JP4697730B2 - Turbine equipment - Google Patents

Description

  The present invention relates to a turbine apparatus that rotates a turbine blade using a non-azeotropic mixed medium of ammonia and water as a working medium.

  In recent years, a power generation method using a non-azeotropic mixed medium of ammonia / water has been studied as a technique for recovering power from unused energy. In this power generation system, the non-azeotropic mixture of ammonia / water is evaporated using heat from a heat source such as an engine, and the rotating shaft is rotated together with the turbine blade by the vapor pressure, and the power of the rotating shaft is It is to generate electricity using. In a cogeneration system (for example, Patent Document 1) as an example of this conventional method, water is evaporated using heat of exhaust gas from, for example, a gas engine of cogeneration, and a steam turbine is rotated by generated steam. Driven. The heat of the cooling water of the gas engine is used to evaporate the non-azeotropic mixture of ammonia / water, and the heat of the exhaust gas from the gas engine (the plain gas after being used to generate water vapor) is used. Thus, the non-azeotropic mixed medium is evaporated, and the low-temperature steam turbine is rotationally driven by the generated steam.

  In this cogeneration system, the heat of the exhaust gas of the gas engine is recovered to rotate and drive the steam turbine, and the heat of the cooling water of the gas engine and the heat of the exhaust gas after steam generation is recovered to recover the low temperature steam. Since the turbine is driven to rotate, it is possible to effectively recover the exhaust heat of the gas engine and further improve the operation efficiency of the cogeneration system.

JP 2002-221008 A

  However, when a non-azeotropic mixture of ammonia / water is used as a working medium for a low-temperature steam turbine, it is necessary to prevent leakage of ammonia from between the turbine housing and the rotating shaft from the viewpoint of environmental safety. In order to prevent this, a mechanical seal means is used. The contact seal means as the mechanical seal means has a problem that since the seal member comes into contact with the rotating shaft, a frictional resistance is generated on the rotating shaft and a mechanical loss occurs. In addition, the labyrinth seal means as the mechanical seal means does not cause mechanical loss, but has a problem that ammonia leaks from the gap of the labyrinth structure. Therefore, in order to prevent the leakage of ammonia, the leakage gas is submerged in water. After bubbling, it is discharged to the outside, and equipment for this bubbling is required, so that the apparatus becomes large and the treatment of water that has absorbed ammonia becomes a problem.

  An object of the present invention is to reliably prevent an ammonia / water non-azeotropic mixture from leaking to the outside, and to prevent adverse effects on the non-azeotropic mixture as a working medium. Is to provide a device.

The turbine apparatus according to claim 1 of the present invention includes a turbine blade that is rotated using a non-azeotropic mixed medium of ammonia and water as a working medium, a rotating shaft that rotatably supports the turbine blade, and the turbine A turbine apparatus comprising: a turbine housing that defines a turbine chamber for housing blades; and a sealing means for sealing between the rotating shaft and the turbine housing,
The seal means seals between an inner portion of the turbine housing and the rotary shaft, and seals between an outer portion located on the outer side in the axial direction from the inner portion of the turbine housing and the rotary shaft. Water vapor introduced from the water vapor introduction line , comprising: an outer seal means for performing the operation, an intermediate seal means provided between the inner seal means and the outer seal means, and a water vapor introduction line for introducing water vapor. Is introduced into the outer annular space between the outer seal means and the intermediate seal means, and the pressure of the steam introduced from the steam introduction line is higher than the steam pressure of the working medium introduced into the turbine chamber. An inner annular space between the intermediate sealing means and the inner sealing means is provided for generating the working medium. Characterized in that it communicates with the gin of the exhaust system.

In the turbine device according to claim 2 of the present invention, the rotating shaft is further provided with steam turbine blades that are rotated using steam as a working medium, and a part of the steam as the working medium is provided. It is introduced into the outer annular space between the intermediate sealing means and the outer sealing means through the water vapor introduction line.

