• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    An exhaust gas turbine (20), waste heat recovery system (1), and method of operating a waste heat recovery system, the exhaust gas turbine having a turbine housing (21), a rotor (23) rotatably supported in the turbine housing, and a plurality of turbine blades (23a) the turbine housing having a plurality of exhaust gas inlet passages (22a, 22b) for passing exhaust gas to the turbine blades via the baffle, the respective exhaust gas inlet passages being separate from one another to the guide grid and wherein in each exhaust gas inlet passage a pressure sensor is arranged to measure an exhaust gas pressure (PI, PII) in the respective exhaust gas inlet passage. With the invention, an improved efficiency in the waste heat recovery can be realized in multi-engine systems while avoiding vibration induction on the turbine blades.
    公开号:CH704827B1
    申请号:CH00354/12
    申请日:2012-03-12
    公开日:2016-01-15
    发明作者:Alfons Bornhorn；Klaus Bartholomä；Alexander Rippl；Stefan Mayr
    申请人:Man Diesel & Turbo Se；
    IPC主号:
    专利说明:

    The invention relates to an exhaust gas turbine, a waste heat recovery system equipped with such an exhaust gas turbine and a method for operating such a waste heat recovery system.
    In marine applications, in multi-engine plants, i. several internal combustion engines having systems to perform respective exhaust strands of the internal combustion engine independently, so as to ensure that a fault in an exhaust line has no effect on the operation of other internal combustion engines.
    If a WHR system (Waste-Heat-Recovery - waste heat recovery) with a waste heat using steam turbine and a Abgasnutzturbine are executed for a multi-engine plant, so usually one exhaust gas turbine is provided per engine.
    However, several smaller Abgasnutzturbinen have disadvantages in terms of poorer efficiency (as a large exhaust gas turbine) and in terms of a complex structure with multiple, high-speed transmissions (as a large, slow-running exhaust gas turbine) with in turn higher losses and additional losses through a collection gear.
    Would merge several exhaust bypass strands before a larger exhaust gas turbine power turbine or turbine, reactions would result in the respective exhaust systems of the internal combustion engine with each other, if the internal combustion engines are operated at different load and the exhaust gas pressures are different.
    The invention has for its object to provide a Abgasnutzturbine, equipped with such a Abgasnutzturbine waste heat recovery system and a method for operating such a waste heat recovery system, which in multi-engine systems while avoiding vibration induction on the turbine blades improved efficiency in waste heat recovery can be realized.
    This is achieved with an exhaust gas turbine according to claim 1, a waste heat recovery system according to claim 7 and a method according to claim 10. Further developments of the invention are defined in the respective dependent claims.
    According to a first aspect of the invention, an exhaust gas turbine for the energetic use of engine exhaust gas is provided, wherein the exhaust gas turbine has: a turbine housing; a rotor rotatably supported in the turbine housing and having a plurality of turbine blades; a turbine grille disposed in the turbine housing for controlling an exhaust gas flow of the turbine blades, the turbine housing having a plurality of exhaust gas inlet passages for passing via the guide grid exhaust gas to the turbine blades, wherein the respective exhaust gas inlet passages are separated from each other to the guide grid, and wherein in each exhaust gas inlet passage, a pressure sensor arranged to measure an exhaust pressure in the respective exhaust gas inlet passage; and pressure equalizing means connected to the pressure sensors and configured to equalize the respective exhaust gas pressures (PI, PII) in the exhaust gas inlet passages (22a, 22b).
    By the pressure equalization vibration inducement is reliably avoided on the turbine blades. As a result, a single such exhaust gas turbine can be provided for a multi-engine system, and the single exhaust gas turbine can thus be made larger and with a higher degree of efficiency.
    According to one embodiment of the inventive exhaust gas turbine, the turbine blades are designed as undamped, in particular damper wireless, turbine blades.
    Damper wires are used in conventional turbines to dampen vibrations of the free-standing turbine blades, wherein the damping takes place by friction at bearing points of the wire. The damper wires may be passed through holes in the turbine blades. Since these holes represent weak points of the turbine blades, which frequently result in blade fractures, the turbine blades are usually thickened in the area of the holes. Damper wires are in any case disturbances of the flow around the turbine blade profile and thus reduce the efficiency of the turbine.
