, and an output shaft of the third auxiliary turbine is connected to the main drive gear via a clutch, and the first auxiliary turbine and the third auxiliary turbine are connected to each other. A turbine may be arranged on the opposite sides in the axial direction with respect to the main reduction gear.

  According to the said structure, the output shaft of the 3rd sub turbine is connected to the main drive gear. For this reason, even if the third sub turbine is stopped, it is possible to prevent idling of the gears constituting the main reduction gear. In addition, since the clutch is interposed between the third sub turbine and the main drive gear, when the third sub turbine is stopped, the main shaft is connected between the output shaft of the third sub turbine and the main reduction gear. There is no occurrence of idle rotation of the gear due to the rotational force of the turbine. In addition, the third sub turbine is arranged side by side with the generator in the radial direction, but the main drive gear and the main driven gear are arranged apart from each other in the radial direction by interposing the idle gear. Can be suitably spaced apart from the generator in the radial direction. Therefore, it is not necessary to lengthen the output shaft of the third sub-turbine or the input shaft of the generator, and it is possible to prevent the entire system from becoming large in the axial direction or from complicating the shaft support structure.

  The power generation system is a power generation system mounted on a ship having one main engine, the main turbine is a steam turbine that extracts rotational power from waste heat around the main engine, and the one or more sub turbines are A power turbine that extracts the rotational force from the exhaust of the main engine may be used.

  The power generation system is a power generation system mounted on a ship having two main engines, and the main turbine is a steam turbine that extracts rotational force from waste heat around the two main engines, and The turbine is a first power turbine that extracts rotational power from one exhaust of the two main engines, and the second sub-turbine is a second power that extracts rotational power from the other exhaust of the two main engines. The power turbine may be used.

  At this time, a waste heat recovery system that recovers waste heat of the two main machines to generate steam is provided, and the waste heat recovery system recovers the heat of the exhaust of one of the two main machines. An exhaust gas economizer, a second exhaust gas economizer that recovers heat of the other exhaust of the two main engines, a steam separator for supplying steam to the steam turbine, the first exhaust gas economizer, and the second exhaust gas economizer A circulating water system for connecting an exhaust gas economizer in parallel to the steam separator.

  According to the present invention, in a power generation system in which the rotational force of a plurality of turbines is transmitted to a generator via a gear train and part of the turbine may be stopped during system operation, hammering is prevented and power generation efficiency is improved. This can improve the size of the entire system.

It is a conceptual diagram which shows the whole structure of the electric power generation system which concerns on 1st Embodiment of this invention. FIG. 2 is a cross-sectional view of a main reduction gear and a sub reduction gear cut along the line II-II in FIG. 1. It is a conceptual diagram which shows the whole structure of the electric power generation system which concerns on 2nd Embodiment of this invention. It is a conceptual diagram which shows the whole structure of the electric power generation system which concerns on 3rd Embodiment of this invention. It is a conceptual diagram which shows the structure of the power transmission system of the electric power generation system which concerns on 4th Embodiment of this invention. It is a conceptual diagram which shows the structure of the power transmission system of the electric power generation system which concerns on 5th Embodiment of this invention.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. In addition, the same code | symbol is attached | subjected to the element which is the same or it corresponds through all the figures, and the overlapping description is abbreviate | omitted.

[First Embodiment]
FIG. 1 is a conceptual diagram showing an overall configuration of a power generation system 100 according to the first embodiment of the present invention. As shown in FIG. 1, a power generation system 100 is mounted on a ship equipped with a marine diesel engine 1 (hereinafter simply referred to as “engine”) as a main engine that is a propulsion motor.

  The power generation system 100 includes a generator 2, a power turbine 4 that extracts rotational force from the exhaust gas of the engine 1 that is about to be discharged out of the ship by the exhaust system 3, and waste around the engine 1 that is recovered by the waste heat recovery system 5. A steam turbine 6 that extracts the rotational force from the heat, and a power transmission system 7 that transmits the rotational force of the turbines 4 and 6 to the generator 2 are provided. The generator 2 is driven by the rotational force of the turbines 4 and 6 and generates electric power required in the ship.

  The generator 2 is a so-called steam turbo generator with a marine power turbine. That is, the steam turbine 6 functions as a main turbine, and always operates in principle when the system is to be operated (that is, when the generator 2 is to be driven). The power turbine 4 functions as a sub-turbine, and operates or stops as appropriate depending on the situation such as the level of power load and the level of propulsion load even when the system is operating.

  The power generation system 100 according to the present embodiment is mounted on a ship including one engine 1 and includes one generator 2, one steam turbine 6, and one power turbine 4. Hereinafter, the exhaust system 3, the waste heat recovery system 5, and the power transmission system 7 in the power generation system 100 will be described in order.

(Exhaust system)
The exhaust system 3 includes an exhaust pipe 11 for guiding exhaust gas from the engine 1 to an exhaust outlet such as a chimney. A supply passage 12 is branched from the exhaust pipe 11 so that a part of the exhaust gas can be supplied to the gas inlet of the power turbine 4 through the supply passage 12. The power turbine 4 is a gas turbine having a plurality of moving blades, and rotates the moving blades with the exhaust gas supplied to the gas inlet to generate a rotational force on the output shaft 61. A reflux passage 13 is connected to the gas outlet of the power turbine 4. The gas discharged from the gas outlet of the power turbine 4 is returned to the exhaust pipe 11 through the reflux passage 13.

  On-off valves 14 and 15 are provided in the supply passage 12 and the reflux passage 13, respectively. The on-off valves 14 and 15 are opened in a situation where the power turbine 4 should be operated. On the other hand, the on-off valves 14 and 15 are closed in a situation where the power turbine 4 should be stopped, and block the flow of exhaust gas to the power turbine 4.

(Waste heat recovery system)
The waste heat recovery system 5 mainly includes an exhaust gas economizer 21, a high pressure drum 22 (high pressure side steam separator), a low pressure drum 23 (low pressure side steam separator), a high pressure circulating water system 24, a steam system 25, a low pressure A circulating water system 26 and an air-mixing system 27 are provided.