According to the turbine apparatus of the first aspect of the present invention, the sealing means for preventing the leakage of the non-azeotropic mixed medium includes the inner sealing means, the outer sealing means, and the intermediate sealing means disposed therebetween. When, a steam introduction line for introducing steam, the steam from the steam introduction means is introduced into the outer annular space between the middle sealing means and the outer sealing means, non-by the action of water vapor to be introduced Leakage of the azeotropic mixing medium to the outside can be prevented. Moreover, since the pressure of the steam introduced through the steam introduction line is set higher than the steam pressure of the working medium (non-azeotropic mixture medium) introduced into the turbine chamber, the steam introduced into the outer annular space This allows the working medium to flow into the inside, thereby reliably preventing leakage of the working medium to the outside. Further, since the inner annular space between the intermediate sealing means and the inner sealing means is communicated with the engine exhaust system, water vapor that flows into the inner annular space from the outer annular space flows into the engine exhaust system, and temporarily enters the turbine chamber. Even if the working medium (ammonia) leaks from, the leaked working medium flows into the exhaust system together with the water vapor, and can be determined as required in this exhaust system. Although steam from the annular space flows into the turbine chamber, since the working medium is a non-azeotropic mixture of ammonia and water, even if some steam is added to the working medium, the performance (turbine device) Will not cause any problems).

According to the turbine device of the second aspect of the present invention, a part of the steam for rotating the steam turbine blades passes through the steam introduction line into the outer annular space between the intermediate sealing means and the outer sealing means. Since it is introduced, a dedicated facility for generating water vapor is not required, and the configuration of the turbine device can be simplified.

  Hereinafter, an embodiment of a turbine apparatus according to the present invention will be described with reference to the accompanying drawings. FIG. 1 is a simplified diagram illustrating an example of a cogeneration system to which a turbine apparatus according to an embodiment is applied. FIG. 2 is a cross-sectional view illustrating a part of the turbine apparatus in the cogeneration system of FIG. 3 is a cross-sectional view illustrating a part of a modified turbine apparatus, and FIG. 4 is a diagram schematically illustrating a part of another turbine apparatus.

  In FIG. 1, an illustrated cogeneration system to which a turbine device 2 according to an embodiment of the present invention is applied includes an engine 6 (for example, a gas engine) including a supercharger 4 and a cup connected to an output shaft of the engine 6. And a generator 10 that is drivingly connected via a ring 8. The supercharger 4 connects the turbine rotor 14 disposed in the exhaust passage 12 of the engine 6, the guide blades 18 disposed in the supply passage 16 of the engine 6, the turbine rotor 14 and the guide blades 8. The turbine rotor 14 is rotated in a predetermined direction by the exhaust gas from the engine 6, and the guide blade 18 is rotated through the rotation shaft 20 by the rotation of the turbine rotor 14. The air supplied to the engine 6 is supercharged by the rotation of the guide vanes 18.

  In this cogeneration system, when the engine 6 is operated, the output shaft of the engine 6 is rotated in a predetermined direction, and the rotating force of the output shaft is operated via the coupling 8 to operate the generator 10. Power generation by the generator 10 is performed using the rotation of the output shaft.

  In this embodiment, the first heat recovery system 22 for recovering the heat of the exhaust gas of the engine 6, the second heat recovery system 24 for recovering the heat of the cooling water of the engine 6, and the first and second There is provided a turbine apparatus 2 that is operated as described later by heat recovered by the heat recovery systems 22 and 24. The first heat recovery system 22 is for recovering and extracting heat by the steam turbine 26 of the turbine device 2, the steam turbine 26 rotated by the steam as the working medium, and the first for generating the steam. 1 heat exchanger 28, a first condenser 30 for returning steam as working medium to water, and a first condenser 30 for circulating through the first heat exchanger 28, the steam turbine 26 and the first condenser 30. 1 circulation flow path 32. A first feed pump 34 is disposed in the first circulation channel 32.