    Due to the inventive design of the turbine blades as undamped, in particular damper wireless, turbine blades such efficiency reduction is avoided.
    According to a further embodiment of the inventive exhaust gas turbine, the Druckangleichmittel are formed by each exhaust gas inlet passage is arranged to regulate the pressure in the respective exhaust gas inlet passage pressure regulating device, wherein the respective pressure sensors and the respective pressure control devices are connected to a turbine control device, and wherein the turbine control device is arranged to control the respective pressure control devices based on the measured from the respective pressure sensors exhaust gas pressures to regulate the exhaust gas pressures in all exhaust gas inlet passages to a uniform desired pressure level.
    According to yet another embodiment of the inventive exhaust gas turbine, the uniform desired pressure level with a control deviation of the exhaust gas pressures from each other of ≤1,0 bar specified.
    According to yet another embodiment of the exhaust gas turbine according to the invention, each pressure regulating device has a throttle device for throttling an exhaust gas inflow into the respective exhaust gas inlet passage.
    Alternatively or additionally, according to a further embodiment of the exhaust gas turbine according to the invention, each pressure regulating device has a bypass device for branching off exhaust gas from an exhaust gas inflow into the respective exhaust gas inlet passage.
    According to a second aspect of the invention, there is provided a waste heat recovery system comprising: a plurality of internal combustion engines, each internal combustion engine having a separate exhaust line, and a single exhaust gas turbine according to one, several or all previously described embodiments of the first aspect of the invention in every conceivable embodiment A combination wherein the exhaust line of a first internal combustion engine of the internal combustion engine for introducing exhaust gas is connected to a first exhaust gas inlet passage of the exhaust gas inlet passages of the exhaust gas turbine, and wherein the exhaust line of a second internal combustion engine of the internal combustion engine is connected to a second exhaust gas inlet passage of the exhaust gas inlet passages of the exhaust gas turbine.
    By the pressure equalization vibration inducement is reliably avoided on the turbine blades. Characterized in that a single inventive exhaust gas turbine is provided for the waste heat recovery system, this single exhaust gas turbine can be made larger and thus with higher efficiency.
    According to one embodiment of the waste heat recovery system according to the invention this further comprises: a steam turbine and in each exhaust line, a heat exchanger with a primary strand, which is adapted for the passage of exhaust gas, and a secondary strand, which is adapted to provide steam, wherein the secondary strands of the respective heat exchanger are connected to a steam inlet of the steam turbine.
    According to a further embodiment of the inventive waste heat recovery system, this further comprises an electric generator, wherein a drive shaft of the electric generator can be brought into rotational drive connection both with a rotationally driven by the rotor of the exhaust gas turbine output shaft of the exhaust gas turbine and with a rotationally driven by a rotor of the steam turbine output shaft of the steam turbine ,
    According to a third aspect of the invention there is provided a method of operating a waste heat recovery system according to one, several or all previously described embodiments of the second aspect of the invention in any conceivable combination, the method comprising the steps of: measuring the exhaust gas pressures in the respective exhaust gas inlet passages the exhaust gas turbine, comparing the measured exhaust gas pressures, and matching the respective exhaust gas pressures in the exhaust gas inlet passages.
    By the pressure equalization vibration inducement is reliably avoided on the turbine blades. Characterized in that a single inventive exhaust gas turbine is provided for in the waste heat recovery system, this single exhaust gas turbine can be made larger and thus with higher efficiency.
    According to one embodiment of the inventive method, comparing the measured exhaust gas pressures also includes determining a lowest exhaust gas pressure of the measured exhaust gas pressures, the remaining exhaust gas pressures are determined as higher pressure exhaust gas pressures, from the lowest exhaust pressure, a desired pressure level is determined, and wherein, as the respective exhaust pressures in the exhaust gas inlet passages match, the higher pressure exhaust pressures are reduced to the desired pressure level.
    According to a further embodiment of the inventive method, the uniform desired pressure level with a control deviation of the exhaust gas pressures from each other of ≤ 1.0 bar adjusted.
    According to yet a further embodiment of the method according to the invention, reducing the exhaust gas pressures of higher pressure is carried out by throttling a respective exhaust gas inflow into the respective exhaust gas inlet passages.