  The exhaust gas economizer 21 is interposed between the exhaust pipe 11 and the exhaust outlet, and constitutes a part of the exhaust system 3. The exhaust gas economizer 21 includes an inlet pipe 31, a high-pressure evaporator 32, an intermediate pipe 33, a low-pressure evaporator 34, and an outlet pipe 35 in order from the upstream side. The inlet pipe 31 is connected to the exhaust pipe 11 and guides the exhaust gas from the engine 1 to the high-pressure evaporator 32. The intermediate pipe 33 guides the exhaust gas after heat exchange in the high-pressure evaporator 32 to the low-pressure evaporator 34. The outlet pipe 35 guides the exhaust gas after heat exchange in the low-pressure evaporator 34 to the exhaust outlet.

  The high-pressure drum 22 stores water supplied from a water supply system (not shown) as circulating water. The high-pressure circulating water system 24 includes a line 24 a that connects the high-pressure drum 22 to the high-pressure evaporator 32 and a line 24 b that connects the high-pressure evaporator 32 to the high-pressure drum 22. The steam system 25 has a line 25a that connects the high-pressure drum to the steam inlet of the steam turbine. When the pump 24P on the line 24a is operated, the circulating water in the high-pressure drum 22 is sent to the high-pressure evaporator 32 via the line 24a, and the sent circulating water is exchanged with exhaust gas in the high-pressure evaporator 32. It becomes steam. The circulating water is returned to the high-pressure drum 22 through the line 24 b in a gas-liquid mixed state, and the returned circulating water is separated into vapor and liquid in the high-pressure drum 22. The steam in the high pressure drum 22 is supplied to the steam inlet of the steam turbine 6 through a line 25a.

The low-pressure drum 23 can store water supplied from a water supply system (not shown) as circulating water. The low-pressure circulating water system 26 includes a line 26 a that connects the low-pressure drum 23 to the low-pressure evaporator 34, and a line 26 b that connects the low-pressure evaporator 34 to the low-pressure drum 23. The mixture system 27 has a line 2 7 a that connects the low-pressure drum 23 to the mixture inlet of the steam turbine 6. When the pump 26P on the line 26a is operated, the circulating water in the low-pressure drum 23 is sent to the low-pressure evaporator 34 via the line 26a, and the sent circulating water is exchanged with exhaust gas in the low-pressure evaporator 34. It becomes steam. Circulating water is returned to the low pressure drum 2 3 through a line 26b in the gas-liquid mixed state, returned circulation water is separated into vapor and liquid in the low pressure drum 23. The steam in the low-pressure drum 23 is supplied to the mixture inlet of the steam turbine 6 through the line 27a.

  The steam turbine 6 is a multistage steam turbine having a plurality of moving blades, and rotates the moving blades by steam from the high pressure drum 22 supplied to the steam inlet and steam from the low pressure drum 23 supplied to the mixed gas inlet. To generate a rotational force on the output shaft 41. The steam system 25 has a valve unit 25V that controls whether or not the steam supplied to the steam inlet via the line 25a is routed through the superheater 36. The superheater 36 is provided in the inlet pipe 31 of the exhaust gas economizer 21. When the steam passes through the superheater 36, the temperature of the steam can be raised by heat exchange with the exhaust gas. The air-mixing system 27 has a valve unit 27V that adjusts the flow rate of steam supplied to the air-fuel mixture inlet via the line 27a. By controlling the operations of these valve units 25V and 27V, the rotational force generated in the output shaft 41 can be adjusted according to the load or the like.

  Note that the steam supplied to the steam turbine 6 is discharged from the steam outlet, condensed by a condenser (not shown), and supplied to the high-pressure drum 22 and the low-pressure drum 23 along the water supply system. The feed water system includes a feed water heater (not shown) that heats feed water using waste heat around the engine 1 such as heat radiation from the supply air to the engine 1 as a heat source. Further, the high-pressure drum 22 and the low-pressure drum 23 are provided with heaters 22a and 23a for heating the circulating water stored by using a part of the steam sent to the steam system 25 as a heat source (see the US mark in the figure). ing.

  In this way, the waste heat recovery system 5 recovers the heat of the exhaust gas with the exhaust gas economizer 21 and also recovers the heat released from the supply air, generates steam with the recovered heat, and generates the steam turbine 6 with the generated steam. To drive. Since the steam turbine 6 is driven by the steam generated by using the waste heat around the engine 1 mainly including the heat of the exhaust gas as a heat source, the power generation system 100 can be suitably saved in energy.

(Power transmission system)
FIG. 1 schematically shows the arrangement of the power transmission system 7 in plan view. The power transmission system 7 is configured so that the rotational force of one steam turbine 6 and the rotational force of one power turbine 4 can be input to one generator 2.

  The output shaft 41 of the steam turbine 6 and the input shaft 44 of the generator 2 are arranged in parallel to each other, and the input shaft 44 of the generator 2 is connected to the rotating shaft 42 via a coupling 43. The output shaft 41 is connected to the rotary shaft 42 via the main speed reducer 50. The main speed reducer 50 includes a main drive gear 51 with an output shaft 41 fixed, a main driven gear 52 with a rotation shaft 42 fixed, and one idle gear interposed between the main drive gear 51 and the main driven gear 52. 53 is a reduction gear train. These three gears 51 to 53 are all gears having external teeth, and the number of teeth of the main drive gear 51 is smaller than the number of teeth of the main driven gear 52. The idle gear 53 meshes with the main drive gear 51 and meshes with the main driven gear 52.

On the other hand, the output shaft 61 of the power turbine 4 is disposed in parallel with the output shaft 41 of the steam turbine 6, the input shaft 44 of the generator 2, and the rotating shaft 63. The output shaft 61 is connected to the rotating shaft 63 via the sub reduction gear 62. The sub reduction gear 62 is a reduction gear train having a sub drive gear 64 with the output shaft 61 fixed and a sub driven gear 65 with the rotation shaft 63 fixed. These two gears 6 4 , 6 5 are both gears having external teeth, and the number of teeth of the auxiliary drive gear 64 is smaller than the number of teeth of the auxiliary driven gear 65. The sub drive gear 64 and the sub driven gear 65 are meshed with each other in the radial direction. The rotating shaft 63 is connected to the main driven gear 52 of the main reduction gear 50 via the SSS clutch 66.