  In the first heat recovery system 22, the water of the first condenser 30 is fed to the first heat exchanger 28 by the action of the first feed pump 34. In the first heat exchanger 28, heat exchange is performed between the exhaust gas flowing through the exhaust passage 12 (downstream of the supercharger 4) of the engine 6 and the water flowing through the first circulation passage 32. Water vapor is generated by heat exchange. The generated steam is fed to the steam turbine 26, and the steam turbine 26 is rotated in a predetermined direction by the steam. The steam that has flowed through the steam turbine 26 returns to the first condenser 30 through the first circulation passage 32, and is returned to water by the first condenser 30. In this embodiment, an intercooler 36 is disposed between the first condenser 30 and the first heat exchanger 28, and the intercooler 36 is configured to supply water and air supply passage 16 through the first circulation passage 32. Heat exchange is performed with the supply air flowing through (the downstream side of the guide vane 18 of the supercharger 4) to cool the supply air.

  The second heat recovery system 24 is for recovering and extracting heat by the low-temperature steam turbine 42 of the turbine device 2, and is a low temperature rotated by a non-azeotropic mixture medium of ammonia and water as a working medium. Steam turbine 42; second and third heat exchangers 44 and 46 for generating non-azeotropic medium steam; and fractionator 48 for fractionating non-azeotropic medium into liquid and steam. A second condenser 50 for returning the vapor of the non-azeotropic mixture medium to a liquid, these second and third heat exchangers 44 and 46, a fractionator 48, a low-temperature steam turbine 42 and a second condensate. And a second circulation channel 52 for circulation through the vessel 50. The upstream side portion of the second circulation channel 32 (the portion between the second condenser 50 and the fractionator 48) is branched into a first branch channel 54 and a second branch channel 56, and the first branch The first heat exchanger 44 is disposed in the flow path 54, the second heat exchanger 46 is disposed in the second branch flow path 56, and the downstream side of the second condenser 50 in the second circulation flow path 52. Is provided with a second feed pump 58.

  In the second heat recovery system 24, the non-azeotropic mixed medium (ammonia / water mixed medium) of the second condenser 50 passes through the first branch flow path 54 by the action of the second feed pump 58. While being fed to the second heat exchanger 44, it is fed to the third heat exchanger 46 through the second branch flow path 56. In the second heat exchanger 44, heat exchange is performed between the cooling water circulated from the engine 6 through the cooling water circulation passage 60 and the non-azeotropic mixed medium flowing through the first branch passage 54. The non-azeotropic mixed medium that is partially vaporized is fed to the fractionator 48. Further, in the third heat exchanger 46, the non-azeotropic mixture flowing through the exhaust gas flow path 12 (exhaust gas after heat exchange in the first heat exchanger 28) and the second branch flow path 56. Heat exchange is performed with the medium, and the non-azeotropic mixed medium that is partially vaporized by the heat exchange is fed to the fractionator 48. In the fractionator 48, the non-azeotropic mixing medium is separated into steam and liquid, and the steam is supplied to the low-temperature steam turbine 42 through the second circulation passage 52, and the non-azeotropic mixing medium steam is cooled at a low temperature. The steam turbine 42 is rotated in a predetermined direction, and the steam that has flowed through the low-temperature steam turbine 42 returns to the second condenser 50 through the second circulation passage 52, and in this second condenser 50, the non-azeotropic mixture medium Returned to the liquid. The liquid fractionated by the fractionator 48 is returned to the second condenser 50 through the liquid return channel 62. In this embodiment, a fourth heat exchanger 64 is disposed between the second condenser 50 and the second heat exchanger 44, and the fourth heat exchanger 64 does not flow through the first branch flow path 54. Heat exchange is performed between the azeotropic mixing medium and the non-azeotropic mixing medium flowing through the liquid return flow path 62, and the non-azeotropic mixing medium heated by this heat exchange is sent to the second heat exchanger 44. The

  In this cogeneration system, a steam turbine 26 and a low-temperature steam turbine 42 are provided on a rotating shaft 66, and the rotating shaft 66 is drivingly connected to a generator 68 for the turbine. Accordingly, when the steam turbine 26 is rotated by the steam and the low-temperature steam turbine 42 is rotated by the steam of the non-azeotropic mixture medium, the generator 68 is operated via the rotating shaft 66 to generate power. In this cogeneration system, the heat of the exhaust gas of the engine 6 is recovered in the first heat recovery system 22, and the heat of the exhaust gas of the engine 6 and the heat of the cooling water of the engine 6 are recovered in the second heat recovery system 24. These heats can be recovered to generate electricity. Note that the rotation shaft 66 of the steam turbine 26 and the low-temperature steam turbine 42 may be connected to a pump, a compressor, various mechanical devices, and the like to extract heat recovered from the exhaust gas and the cooling water as power.