    Alternatively or additionally, according to yet another embodiment of the method according to the invention, reducing the exhaust gas pressures of higher pressure is carried out by branching off exhaust gas from a respective exhaust gas inflow into the respective exhaust gas inlet passages.
    The invention expressly extends to such embodiments, which are not given by combinations of features of explicit back references of the claims, with which the disclosed features of the invention - as far as is technically feasible - can be combined with each other.
    In summary it should be mentioned that was recognized by the inventors as a solution an exhaust gas turbine or power turbine with a plurality of inlet nozzle, i. with a shock-charging-like turbine housing, wherein the exhaust gas streams are mixed only after the turbine guide (nozzle ring) and thus do not affect, so that there is no feedback.
    The inventors have also recognized that turbines in the boost charging operation experience higher vibration excitations on their turbine blades due to the non-uniformity of the exhaust gas supply, which is why robust turbines with damping wire or damping elements and thus poorer efficiency would be necessary.
    As a solution, it is therefore proposed by the inventors to form the turbine blades dämpferdrahtlos for best efficiencies, wherein the problem of caused by non-uniform loading vibration excitation of the turbine blades is reduced or eliminated by individually throttled the pressure in the individual exhaust ducts or exhaust gas inlet passages is, so that the exhaust gas inlet passages are operated at the same pressure as possible and thus speed level.
    This is shown, e.g. by measuring the respective pressures in an inflow pipe in front of the turbine and regulating the respective higher pressure by throttling and / or bypass control. The throttle operation leads to a higher exhaust gas pressure, which benefits a connected internal combustion engine and leads to a better charging of this, as far as a maximum ignition pressure permits. In bypass mode, the residual heat in the exhaust gas can be raised and converted into a steam turbine.
    This may result in a WHR system for at least two internal combustion engines, consisting of a steam turbine and an exhaust gas turbine, together on a train with e.g. a generator mounted. Furthermore, there may result an exhaust gas turbine with at least two inlets (equal to the number of internal combustion engines to be interconnected, without damper wire for the best possible efficiency.) Furthermore, there may be a regulation with pressure measurement and control devices, which ensures that the exhaust gas pressures upstream of the turbine respectively similar level are (control deviation eg <= 1.0 bar)
    In the following the invention with reference to a preferred embodiment and with reference to the accompanying figures will be described in more detail.<Tb> FIG. 1 <SEP> is a schematic of a standard waste heat recovery system.<Tb> FIG. 2 <SEP> is a circuit diagram of a waste heat recovery system according to an embodiment of the invention.<Tb> FIG. FIG. 3 shows a partial perspective view of an exhaust gas turbine according to an embodiment of the invention. FIG.<Tb> FIG. FIG. 4 shows, in two perspective partial views, a part of a turbine housing of the exhaust gas turbine of FIG. 3 cut on a plane A in FIG. 3.<Tb> FIG. FIG. 5 shows a view similar to FIG. 2, with some elements of the waste heat recovery system according to the invention being omitted for the sake of clarity.
    FIG. 1 shows a circuit diagram of a standard waste heat recovery system 1 integrated into a ship (not fully illustrated and not separately labeled).
    The waste heat recovery system 1 of Fig. 1 comprises a first internal combustion engine 10 and a second internal combustion engine 50, which serve to drive the ship.
    Each internal combustion engine 10, 50 has a separate exhaust line 15 and 55 with respective exhaust gas outlet 16 and 56 (here a chimney), a separate exhaust gas turbine power turbine 20 and 60, respectively the respective associated exhaust line 15 or 55 is connected, so that the exhaust gas turbines 20, 60 can be driven via the exhaust gas of their respective exhaust line 15 and 55, a separate heat exchanger 25 and 65, the Steam generation with a primary strand 25a and 65a which is integrated into the respectively associated exhaust line 15 and 55, and two exhaust gas turbochargers 30a, 30b and 70a, 70b (with respective exhaust gas turbine and respective compressor - not separately designated), which are connected to the respective associated exhaust line 15 and 55 for turbocharging the respective internal combustion engine 10 and 50 respectively.
    The exhaust heat recovery system 1 of FIG. 1 further includes a steam turbine 75 and an electric generator 80. The steam turbine 75 is connected to each of respective secondary strands 25b and 65b of the heat exchangers 25, 65, respectively, so that the steam turbine 75 can be driven by steam generated by the heat exchangers 25, 65.