  According to the above configuration, the rotational force of the steam turbine 6 is transmitted to the input shaft 44 of the generator via the main drive gear 51, the idle gear 53, the main driven gear 52, the rotary shaft 42, and the coupling 43 in this order. . Since the steam turbine 6 functions as a main turbine as described above, these members 42 to 44 and 51 to 53 are always rotated by the rotational force of the steam turbine 6 in principle when the system is operating. This contributes to transmitting power to the generator 2.

  On the other hand, when the power turbine 4 is operating, the rotational force of the power turbine 4 passes through the sub drive gear 64, the sub driven gear 65, the rotary shaft 63 and the SSS clutch 66 in this order, and the main driven gear 52 and the rotary shaft 42. Is transmitted to. Even when the power turbine 4 is stopped, the main driven gear 52 is a gear that contributes to transmitting the rotational force of the steam turbine 6 to the generator 2. Does not exist. Further, when the power turbine 4 is stopped, the difference between the rotational speed of the main driven gear 52 and the rotational speed of the sub driven gear 65 becomes significant. The power transmission path with the machine 62 is disconnected. For this reason, the gear which comprises the sub reduction gear 62 does not run idle by the rotational force of the steam turbine 6. FIG.

  Next, the arrangement of the power transmission system 7 will be specifically described. The output shaft 41 and the rotary shaft 42 of the steam turbine 6 extend in the axial direction opposite to each other with respect to the main speed reducer 50, and the rotary shaft 42 and the rotary shaft 63 are based on the main speed reducer 50. Extending in opposite directions in the axial direction. Therefore, the generator 2 is disposed on the opposite side in the axial direction from the steam turbine 6 and the power turbine 4 with respect to the main reduction gear 50. For this reason, it is not necessary to lengthen the input shaft 44 of the generator 2 in order to release the generator 2 from the turbine in the axial direction.

Further, the steam turbine 6 and the power turbine 4 are arranged on the same side in the axial direction with respect to the main reduction gear 50. That is, the steam turbine 6 and the power turbine 4 are arranged so as to be aligned in the radial direction of the main reduction gear 50. On the other hand, the main reduction gear 50 according to this embodiment includes a main drive gear 51 the output shaft 41 is connected to the steam turbine 6, between the main driven gear 52 the output shaft 61 of the power turbine 4 is connected One idle gear 53 is interposed. For this reason, the main drive gear 51 and the main driven gear 52 are arranged away from each other in the radial direction. Then, the sub-reducer 62 is interposed between the output shaft 61 and the main driven gear 52 of the power turbine 4. The sub driven gear 65 is arranged on the same axis as the main driven gear 52, while the sub driving gear 64 is arranged so as to be away from the main driving gear 51 when viewed from the main driven gear 52 and the sub driven gear 65. ing. By such an idle gear 53 and the sub-reduction gear 62, the steam turbine 6 and the power turbine 4 can be arranged away from each other in the radial direction of the main reduction gear 50 and the sub-reduction gear 62, and the radial direction is impossible. Can be arranged without any problems. Then, it is not necessary to lengthen the output shaft 41 of the steam turbine 6, the output shaft 61 of the power turbine 4, or the rotating shaft 63 in order to allow the power turbine 4 to escape from the steam turbine 6 in the axial direction. In addition, since the rotating shaft 63 and the output shaft 61 of the power turbine 4 extend on the opposite sides in the axial direction with respect to the sub reducer 62, the power turbine 4 is connected to the main reducer 50 or the generator 2. There will be no interference. As described above, since the interaxial distance between the steam turbine 6 and the power turbine 4 can be increased, the steam turbine 6 and the power turbine 4 are arranged so as to overlap in a side view without interfering with each other. Is possible.

  As described above, according to the power transmission system 7 according to the present embodiment, since there is no idle gear, it is possible to prevent hammering from occurring in the gear and to extend the life of the power transmission system 7. be able to. Further, it is possible to prevent the rotational force of the steam turbine 6 from being wasted, and to improve the power generation efficiency of the power generation system 100. Furthermore, the dimensions on both sides in the axial direction centering on the main reduction gear 50 are all compact. Therefore, the enlargement of the entire system can be suppressed. Further, a shaft support structure between the main speed reducer 50 and the generator 2, a shaft support structure between the main speed reducer 50 and the steam turbine 6, and a shaft support structure between the main speed reducer 50 and the power turbine 4. Can be prevented from becoming complicated.

  2 is a cross-sectional view of the main reduction gear 50 and the sub reduction gear 62 shown cut along the line II-II in FIG. The idle gear 53 of the main reduction gear 50 is provided on an idle shaft 45 disposed between the output shaft 41 and the rotary shaft 42 of the steam turbine 6. The idle shaft 45 may be a fixed shaft or a rotating shaft. When the shaft is a fixed shaft, the idle gear 53 is rotatably supported by the idle shaft 45 via a needle bearing or the like. When it is a rotating shaft, the idle gear 53 is fixed to the idle shaft 45 and rotates integrally with the idle shaft 45.

The rotation center of the main drive gear 51 (the axis of the output shaft 41), the rotation center of the idle gear 53 (the axis of the idle shaft 45), and the rotation center of the main driven gear 52 (the axis of the rotation shaft 42). Are arranged on the same straight line. Further, the rotation center of the main driven gear 52 coincides with the rotation center of the sub driven gear 65 (the axis of the rotation shaft 63), and the rotation center of the sub driven gear 65 and the rotation center of the sub drive gear 64 (output shaft 61). Are also arranged on the same straight line. For this reason, the distance L between the output shaft 41 of the steam turbine 6 and the output shaft 61 of the power turbine 4 is the radius (r1) of the pitch circle of the main drive gear 51 and the diameter (2 of the pitch circle of the idle gear 53). Corresponds to the sum of r2), the radius of the pitch circle of the main driven gear 53 (r3), the radius of the pitch circle of the secondary driven gear 65 (r4), and the radius of the pitch circle of the secondary drive gear 64 (r5). (L = r1 + 2 · r2 + r3 + r4 + r5). Thus, the inter-axis distance L between the output shaft 41 of the steam turbine 6 and the output shaft 61 of the power turbine 4 constitutes the size of the three gears 51 to 53 constituting the main reduction gear 50 and the auxiliary reduction gear 62. The size of the two gears 64 and 65 to be used is maximized. In other words, the gear size is minimized when a certain distance between the axes is to be secured, so that the gear can be easily manufactured and the gear manufacturing cost can be reduced.