  In this cogeneration system, a non-azeotropic mixture medium of ammonia and water is used as a working medium for operating the low-temperature steam turbine 42. Therefore, in order to prevent leakage of ammonia to the outside in particular, the turbine device 2 The following sealing means 72 is provided. Referring mainly to FIG. 2, the low-temperature steam turbine 42 includes a turbine housing 76 that defines a turbine chamber 74, and turbine blades 78 accommodated in the turbine housing 76. The seal means 72 is disposed on both sides of the turbine blade 78 so as to rotate integrally.

  A pair of projecting portions 80, 82 projecting on both sides are provided at both ends of the turbine housing 76, and the outer diameter of the predetermined portion of the rotating shaft 66 is somewhat larger corresponding to the pair of projecting portions 80. Diameter portions 84 and 86 are provided, and the sealing means 72 is provided in association with the protruding portions 80 and 82 and the large diameter portions 84 and 86. The sealing means 72 has substantially the same configuration, and what is provided in relation to the one projecting portion 80 and the large diameter portion 84 will be described below.

  The illustrated sealing means 72 includes an inner sealing means 88 disposed on the inner side in the axial direction (left-right direction in FIG. 2) and an outer sealing means 90 disposed on the outer side. The inner seal means 88 includes an inner seal member 94 and an outer seal member 96 disposed on the outer side in the axial direction of the inner seal member 94. The inner seal member 94 is attached to an annular groove 92 provided in the large-diameter portion 84 of the rotary shaft 66 and is supported in the axial direction by an annular support member 93 attached to the rotary shaft 66. The outer seal member 94 is attached to the inner side surface of the inner portion of the projecting portion 80 of the turbine housing 76 via a coil spring 98 (constituting elastic biasing means), and the outer seal member 94 is axially moved by the action of the coil spring 98. It is biased elastically toward the inner seal member 94 in the direction.

  With this configuration, when the rotation of the rotating shaft 66 (the low temperature steam turbine 42) is stopped, the tip of the outer seal member 94 is brought into contact with the side surface of the inner seal member 94 by the action of the coil spring 98. It is elastically pressed, and the space between the projecting portion 80 and the large-diameter portion 84 of the rotating shaft 66 is hermetically sealed, and the vapor of the non-azeotropic mixture medium (particularly ammonia) in the turbine chamber 74 leaks to the outside. Absent. Further, when the rotary shaft 66 is rotating, the outer seal member 94 is slightly separated from the inner seal member 94 against the elastic force of the coil spring 98, and the inner seal member 92 rotates without contact with the outer seal member 96. Move.

  Further, the outer seal means 90 is constituted by an annular seal member 100, and this annular seal member 100 is attached to the inner peripheral surface of the outer portion of the projecting portion 80 of the turbine housing 76 (the outer portion in the axial direction of the inner portion). It is provided in contact with or close to the outer peripheral surface of the large diameter portion 84 of the rotating shaft 66.

  The turbine apparatus 2 is further configured to introduce water vapor into the annular space 102 between the inner seal means 88 and the outer seal means 90. In other words, the turbine device 2 is provided with a steam introduction line 04, and one branch line 106 of the steam introduction line 104 is communicated with the annular space 102 defined in one protrusion 80 of the turbine housing 76, and the other branch. A line 108 communicates with the annular space 102 defined in the other protrusion 82 of the turbine housing 76. The steam introduction line 104 is connected to the steam generation means 110. The steam generating means 110 includes a boiler body 112, and a heater 114 is disposed in the boiler body 112. Water generated in the boiler body 112 is heated by the heat generated by the heater 114, and steam is generated. The steam is fed through the steam introduction line 104.