    The two exhaust gas turbines 20, 60 are the output side selectively selectively connected to a drive shaft 81 of the electric generator 80 via a collecting gear 85. The steam turbine 75 is rotationally driven via a transmission 90 on the output side with the drive shaft 81 of the electric generator 80 connected.
    Now, with reference to Figs. 2 to 5, a waste heat recovery system 1 integrated into a ship (not fully illustrated and not separately referred to) according to an embodiment of the invention will be described.
    The inventive waste heat recovery system 1 comprises a first internal combustion engine 10 and a second internal combustion engine 50, which serve to drive the ship.
    Each internal combustion engine 10, 50 has a separate exhaust line 15 or 55 with a plurality of exhaust pipes (not separately designated) and with respective exhaust gas outlet 16 and 56 (hiereinem a chimney), a separate heat exchanger 25 and 65, for generating steam with a configured for passing exhaust gas primary train 25a and 65a which is integrated into the respective associated exhaust line 15 and 55, and two exhaust gas turbocharger 30a, 30b and 70a, 70b (with respective exhaust gas turbine and respective compressor - not separately designated), the are connected to the respective associated exhaust line 15 and 55 for turbocharging the respective internal combustion engine 10 and 50 respectively.
    The inventive waste heat recovery system 1 further comprises the energetic use of engine exhaust gas to a Abgasnutzturbine or Powerturbine 20, which is connected via exhaust pipes to the two exhaust lines 15, 55, so that the exhaust gas turbine 20 via the exhaust gas of the two exhaust lines 15, 55 driven can be.
    As can be seen in particular in FIGS. 2, 3 and 5, the exhaust gas turbine 20 has a turbine housing 21 with a Turbinenzuströmgehäuse 22, a rotor 23 (only schematically and partially shown), which is rotatably mounted in the turbine housing 21 and a plurality of undamped, in particular damperless, turbine blades 23a, a turbine grille 21 arranged in the guide grid 24 (or a nozzle ring) for controlling an exhaust gas flow of the turbine blades 23a and an exhaust diffuser 24a on for discharging the exhaust gas from the exhaust gas turbine 20.
    The turbine inlet housing 22 of the turbine housing 21 has a plurality of exhaust gas inlet passages for passing exhaust gas to the turbine blades 23a via the guide rail 24, the respective exhaust gas inlet passages being separate from each other to the guide grid 24. According to the embodiment of the invention described in FIGS. 2 to 5, the turbine inlet housing 22 of the turbine housing 21 has a first exhaust gas inlet passage 22a and a second exhaust gas inlet passage 22b, which are separated from each other in terms of flow from shortly before directly to the guide grid 24 via a partition wall 22c , FIG. 4 shows, in two perspective partial views, a part of the turbine inlet housing 22 which is cut on a plane A in FIG. 3 and is similar to a "trouser piece".
    The exhaust line 15 of the first internal combustion engine 10 is connected to the inlet of exhaust gas to the first exhaust gas inlet passage 22a of the exhaust gas turbine 20. The exhaust line 55 of the second internal combustion engine 50 is connected to the second exhaust gas inlet passage 22 b of the exhaust gas turbine 20 for introducing exhaust gas.
    Although not shown in Figs. 2-5, in each of the exhaust gas inlet passages 22a, 22b, a pressure sensor is arranged to measure an exhaust gas pressure PI or PII (see Fig. 2) in the respective exhaust gas inlet passage 22a, 22b.
    Each exhaust gas inlet passage 22a, 22b is preceded by a pressure regulating device 60a, 60b provided for regulating the exhaust gas pressure PI or Pll in the respective exhaust gas inlet passage 22a, 22b. Each pressure control device 60a, 60b has an electronic control unit 61a or 61b and a first preferably electromotive (marked with "M") controllable valve 62a and 62b and a second preferably electromotive (marked with "M") controllable valve 63a and 63b , The first and second valves 62a, 63a and 62b, 63b are electrically connected to their associated control units 61a and 61b for driving, respectively.
    The first valve 62a, 62b of each pressure regulating device 60a, 60b acts as a throttle device for throttling an exhaust gas inflow into the respectively assigned exhaust gas inlet passage 22a, 22b, respectively. The second valve 63a, 63b of each pressure regulator 60a, 60b functions as a bypass means for branching exhaust gas from the exhaust gas inflow into the respective associated exhaust gas inlet passages 22a, 22b, respectively.