  However, such a shaft layout is an example, and the inter-shaft distance between the output shaft 41 of the steam turbine 6 and the output shaft 61 of the power turbine 4 and the reduction ratio to be set in the main reduction gear 50 (roughly r3 / r1). ), The reduction gear ratio (roughly r4 / r5) to be set in the sub-reduction gear 62, and the minimum gear size required to withstand the rotational force input to the main reduction gear 50 and the sub-reduction gear 62 The position of the axis of the idle shaft 45 may be changed according to the relationship between the two. That is, the line connecting the axis of the output shaft 41 and the axis of the idle shaft 45 and the line connecting the axis of the rotary shaft 42 and the axis of the idle shaft 45 may form a V shape. . Further, an idle gear may be provided in the sub reduction gear 62.

[Second Embodiment]
FIG. 3 is a conceptual diagram showing an overall configuration of a power generation system 200 according to the second embodiment of the present invention. As shown in FIG. 3, the power generation system 200 according to the present embodiment is mounted on a ship equipped with one engine 1, and includes one generator 2, one steam turbine 6, and two powers. Turbines 4A and 4B are provided. For this reason, the exhaust system 203 is configured to be able to supply exhaust gas from one engine 1 to each of the two power turbines 4A and 4B, and the power transmission system 207 includes the steam turbine 6 and the first power turbine 4A. And each rotational force of the 2nd power turbine 4B is comprised so that input to the one generator 2 is possible. The generator 2 is a steam turbo generator with an inboard power turbine, and the configurations of the waste heat recovery system 5 and the steam turbine 6 are the same as those in the first embodiment.

(Exhaust system)
According to the exhaust system 203 according to the present embodiment, the first supply passage 12 branches from the exhaust pipe 11, and a part of the exhaust gas can be supplied to the gas inlet of the first power turbine 4A via the first supply passage 12. It is like that. A first recirculation passage 13 is connected to the gas outlet of the first power turbine 4 </ b> A, and the first recirculation passage 13 is connected to the exhaust pipe 11. The gas discharged from the gas outlet of the first power turbine 4 </ b> A is returned to the exhaust pipe 11 through the first reflux passage 13. On-off valves 14 and 15 are provided in the first supply passage 12 and the first reflux passage 13.

  Further, the second supply passage 16 branches from the upstream side of the on-off valve 14 in the first supply passage 12, and a part of the exhaust gas enters the gas inlet of the second power turbine 4 </ b> B via the second supply passage 16. It can be supplied. A second recirculation passage 17 is connected to the gas outlet of the second power turbine 4B, and the second recirculation passage 17 is connected to the downstream side of the on-off valve 15 in the first recirculation passage 13. The gas discharged from the gas outlet of the second power turbine 4B is returned to the first reflux passage 13 via the second reflux passage 17. The second supply passage 16 and the second reflux passage 17 are also provided with on-off valves 18 and 19.

  The first power turbine 4A and the second power turbine 4B are gas turbines similar to the gas turbine 4 of the first embodiment. The on-off valves 14, 15, 18, 19 open and close depending on the situation. As a result, any one of the four states of the state where both the first power turbine 4A and the second power turbine 4B operate, the state where both stop, and the state where one operates and the other stops is appropriately selected. The

(Power transmission system)
According to the power transmission system 207 according to the present embodiment, the input shaft of the generator 2 includes the first input shaft portion 44A and the second input shaft portion 44B that extend in opposite directions in the axial direction. The first input shaft portion 44A and the second input shaft portion 44B are arranged on the same axis and rotate in synchronization.

  The configuration on the right side in FIG. 3 when viewed from the generator 2 is the same as that of the power transmission system 7 according to the first embodiment. That is, the first input shaft 44 </ b> A is the same as the input shaft 44 according to the first embodiment, extends to the right side from the generator 2, and drives the main speed reducer 50 through the coupling 43 and the rotating shaft 42. It is connected to the gear 52. The rotational force of the steam turbine 6 is transmitted to the first input shaft portion 44A via the main speed reducer 50. The first power turbine 4A according to the present embodiment is replaced with the power turbine 4 according to the first embodiment. The output shaft 61 of the first power turbine 4A is connected to the main reduction gear 50 via the first auxiliary driving gear 64 and the first auxiliary driven gear 65 of the first auxiliary reduction gear 62, the first rotary shaft 63 and the first SSS clutch 66. The main driven gear 52 is connected. The first sub-reduction gear 62, the first sub-drive gear 64, the first sub-driven gear 65, the first rotating shaft 63, and the first SSS clutch 66 are given ordinal numbers for the sake of convenience. The sub-reduction gear, the sub-drive gear, the sub-driven gear, the rotation shaft, and the SSS clutch are the same.

  The second input shaft portion 44B extends from the generator 2 to the left side. The second power turbine 4B is disposed on the same side in the axial direction as the second input shaft portion 44B with respect to the generator 2, that is, the steam turbine 6 and the first power turbine 4A and the axis with respect to the generator 2. Arranged on the opposite side in the direction.

  The output shaft 71 of the second power turbine 4B is disposed in parallel with the second input shaft portion 44B. The output shaft 71 is connected to the second rotating shaft 73 via the second sub reduction gear 72. The second sub reduction gear 72 is a reduction gear train having a second sub drive gear 74 to which the output shaft 71 is fixed and a second sub driven gear 75 to which the rotation shaft 73 is fixed. These two gears 74 and 75 are both gears having external teeth, and the number of teeth of the second auxiliary drive gear 74 is smaller than the number of teeth of the second auxiliary driven gear 75. The second sub drive gear 74 and the second sub driven gear 75 are meshed with each other in the radial direction. The second rotating shaft 73 is disposed coaxially with the second input shaft portion 44B, and is connected to the second input shaft portion 44B via the second SSS clutch 76.

  According to the above configuration, when the second power turbine 4B is operating, the rotational force of the second power turbine 4B is such that the second auxiliary drive gear 74, the second auxiliary driven gear 75, the second rotary shaft 73, and the second SSS. The clutch 76 is input to the second input shaft portion 44B through this order. When the second power turbine 4B is stopped, the difference between the rotation speed of the first input shaft portion 44A and the second input shaft portion 44B and the rotation speed of the second rotation shaft 73 becomes significant, so that the second SSS clutch 76 is Thus, the power transmission path between the generator 2 and the second sub reducer 72 is disconnected. For this reason, the gear which comprises the 2nd sub reduction gear 72 does not run idle by the rotational force of the steam turbine 6. FIG.