  A pressure control valve 116 is disposed in the steam introduction line 104, and the pressure control valve 116 adjusts the pressure of the steam supplied to the annular space 102 of the turbine apparatus 2 through the steam introduction line 104. In the turbine device 2, the pressure of the steam supplied through the steam introduction line 104 is set in the turbine chamber 74 in order to prevent leakage of a non-azeotropic mixture medium (particularly ammonia) during rotation of the rotary shaft 66. It is important to make the pressure higher than the vapor pressure of the non-azeotropic medium, and the pressure control valve 116 sets the water vapor pressure so as to have the above-described pressure relationship.

  A water supply line 118 is also connected to the boiler body 112, and a water supply pump 120 is disposed in the water supply line 118. Further, the boiler body 112 is provided with a water level detection sensor 122. The water level detection sensor 122 detects the water level in the boiler body 112, and a detection signal from the water level detection sensor 122 is sent to the controller 124. The When the water level detection sensor 122 detects a decrease in the water level, the controller 124 operates the water supply pump 120 based on the water level decrease signal from the water level detection sensor 122, and the water supply pump 120 acts through the water supply line 118. Water is supplied to the boiler body 112. Further, when the water level detection sensor 122 detects a rise in the water level, the controller 124 stops the operation of the water supply pump 120 based on the water level rise signal from the water level detection sensor 122 and supplies water through the water supply line 118. Is stopped. Since the water supply pump 120 is controlled in this manner, the water level in the boiler body 112 is kept at a constant level.

  In the turbine device 2, when the turbine blades 78 (rotary shaft 66 integrally therewith) of the low-temperature steam turbine 42 are rotated by the steam of the non-azeotropic mixed medium, the steam generating means 110 is operated, The steam generated by the generating means 110 is fed to the annular space 102 of the projecting portions 80 and 82 of the turbine housing 76 through the steam introduction line 104. Since the pressure of the water vapor is adjusted by the pressure control valve 116 to be higher than the vapor pressure of the non-azeotropic mixture medium in the turbine chamber 74, the water vapor supplied to the annular space 102 is the inner sealing means 88. The gas flows into the turbine chamber 74 through the gap between the inner seal member 94 and the outer seal member 96, and the non-azeotropic mixture medium (especially ammonia) in the turbine chamber 74 is externally passed through the gap. It is possible to reliably prevent leakage. Although the steam supplied to the annular space 102 through the steam introduction line 104 somewhat flows into the turbine chamber 74, the non-azeotropic mixture medium originally contains water. There is no problem. Further, the water vapor supplied to the annular space 102 leaks to the outside somewhat through the outer sealing means 90 (the gap between the annular seal member 100 and the large diameter portions 84 and 86 of the rotating shaft 66), but it is the water vapor that leaks. Therefore, even if it leaks somewhat, it does not become a problem.

  In the turbine apparatus 2 provided with the sealing means 72 as described above, the steam is introduced into the annular space 102 between the inner sealing means 88 and the outer sealing means 90 through the steam introduction line 104. Further, leakage of the non-azeotropic mixture medium in the turbine chamber 74 to the outside can be reliably prevented.

  Next, a modification of the turbine apparatus will be described with reference to FIG. In the following embodiments, members that are substantially the same as those in the embodiment shown in FIGS. 1 and 2 are given the same reference numerals, and descriptions thereof are omitted.

  In FIG. 3, in this modified turbine apparatus 2A, the sealing means 72A includes an intermediate sealing means 132 in addition to the inner sealing means 88 and the outer sealing means 90, and the intermediate sealing means 132 is a protrusion 80A of the turbine housing 76A. , 82A. The intermediate sealing means 132 is disposed between the inner sealing means 88 and the outer sealing means 90, and the inner peripheral portion of the tip is located close to the outer peripheral surface of the rotating shaft 66. An inner annular space 134 is defined between the sealing means 132 and an outer annular space 136 is defined between the intermediate sealing means 132 and the outer sealing means 90. The configuration of the inner sealing means 88 and the outer sealing means 90 is substantially the same as that of the above-described embodiment.