    The waste heat recovery system 1 according to the invention also has an electronic turbine control device 100, which is electrically connected to the respective pressure sensors for signal reception and for driving with the control units 61a, 61b of the respective pressure control devices 60a, 60b. The turbine control apparatus 100 is configured to drive the control units 61a, 61b of the respective pressure control devices based on the exhaust pressures PI, PII measured by the respective pressure sensors to increase the exhaust pressures PI, Pll in all the exhaust gas inlet passages 22a, 22b to a uniform target pressure level regulate. The uniform desired pressure level is preferably predetermined by a control deviation of the exhaust gas pressures PI, Pll from ≤ 0.2 bar.
    In conclusion, the pressure control devices 60a, 60b and the turbine control device 100 form pressure equalizing means connected to the pressure sensors and configured to match the respective exhaust pressures PI, Pll in the exhaust gas inlet passages 22a, 22b.
    The inventive waste heat recovery system 1 also has a steam turbine 75 and an electric generator 80. A steam inlet (not separately indicated) of the steam turbine 75 is connected via steam lines (not separately labeled) to each of the secondary steam supply lines 25b and 65b of the heat exchangers 25, 65, respectively, so that the steam turbine 75 is connected by both heat exchangers 25, 65 generated steam can be driven.
    A drive shaft 81 of the electric generator 80 is via a gear 85 with a rotationally driven by the rotor 23 of the exhaust gas turbine 20 output shaft 23b of the exhaust gas turbine 20 and via a gear 90 with a of a rotor (not labeled) of the steam turbine 75 rotationally driven output shaft 75a of the steam turbine 75 can be brought into rotary drive connection.
    In the embodiment shown, the exhaust gas turbine 20 via the gear 85 and a clutch (not labeled) selectively drivingly connected to the drive shaft 81 of the electric generator 80 and the steam turbine 75 via the transmission 90 on the output side continuously with the drive shaft 81 of the electric generator 80th rotary drive connected.
    According to a method according to the invention for operating the waste heat recovery system 1 described in FIGS. 2-5, at least the following steps are carried out:by means of the pressure sensors measure the exhaust gas pressures PI, Pll in the respective exhaust gas inlet passages 22a, 22b,in the turbine control apparatus 100 compare the measured exhaust pressures PI, Pll, andby the pressure equalizing means, matching the respective exhaust pressures PI, Pll in the exhaust gas inlet passages 22a, 22b.
    According to the method, comparing the measured exhaust gas pressures PI, Pll also includes determining a lowest exhaust gas pressure of the measured exhaust gas pressures PI, Pll, wherein the remaining exhaust gas pressures are determined as higher pressure exhaust pressures, wherein from the lowest exhaust pressure determines a desired pressure level and, when the respective exhaust pressures PI, Pll in the exhaust gas inlet passages 22a, 22b become equal to each other, the higher pressure exhaust gas pressures are reduced to the target pressure level by the pressure regulating devices 60a, 60b.
    According to the method, the uniform target pressure level is preferably adjusted from one another by ≤ 0.2 bar with a control deviation of the exhaust gas pressures PI, Pll.
    According to the method, reducing the higher pressure exhaust gas pressures is preferably performed by throttling the exhaust gas inflow into the higher pressure exhaust gas inlet passage (s) by partially closing the first valve 62a or 62b of the pressure regulating device 60a, 60b in question.
    Alternatively or additionally, according to the method, reducing the higher pressure exhaust gas pressures is preferably performed by diverting exhaust gas from the exhaust gas inlet into the higher pressure exhaust gas inlet passage (s) by opening the second valve 63a or 63b of the respective pressure regulator 60a, 60b.
    According to the method, the internal combustion engines 10, 50 are operated with a more than 50% divergent engine load, while still with respect to the internal combustion engine 10, 50 feedback-free operation of the single generator-coupled exhaust gas turbine 20 is ensured.