  Further, the output shaft of the second power turbine 4 </ b> B extends on the opposite side in the axial direction from the second rotating shaft 73 with respect to the second sub reduction gear 72. For this reason, the second power turbine 4B does not interfere with the generator 2. Since only the configuration related to the second power turbine 4B is arranged on the right side when viewed from the generator 2, the output shaft 71, the rotary shaft 73, and the second input shaft portion 44B of the second power turbine 4B are arranged. It can be configured as short as possible. Therefore, it is possible to satisfactorily suppress an increase in the size of the entire system in the radial direction and make it compact in the axial direction, and the shaft support structure between the generator 2 and the second power turbine 4B is complicated. Can be suppressed.

  Note that the output shaft 61 of the first power turbine 4A and the output shaft 71 of the second power turbine 4B are connected to the input shaft portions 44A and 44B via two gear trains in the same direction. Will rotate. For this reason, the configuration of the first power turbine 4A and the second power turbine 4B can be made common, and the power generation system 200 can be easily manufactured.

[Third Embodiment]
Here, in a container ship which is a typical cargo handling ship, high speed navigability and an increase in loadable capacity are always required in order to suppress the transportation cost per unit distance unit container. In recent years, with the economic development of Asian countries, freight transportation using container ships with Overpanamax or Oversuemax hulls has become a reality, and the increase in the loadable capacity has become huge. It is going to be achieved by Thus, when it is going to enlarge a hull and to increase a loadable capacity, if it is one main machine, it will become very difficult to ensure high-speed navigability. Therefore, it is assumed that the propulsion system for the container ship will adopt two main engines provided with propulsion shafts (so-called two-machine two-shaft type). The power generation system according to the third embodiment of the present invention is a ship equipped with such a two-machine / two-shaft propulsion system, and in particular, a cargo handling ship with the original purpose of securing a space for cargo loading. It is preferably applied to.

  FIG. 4 is a conceptual diagram showing an overall configuration of a power generation system 300 according to the third embodiment of the present invention. As shown in FIG. 4, the power generation system 300 according to this embodiment is mounted on a ship including two engines 1A and 1B, and includes one generator 2, one steam turbine 6, and two Power turbines 4A and 4B are provided. The generator 2 is a steam turbo generator with a ship power turbine.

Each engine 1A, 1B is provided with an exhaust system 3A, 3B individually. Each exhaust system 3A, 3B is configured similarly to the exhaust system 3 of the first embodiment. That is, each exhaust system 3A, 3B supplies exhaust gas to the corresponding power turbine 4A, 4B, respectively. The waste heat recovery system 305 recovers the heat of the exhaust gas from both the engines 1A and 1B, generates steam with the recovered heat, and drives the steam turbine 6 with the generated steam. A connection line that connects one exhaust system 3A and the other exhaust system 3B may be provided. In this case, when the load on both engines is reduced, the exhaust gas from the two engines merges into one unit in a situation where one power turbine cannot operate due to the exhaust gas from each engine. It becomes possible to drive the power turbine. At that time, one of the power turbines needs to be stopped, and each engine needs to be able to operate a corresponding one of the power turbines. Therefore, the connection line 20 opens and closes in one supply passage 12A. a lower flow side of the valve 14A, it is preferable so as to connect the lower stream side of the opening and closing valve 14B of the other supply passage 12B, also provided an on-off valve 20V on the connection line 20.

  The power transmission system 207 is the same as that of the second embodiment, and is configured to be able to input the rotational force of the steam turbine 6, the first power turbine 4 </ b> A, and the second power turbine 4 </ b> B to one generator 2. Therefore, as in the second embodiment, the idle gear can be eliminated even if the first power turbine 4A and the second power turbine 4B are stopped. Further, the configuration of the entire system becomes compact in the axial direction, and the shaft support structure can be prevented from becoming complicated. Since the power generation system 300 having such a compact configuration can be provided, it is very useful when applied to a cargo handling ship.

(Waste heat recovery system)
The waste heat recovery system 305 mainly includes a first exhaust gas economizer 21A, a second exhaust gas economizer 21B, a high pressure drum 22, a low pressure drum 23, a high pressure circulating water system 324, a steam system 325, a low pressure circulating water system 326, and an air mixture system 27. I have. High pressure drum 22, low pressure drum 23 and admission lines 2 7 is the same as in the first embodiment.

  The first and second exhaust gas economizers 21A and 21B are configured in the same manner as the exhaust gas economizer 21 according to the first embodiment. The first exhaust gas economizer 21A includes, in order from the upstream side, a first inlet pipe 31A, a first superheater 36A, a first high-pressure evaporator 32A, a first intermediate pipe 33A, a first intermediate pipe 33A connected to the exhaust pipe 11A of the first engine 1A. 1 low-pressure evaporator 34A and first outlet pipe 35A. The second exhaust gas economizer 21B is, in order from the upstream side, a second inlet pipe 31B, a second superheater 36B, a second high-pressure evaporator 32B, a second intermediate pipe 33B, and a second intermediate pipe 33B connected to the exhaust pipe 11B of the second engine 1B. 2 It has a low-pressure evaporator 34B and a second outlet pipe 35B. The exhaust gas from the first engine 1A passes through the first exhaust gas economizer 21A and is guided to the exhaust outlet, and the exhaust gas from the second engine 1B passes through the second exhaust gas economizer 21B and is guided to the exhaust outlet.

  The high-pressure circulating water system 324 includes a line 24a that connects the high-pressure drum 22 to the first high-pressure evaporator 32A of the first exhaust gas economizer 21A, a line 24b that connects the first high-pressure evaporator 32A to the high-pressure drum 22, and a line 24a. A line 24c branched and connected to the second high-pressure evaporator 32B of the second exhaust gas economizer 21B and a line 24d connecting the second high-pressure evaporator 32B to the line 24b are provided. As described above, the high-pressure circulating water system 324 of the high-pressure drum 22 connects the first high-pressure evaporator 32A and the second high-pressure evaporator 32B to the high-pressure drum 22 in parallel.