  In relation to this, one end side of the water vapor introduction line 104 communicates with the outer annular space 136, and the other end side is connected to the water vapor generating means (see FIG. 2) in the same manner as in the above embodiment. That is, one branch line 106 of the steam introduction line 104 is communicated with the outer annular space 136 defined by one protrusion 80A of the turbine housing 76A, and the other branch line 108 is connected to the other protrusion 82A of the turbine housing 76A. Are communicated with the outer annular space 136 defined in FIG. Further, the inner annular space 134 defined in one projecting portion 80A of the turbine housing 76 is communicated with an engine exhaust passage (see FIG. 1) via a steam outlet line 138, and is defined in the other projecting portion 82A. The inner annular space 134 communicated with the exhaust flow path via the water vapor outlet line 140. Note that the water vapor outlet lines 138 and 140 may communicate with the exhaust passage through a common outlet line. Other configurations of this modified embodiment are substantially the same as those of the above-described embodiment.

  In the turbine apparatus 2A of this modified embodiment, when the turbine blade 78 of the low-temperature steam turbine 42 (rotary shaft 66 integrally therewith) is rotated by the steam of the non-azeotropic mixture medium, the steam generating means (not shown) The water vapor generated at (1) is fed to the outer annular space 136 of the projecting portions 80A, 82A of the turbine housing 76A through the water vapor introduction line 104 (first and second branch lines 106, 108). Since the water vapor pressure is set to be higher than the vapor pressure of the non-azeotropic mixture medium in the turbine chamber 74 as in the above-described embodiment, the water vapor supplied to the annular space 132 is It flows into the inner annular space 134 on the inner side in the axial direction through the intermediate sealing means 132 (the gap between the inner peripheral portion thereof and the large diameter portions 84 and 86 of the rotating shaft 66). A part of the steam thus flowed flows into the turbine chamber 74 through a gap between the inner seal member 94 and the outer seal member 96 of the inner seal means 88, and the steam flow causes non-co-retention in the turbine chamber 74. It is possible to reliably prevent the boiling mixed medium (in particular, ammonia) from leaking through the gap. Most of the water vapor flows into the exhaust passage of the engine 6 through the steam outlet lines 138 and 140, and is discharged to the outside together with the exhaust gas flowing through the exhaust passage. If a non-azeotropic mixed medium (particularly ammonia) leaks from the turbine chamber 74 to the inner annular space 134, the leaked non-azeotropic mixed medium vapor passes through the water vapor outlet lines 138 and 140 together with the water vapor flow described above. It flows in the exhaust passage of the engine. An NOx catalyst for reducing the concentration of NOx (nitrogen oxide) is often disposed in the exhaust passage of the engine, and when this NOx catalyst is disposed, ammonia in the non-azeotropic mixture medium Reacts with NOx in the exhaust gas under the NOx catalyst to reduce the NOx concentration in the exhaust gas.

  Even at this time, the water vapor fed from the water vapor introduction line 104 to the inner annular space 134 through the outer annular space 136 somewhat flows into the turbine chamber 74. However, as described above, this is particularly problematic. There is no. Further, the water vapor supplied to the outer annular space 136 leaks to the outside somewhat through the outer sealing means 90, but such leakage is not particularly problematic.

  In the turbine apparatus 2A provided with the sealing means 72A as described above, steam is introduced into the outer annular space 136 between the outer sealing means 90 and the intermediate sealing means 132 through the steam introduction line 104, and then the intermediate sealing means 132 is introduced. The intermediate seal means 132 and the inner seal means 88 are introduced into the inner annular space 134 between the intermediate seal means 132 and the inner seal means 88, so that the flow of water vapor reliably prevents the non-azeotropic mixture medium in the turbine chamber 74 from leaking to the outside. Can do. Further, since the water vapor is led out from the inner annular space 134 to the engine exhaust passage through the water vapor lead-out lines 38 and 140, even if the vapor of the non-azeotropic mixed medium (particularly ammonia) leaks from the turbine chamber 74, The leaked steam flows into the engine exhaust passage along with the flow of water vapor, and can be processed as required together with the exhaust gas discharged through the exhaust passage.