    LIST OF REFERENCE NUMBERS
    [0060]<tb> 1, 1 <SEP> waste heat recovery system<tb> 10, 10 <SEP> Internal combustion engine<tb> 15, 15 <SEP> Exhaust system<tb> 16, 16 <SEP> Exhaust outlet<tb> 20, 20 <SEP> Exhaust gas turbine<Tb> 21 <September> turbine housing<Tb> 22 <September> Turbinenzuströmgehäuse<tb> 22a, 22b <SEP> Exhaust gas inlet passage<Tb> 22c <September> Partition<Tb> 23 <September> Rotor<Tb> 23 <September> turbine blade (s)<Tb> 23b <September> output shaft<Tb> 24 <September> guide grid<Tb> 24 <September> outlet diffuser<tb> 25, 25 <SEP> Heat Exchangers<tb> 25a, 25a <SEP> primary strand<tb> 25b, 25b <SEP> Secondary strand<tb> 30a, 30a <SEP> Turbocharger<tb> 30b, 30b <SEP> Turbocharger<tb> 50, 50 <SEP> Internal combustion engine<tb> 55, 55 <SEP> Exhaust system<tb> 56, 56 <SEP> Exhaust outlet<tb> 60 <SEP> Exhaust gas turbine<tb> 60a, 60b <SEP> Pressure Regulator<tb> 61a, 61b <SEP> Control unit<tb> 62a, 62b <SEP> Valve<tb> 63a, 63b <SEP> Valve<tb> 65, 65 <SEP> Heat Exchangers<tb> 65a, 65a <SEP> primary strand<tb> 65b, 65b <SEP> Secondary strand<tb> 70a, 70a <SEP> Turbocharger<tb> 70b, 70b <SEP> Turbocharger<tb> 75, 75 <SEP> Steam Turbine<Tb> 75a <September> output shaft<tb> 80, 80 <SEP> Electric generator<tb> 81, 81 <SEP> Drive Shaft<Tb> 85 <September> Gear<tb> 85 <SEP> Collective gear<tb> 90, 90 <SEP> Transmission<Tb> 100 <September> turbine control device<tb> PI, Pll <SEP> Exhaust pressure<Tb> A <September> (cut) level
    权利要求:
    Claims (14)
    [1]
    An exhaust gas turbine (20) for energetically using engine exhaust gas, comprising: a turbine housing (21) and a rotor (23) rotatably supported in the turbine housing (21) and having a plurality of turbine blades (23a) and one in the turbine housing (21) arranged Leitgitter (24) for controlling an exhaust gas flow of the turbine blades (23a),wherein the turbine housing (21) has a plurality of exhaust gas inlet passages (22a, 22b) for passing exhaust gas to the turbine blades (23a) via the baffle (24), the respective exhaust gas inlet passages (22a, 22b)are separated from each other to the guide grid (24), andwherein in each exhaust gas inlet passage (22a, 22b) a pressure sensor is arranged to measure an exhaust gas pressure (PI, Pll) in the respective exhaust gas inlet passage (22a, 22b), andPressure equalizing means connected to the pressure sensors and arranged to match the respective exhaust gas pressures (PI, Pll) in the exhaust gas inlet passages (22a, 22b).
    [2]
    Second exhaust gas turbine (20) according to claim 1, wherein the turbine blades (23a) are formed as dämpferdrahtlose turbine blades.
    [3]
    3. exhaust gas turbine (20) according to claim 1 or 2, wherein the Druckangleichmittel are formed by each exhaust inlet passage (22a, 22b) for regulating the exhaust pressure (PI, Pll) in the respective exhaust gas inlet passage (22a, 22b) arranged pressure control device (60a, 60b), wherein the respective pressure sensors and the respective pressure regulating devices (60a, 60b) are connected to a turbine control device (100), and wherein the turbine control device (60a, 60b) is arranged, the respective pressure regulating devices (60a, 60b) based on to control exhaust gas pressures (PI, Pll) measured by the respective pressure sensors, to regulate the exhaust gas pressures (PI, Pll) in all exhaust gas inlet passages (22a, 22b) to a uniform desired pressure level.
    [4]
    4. exhaust gas turbine (20) according to claim 3, wherein the uniform desired pressure level with a control deviation of the exhaust gas pressures (PI, Pll) from each other by ≤ 1.0 bar is specified.
    [5]
    5. exhaust gas turbine (20) according to claim 3 or 4, wherein each pressure control device (60a, 60b) comprises a throttle device for throttling an exhaust gas inflow into the respective exhaust gas inlet passage (22a, 22b).