Steam system 325, connected to a line 25a extending from the high-pressure drum 22, and 25b that branch from the line 25b, line 25a, 25b has a line 25c formed by the set, the line 25c is a vapor inlet mouth of the steam turbine 6 Has been. A first superheater 36A and a second superheater 36B are connected in parallel to the lines 25a and 25b, respectively, and the steam system 325 controls whether or not the steam flowing through the line 25a passes through the first superheater 36A. And a valve unit 25VB for controlling whether or not the steam flowing through the line 25b passes through the second superheater 36B.

  When the pump 24P provided on the high pressure drum 22 side from the branch point of the lines 24a and 24c operates, a part of the circulating water in the high pressure drum 22 is sent to the first high pressure evaporator 32A via the line 24a. The sent circulating water becomes steam by heat exchange with the exhaust gas in the first high-pressure evaporator 32A. The circulating water is returned to the high-pressure drum 22 through the line 24b in a gas-liquid mixed state. A part of the circulating water in the high-pressure drum 22 is sent to the second high-pressure evaporator 32B via the line 24c, and the sent circulating water is vaporized by heat exchange with the exhaust gas in the second high-pressure evaporator 32B. It becomes. The circulating water is returned to the high-pressure drum 22 through the line 24d and the line 24c in a gas-liquid mixed state. The returned circulating water is separated into vapor and liquid in the high-pressure drum 22.

  A part of the steam in the high-pressure drum 22 is supplied to the steam inlet of the steam turbine 6 through the line 25a and the line 25c in this order. A part of the steam is supplied to the steam inlet of the steam turbine 6 through the line 25b and the line 25c in this order. By operating the valve units 25VA and 25VB in accordance with the rotational force required for the steam turbine 6, the steam flowing through the line 25a can be heated by the first superheater 36A, and the steam flowing through the line 25b is It can heat with 2 superheater 36B.

  The low-pressure circulating water system 326 includes a line 26a connecting to the first low-pressure evaporator 34A, a line 26b connecting the first low-pressure evaporator 34A to the low-pressure drum 23, and a second exhaust gas economizer 21B branched from the line 26a. Line 26c connected to the second low-pressure evaporator 34B, and a line 26d connecting the second low-pressure evaporator 34B to the line 26b. Thus, the low-pressure circulating water system 326 of the low-pressure drum 23 connects the first low-pressure evaporator 34A and the second low-pressure evaporator 34B to the low-pressure drum 23 in parallel.

When the pump 26P provided on the low-pressure drum 23 side from the branch point of the lines 26a and 26c operates, a part of the circulating water in the low-pressure drum 23 is sent to the first low-pressure evaporator 34A via the line 26a. The sent circulating water becomes steam by heat exchange with the exhaust gas in the first low-pressure evaporator 34A. The circulating water is returned to the low-pressure drum 23 through the line 26b in a gas-liquid mixed state. A part of the circulating water in the low pressure drum 23 is sent to a second low pressure evaporator 34B through a line 26c, the circulating water sent by heat exchange with the exhaust gas in the second low-pressure evaporator 34B It becomes steam. The circulating water is returned to the low-pressure drum 23 through the line 26d and the line 26c in a gas-liquid mixed state. The returned circulating water is separated into vapor and liquid in the low-pressure drum 23. The steam in the low-pressure drum 23 is supplied to the mixture inlet of the steam turbine 6 through the line 27a.

  Thus, in this embodiment, the heat of the exhaust gas from each of the two engines 1A and 1B is individually recovered by the two exhaust gas economizers. Two exhaust gas economizers are connected in parallel to a single high-pressure drum via a high-pressure circulating water system, and are connected in parallel to a single low-pressure drum via a low-pressure circulating water system. With this configuration, the configuration of the waste heat recovery system 305 can be made compact as compared with the case where a set of a high pressure drum and a low pressure drum is individually provided in two exhaust gas economizers.

[Fourth Embodiment]
FIG. 5 is a conceptual diagram showing the configuration of the power transmission system 407 of the power generation system 400 according to the fourth embodiment of the present invention. As shown in FIG. 5, the power generation system 400 according to this embodiment includes one generator 2, one steam turbine 6, and two power turbines 4 </ b> A and 4 </ b> B. The generator 2 is a steam turbo generator with a ship power turbine. The second embodiment may be applied to the exhaust system and the waste heat recovery system, or the third embodiment may be applied. The power transmission system 407 according to the present embodiment is a modification of the power transmission system 207 according to the second and third embodiments, regardless of the number of engines, the configuration of the exhaust system, and the configuration of the waste heat recovery system. The present invention is suitably applied to a system including one generator 2, one steam turbine 6, and two power turbines 4A and 4B.

(Power transmission system)
According to the power transmission system 407 according to the present embodiment, the input shaft of the generator 2 has the same first input shaft portion 44A and second input shaft portion 44B as in the second embodiment. The first input shaft portion 44A extends to the right side in FIG. 5 when viewed from the generator, and the second input shaft portion 44B extends to the left side in FIG.

  In the second and third embodiments, the output shaft 41 of the steam turbine 6 is disposed on the upper side in the drawing as viewed from the first input shaft portion 44A. However, in this embodiment, the output shaft of the steam turbine 6 is disposed. 41 is disposed on the lower side in the drawing as viewed from the first input shaft portion 44A. That is, the main reduction gear 452 is configured such that the main drive gear 451, the idle gear 453, and the main driven gear 452 are arranged in this order from the lower side to the upper side in the drawing. Accordingly, the first sub drive gear 464 is also arranged on the upper side of the first sub driven gear 465 in the first sub reduction gear 462. Further, the second sub reduction gear 472 also has a second sub drive gear 474 disposed above the second sub driven gear 475 in the same manner as the first sub reduction gear 462.

  As described above, when viewed from the first input shaft portion 44A and the second input shaft portion 44B of the generator 2, the output shaft 41 of the steam turbine 6, the output shaft 61 of the first power turbine 4A, and the output of the second power turbine 4B. The arrangement of the shaft 71 can be changed as appropriate. The same effect as the power transmission system 207 according to the second and third embodiments can be obtained by the power transmission system 407 according to the fourth embodiment.