  Next, with reference to FIG. 4, a turbine apparatus according to another modified embodiment will be described. In this other modification, a dedicated steam generating means for generating steam is omitted, and the steam generated in the first heat recovery system 22B is supplied through the steam introduction line 152. .

  In FIG. 4, in this modified embodiment, a steam introduction line 152 is provided that branches from the first circulation passage 32 (a portion between the first heat exchanger and the steam turbine 26) of the first heat recovery system 22 </ b> B, The first branch line 154 of the water vapor introduction line 152 is communicated with an annular space between the inner seal means and the outer seal means of one seal means 72, and the second branch line 156 is connected to the inner side of the other seal means 72. A pressure control valve 116 is provided between the sealing means and the outer sealing means. The pressure control valve 116 is provided in the water vapor introduction line 152 to set the pressure of the supplied water vapor. Other configurations of the other modifications may be substantially the same as the embodiment shown in FIGS. 1 and 2.

  In such a turbine device 2B, a part of the steam supplied to the steam turbine 26 is supplied to the annular space defined between the inner seal means and the outer seal means of the seal means 72 through the steam introduction line 152. As a result, a dedicated water vapor generating means for generating water vapor is not required, and the configuration necessary for introducing water vapor can be simplified.

  In the above-described modification, a part of the steam supplied to the steam turbine 26 is used, in other words, steam generated using the heat of the exhaust gas from the engine is introduced through the steam introduction line 152. However, the present invention is not limited to this, steam may be generated using steam supplied to the low-temperature steam turbine 42, and the steam thus generated may be introduced through the steam introduction line 152.

  As mentioned above, although embodiment of the turbine apparatus according to this invention was described, this invention is not limited to this embodiment, A various deformation | transformation thru | or correction | amendment are possible without deviating from the scope of the present invention.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a simplified diagram illustrating an example of a cogeneration system to which a turbine apparatus according to an embodiment is applied. Sectional drawing which shows a part of turbine apparatus in the cogeneration system of FIG. Sectional drawing which shows a part of turbine apparatus of a deformation | transformation form. The figure which shows a part of turbine apparatus of another deformation | transformation simply.

Explanation of symbols

2, 2A, 2B Turbine device 4 Supercharger 6 Engine 22 First heat recovery system 24 Second heat recovery system 26 Steam turbine 42 Low temperature steam turbine 66 Rotating shaft 72, 72A Sealing means 74 Turbine chamber 76 Turbine housing 88 Inner sealing means DESCRIPTION OF SYMBOLS 90 Outer seal means 102 Annular space 104,152 Steam introduction line 110 Steam generation means 116 Pressure control valve 132 Intermediate seal means 134 Inner annular space 136 Outer annular space 138,140 Steam release line

Claims (2)

Turbine housing defining a turbine blade to be rotated non-azeotropic mixed medium of ammonia and water as working medium, a rotary shaft for rotatably supporting the turbine blades, the turbine chamber for housing the turbine blades And a sealing means for sealing between the rotating shaft and the turbine housing,
The seal means seals between an inner portion of the turbine housing and the rotary shaft, and seals between an outer portion located on the outer side in the axial direction from the inner portion of the turbine housing and the rotary shaft. Water vapor introduced from the water vapor introduction line , comprising: an outer seal means for performing the operation, an intermediate seal means provided between the inner seal means and the outer seal means, and a water vapor introduction line for introducing water vapor. Is introduced into the outer annular space between the outer seal means and the intermediate seal means, and the pressure of the steam introduced from the steam introduction line is higher than the steam pressure of the working medium introduced into the turbine chamber. An inner annular space between the intermediate sealing means and the inner sealing means is provided for generating the working medium. Turbine unit, characterized in that in communication with the gin of the exhaust system. The rotating shaft is further provided with a steam turbine blade that is rotated using steam as a working medium, and a part of the steam as the working medium passes through the steam introduction line and the intermediate sealing means and the outer sealing means. The turbine apparatus according to claim 1 , wherein the turbine apparatus is introduced into the outer annular space in between.

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