    [6]
    6. exhaust gas turbine (20) according to any one of claims 3 to 5, wherein each pressure control device (60a, 60b) has a bypass device for branching off exhaust gas from a flowing into the respective exhaust gas inlet passage (22a, 22b) Abgaszströmömung.
    [7]
    7. waste heat recovery system (1) with:a plurality of internal combustion engines (10, 50), each internal combustion engine (10, 50) having a separate exhaust gas line (15, 55), andan exhaust gas turbine (20) according to one of claims 1 to 6,wherein the exhaust line (15) of a first internal combustion engine (10) of the internal combustion engine (10, 50) is connected to a first exhaust gas inlet passage (22a) of the exhaust gas inlet passages (22a, 22b) of the exhaust gas turbine (20), andwherein the exhaust line (55) of a second internal combustion engine (50) of the internal combustion engine (10, 50) is connected to a second exhaust gas inlet passage (22b) of the exhaust gas inlet passages (22a, 22b) of the exhaust gas turbine (20).
    [8]
    The waste heat recovery system (1) according to claim 7, further comprising: a steam turbine (75) and in each exhaust line (15, 55) a heat exchanger (25, 65) having a primary branch (25a, 65a) adapted to pass exhaust gas , and a secondary line (25b, 65b) adapted to provide steam, the secondary lines (25b, 65b) of the respective heat exchangers (25, 65) being connected to a steam inlet of the steam turbine (75).
    [9]
    9. waste heat recovery system (1) according to claim 8, further comprising an electric generator (80), wherein a drive shaft (81) of the electric generator (80) both with a of the rotor (23) of the exhaust gas turbine (20) rotationally driven output shaft (23 b) of the exhaust gas turbine ( 20) as well as with one of a rotor of the steam turbine (75) rotationally driven output shaft (75 a) of the steam turbine (75) can be brought into rotary drive connection.
    [10]
    10. A method of operating a waste heat recovery system (1) according to any one of claims 7 to 9, comprising:Measuring the exhaust gas pressures (PI, Pll) in the respective exhaust gas inlet passages (22a, 22b),Compare the measured exhaust pressures (PI, Pll), andmatching the respective exhaust pressures (PI, Pll) in the exhaust gas inlet passages (22a, 22b).
    [11]
    11. The method of claim 10, wherein comparing the measured exhaust pressures (PI, Pll) further comprises determining a lowest exhaust pressure of the measured exhaust pressures (PI, PII), the remaining exhaust pressures being determined as higher pressure exhaust pressures, the lower exhaust pressure a desired pressure level is determined; and wherein, when the respective exhaust gas pressures (PI, Pll) in the exhaust gas inlet passages (22a, 22b) match, the higher pressure exhaust gas pressures are reduced to the target pressure level.
    [12]
    12. The method according to claim 11, wherein the uniform desired pressure level with a control deviation of the exhaust gas pressures from each other of ≤ 1.0 bar is adjusted.
    [13]
    13. A method according to claim 11 or 12, wherein reducing the higher pressure exhaust gas pressures is performed by throttling a respective exhaust gas inflow into the respective exhaust gas inlet passages (22a, 22b).
    [14]
    14. A method according to any one of claims 11 to 13, wherein reducing the higher pressure exhaust gas pressures is performed by branching off exhaust gas from the respective exhaust gas inflow flowing into the respective exhaust gas inlet passage (22a, 22b).
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    同族专利:
    公开号 | 公开日
    DE102011007386B4|2016-08-18|
    CN102733857A|2012-10-17|
    CH704827A2|2012-10-15|
    DE102011007386A1|2012-10-18|
    KR101283813B1|2013-07-08|
    KR20120117666A|2012-10-24|
    JP5336629B2|2013-11-06|
    JP2012225343A|2012-11-15|
    CN102733857B|2015-06-17|
    引用文献:
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    法律状态:
    2018-07-31| PFA| Name/firm changed|Owner name: MAN ENERGY SOLUTIONS SE, DE Free format text: FORMER OWNER: MAN DIESEL AND TURBO SE, DE |
    优先权:
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    DE102011007386.8A|DE102011007386B4|2011-04-14|2011-04-14|Exhaust gas utilization turbine, waste heat recovery system and method for operating a waste heat recovery system|
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