[Fifth Embodiment]
FIG. 6 is a conceptual diagram showing the configuration of the power transmission system 507 of the power generation system 500 according to the fifth embodiment of the present invention. As shown in FIG. 6, the power generation system 500 according to this embodiment includes a generator 2 of 1 aircraft, one and the steam turbine 6 A, the three power turbine 4A, 4B, and 4C. The generator 2 is a steam turbo generator with a ship power turbine. The power transmission system 507 according to the present embodiment is preferably applied to such a system.

  That is, the power generation system 500 according to this embodiment can appropriately select the number of engines, the configuration of the exhaust system, and the configuration of the waste heat recovery system. For example, when the power generation system 500 is mounted on a ship including one engine, three power turbines may be connected in parallel to an exhaust system corresponding to the one engine. When the power generation system 500 is mounted on a ship having two engines, two power turbines are connected in parallel to the exhaust system corresponding to one engine, and the remaining one power turbine is connected to the exhaust system corresponding to the other engine. It may be connected. When the power generation system 500 is mounted on a ship including three engines, one power turbine may be connected to an exhaust system corresponding to each engine. When the power generation system 500 is mounted on a ship equipped with three engines, the waste heat recovery system has three exhaust gas economizers connected in parallel to one high-pressure drum and three low-pressure drums. The structure which connected the exhaust gas economizer in parallel may be sufficient.

(Power transmission system)
According to the power transmission system 507 according to the present embodiment, the input shaft of the generator 2 includes the first input shaft portion 44A and the second input shaft portion 44B in the same manner as in the second to fourth embodiments. 44 A of 1st input shaft parts and the 2nd input shaft part 44B are mutually extended in an axial direction on the basis of the generator 2, are arrange | positioned coaxially, and rotate synchronously.

  As in the fourth embodiment, the output shaft 71 of the second power turbine 4B is connected to the second input shaft portion 44B via the second auxiliary reduction gear 472, the second rotating shaft 73, the second SSS clutch 76, and the coupling 77. It is connected to.

The first input shaft portion 44A of the generator 2 and the output shaft 41 of the steam turbine 6 A, are arranged parallel to each other. The output shaft 41 of the steam turbine 6 A is the main reduction gear 550, via a rotary shaft 42 and coupling 43 connected to the first input shaft portion 44A. The main reduction gear 550 includes a main drive gear 551 with the output shaft 41 fixed, a main driven gear 552 with the rotation shaft 42 fixed, and two idle gears interposed between the main drive gear 551 and the main driven gear 552. And a reduction gear train having 553 and 554. All of the four gears constituting the main reduction gear 550 are gears having external teeth, and the number of teeth of the main drive gear 551 is smaller than the number of teeth of the main driven gear 552. The idle gear 553 is interposed between the main drive gear 551 and the idle gear 554 and meshes with these gears 551, 554, and the idle gear 554 is interposed between the idle gear 553 and the main driven gear and these gears 554. 552 is engaged. Thus, the rotational force of the steam turbine 6 A is the main drive gear 551, idle gear 553, idle gear 554, the main driven gear 552, via a rotary shaft 42 and coupling 43 in this order, the first input shaft portion 44A Is input.

The output shaft 61 of the first power turbine 4 </ b> A is disposed in parallel with the output shaft 41 of the steam turbine 6 </ b> A, and is connected to the main reducer 550 via the first sub reducer 462, the first rotating shaft 63, and the first SSS clutch 66. The main driven gear 552 is connected. The first sub reduction gear 462 is configured in the same manner as in the fourth embodiment.

The output shaft 81 of the third power turbine 4C, the output shaft 41 of the steam turbine 6 A, the first and second power turbine 4A, 4B of the output shaft 61 and 71, first and second input shaft portion 44A, 44B and, The third rotation shaft 83 is disposed in parallel. The output shaft 81 of the third power turbine 4C is connected to the third rotating shaft 83 via a third sub reduction gear. The third sub-reduction gear 82 is a reduction gear train having a third sub-drive gear 84 that fixes the output shaft 81 and a third sub-driven gear 85 that fixes the third rotation shaft 83. These two gears 84 and 85 are both gears having external teeth, and the number of teeth of the third auxiliary driving gear 84 is smaller than the number of teeth of the third auxiliary driven gear 85, and the auxiliary driving gear 84 and the auxiliary driven gear are included. 85 are meshed with each other in the radial direction. The third rotating shaft 83 is connected to the main drive gear 551 of the main reducer 550 via the third SSS clutch 86.

When the third power turbine 4C is operating, the rotational force of the third power turbine 4C passes through the third auxiliary drive gear 84, the third auxiliary driven gear 85, the third rotary shaft 83, and the third SSS clutch 86 in this order. , it is transmitted to the main drive gear 551, which thereafter is transmitted in the same way as the steam turbine 6 a to the first input shaft portion 44A of the generator 2. Even when the third power turbine 4C is stopped, the main drive gear 551, since it is contributing gears to transmit rotational force of the steam turbine 6 A to the generator 2, the main reduction gear 550 There is no idle gear. Further, when the third power turbine 4C is stopped, the difference between the rotational speed of the main drive gear 551 and the rotational speed of the third sub driven gear 85 becomes significant, so the third SSS clutch 86 is disengaged and the main drive The power transmission path is disconnected between the gear 551 and the third sub reduction gear 82. For this reason, the gear which comprises the 3rd sub reduction gear 82 does not run idle by the rotational force of 6 A of steam turbines.

Then, the output shaft 41 of the third rotating shaft 83 and the steam turbine 6 A, extends opposite to each other in the axial direction with respect to the main reduction gear 550, and an output shaft of the third power turbine 4C No. The three rotation shafts 83 extend on opposite sides in the axial direction with respect to the third sub-reduction gear 82. Therefore, the third power turbine 4C, because the main reduction gear based on is arranged on the opposite side of the steam turbine 6 A and the first power turbine 4A axially, these turbines 6 A, interference between the well 4A Can be prevented.

  On the other hand, the third power turbine 4C and the generator 2 are arranged on the same side in the axial direction with respect to the main reduction gear 550. That is, the third power turbine 4C and the generator 2 are arranged so as to be aligned in the radial direction of the main reduction gear 550 and the third auxiliary reduction gear 82.

  The main speed reducer 550 according to this embodiment includes a main driven gear 552 to which the first input shaft portion 44A of the generator 2 is connected and a main drive gear 551 to which the output shaft 81 of the third power turbine 4C is connected. Two idle gears 553 and 554 are interposed therebetween. For this reason, the main drive gear 551 and the main driven gear 552 are arranged away from each other in the radial direction. The third sub driven gear 85 of the third sub speed reducer 82 is disposed coaxially with the main drive gear 551, while the third sub drive gear 84 includes the third sub driven gear 85 and the main drive gear 551. As viewed from the main driven gear 552, the main driven gear 552 is disposed away from the main driven gear 552. By these two idle gears 553 and 554 and the third sub-reduction gear 82, the generator 2 and the third power turbine 4C are arranged away from each other in the radial direction of the main reduction gear 550 and the third sub-reduction gear 82. Can be arranged without difficulty in the radial direction. Then, it is not necessary to lengthen the output shaft 81 of the third power turbine 4C or the first input shaft portion 44A of the generator 2 in order to allow the third power turbine 4C to escape from the generator 2 in the axial direction. Complicating the shaft support structure between 550 and the generator 2 and the shaft support structure between the main reduction gear 550 and the third power turbine 4C can be suppressed. As described above, when the power turbine is provided side by side in the radial direction with the generator, if a plurality of idle gears are provided in the main reduction gear 550, a radial interval between the power turbine and the generator can be easily secured. It is beneficial because it can.

[Other Embodiments]
Although the embodiment according to the present invention has been described so far, the above configuration can be appropriately changed within the scope of the present invention. For example, in providing a system including two power turbines, the structure shown on the left side of the generator may be omitted from the power transmission system according to the fifth embodiment. The main reduction device may be provided with three or more idle gears, and the auxiliary reduction device may be provided with idle gears.

  Furthermore, although the main turbine is a steam turbine and the sub turbine is a power turbine, this relationship may be reversed. Although the case where a marine diesel engine is employed as the main engine is illustrated, the present invention can be suitably applied even when a gas turbine is employed.

  The present invention prevents hammering and improves power generation efficiency in a power generation system in which the rotational force of a plurality of turbines is transmitted to a generator through a gear train and may partially stop the turbine during system operation. In addition, it has the effect of being able to suppress an increase in the size of the entire system, and is beneficial when mounted on a ship as a ship power generation system.

100, 200, 300, 400, 500 Power generation system 1 (1A, 1B) Marine diesel engine 2 Generator 3 (3A, 3B), 203 Exhaust system 4 (4A, 4B, 4C) Power turbine (sub turbine)
5,305 Waste heat recovery system 6 Steam turbine (main turbine)
7 Power transmission system 21 (21A, 21B) Exhaust gas economizer 41 Steam turbine output shaft 44 (44A, 44B) Generator input shaft 50, 450, 550 Main speed reducer 51, 451, 551 Drive gear 52, 452, 552 Driven Gears 53, 453, 553, 554 Idle gears 61, 71, 81 Power turbine output shafts 62, 72, 82 Sub-reduction gears 66, 76, 86 SSS clutch

Claims (8)

A power generation system that drives a generator by the rotational force of a turbine,
A main turbine operating during system operation;
A main reduction gear having a main drive gear connected to the output shaft of the main turbine and a main driven gear connected to the input shaft of the generator, and transmitting the rotation of the main drive gear to the main driven gear; ,
One or more secondary turbines that operate or stop depending on the situation when the system is operating,
The main reduction gear further includes one or more idle gears interposed between the main drive gear and the main driven gear to transmit the rotation of the main drive gear to the main driven gear,
An output shaft of a first auxiliary turbine included in the one or more auxiliary turbines is connected to the main driven gear;
The first sub turbine and the main turbine are arranged on the same side in the axial direction with respect to the main speed reducer, and the main turbine and the generator are based on the main speed reducer. A power generation system arranged on opposite sides in the axial direction.   2. The power generation system according to claim 1, wherein the centers of the main drive gear, the idle gear, and the main driven gear are located on the same straight line when viewed from the axial direction. A clutch interposed between the output shaft of the first auxiliary turbine and the main driven gear;
A first sub-reduction gear interposed between the output shaft of the first sub-turbine and the clutch;
The first sub reducer has a first sub driven gear connected to the first auxiliary drive gear, and the clutch first being connected with the secondary turbine output shaft, the rotation of the first auxiliary drive gear To the first sub driven gear,
Said first auxiliary drive gear, before Symbol viewed from the main driven gear and said first auxiliary driven gear, said are disposed away from the main drive gear, the power generation system according to claim 1 or 2. The one or more auxiliary turbines further include a second auxiliary turbine,
The input shaft of the generator has a first input shaft portion and a second input shaft portion that extend in opposite directions in the axial direction, and the first input shaft portion is the main follower of the main reducer. 4. The power generation system according to claim 1, wherein the power generation system is connected to a gear, and an output shaft of the second sub turbine is connected to the second input shaft portion via a clutch. The one or more auxiliary turbines further include a third auxiliary turbine,
An output shaft of the third auxiliary turbine is connected to the main drive gear via a clutch, and the first auxiliary turbine and the third auxiliary turbine are opposite to each other in the axial direction with respect to the main reduction gear. The power generation system according to claim 4, which is disposed in The power generation system is a power generation system mounted on a ship having one main engine,
The main turbine is a steam turbine that extracts rotational force from waste heat around the main engine;
The power generation system according to any one of claims 1 to 5, wherein the one or more sub turbines are power turbines that extract a rotational force from the exhaust of the main engine. The power generation system is a power generation system mounted on a ship having two main engines,
The main turbine is a steam turbine that extracts rotational force from waste heat around the two main engines,
The first auxiliary turbine is a first power turbine that extracts rotational power from one exhaust of the two main engines, and the second auxiliary turbine rotates from the other exhaust of the two main engines. The power generation system according to claim 4, wherein the power generation system is a second power turbine for taking out the power. A waste heat recovery system that recovers waste heat of the two main machines to generate steam;
The waste heat recovery system includes a first exhaust gas economizer that recovers the heat of one of the two main engines, a second exhaust gas economizer that recovers the heat of the other of the two main engines, An air / water separator for supplying steam to a steam turbine, and a circulating water system for connecting the first exhaust gas economizer and the second exhaust gas economizer in parallel to the air / water separator. The power generation system described in 1.