CN112805454A - Fluid mechanical device and method for operating a fluid mechanical device - Google Patents
Fluid mechanical device and method for operating a fluid mechanical device Download PDFInfo
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- CN112805454A CN112805454A CN201980063798.5A CN201980063798A CN112805454A CN 112805454 A CN112805454 A CN 112805454A CN 201980063798 A CN201980063798 A CN 201980063798A CN 112805454 A CN112805454 A CN 112805454A
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- 239000012530 fluid Substances 0.000 title claims abstract description 70
- 238000000034 method Methods 0.000 title claims abstract description 25
- 238000010438 heat treatment Methods 0.000 claims description 162
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- 230000006872 improvement Effects 0.000 description 4
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
- F01K7/34—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being of extraction or non-condensing type; Use of steam for feed-water heating
- F01K7/40—Use of two or more feed-water heaters in series
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
- F01K7/16—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type
- F01K7/18—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type the turbine being of multiple-inlet-pressure type
- F01K7/20—Control means specially adapted therefor
Abstract
The present invention relates to an improved fluid machinery apparatus and fluid machinery apparatus control. The invention also relates to a method for optimizing the operation of a fluid mechanical system. The invention also relates to the use of a mass flow for optimizing the operation of a fluid mechanical device.
Description
Technical Field
The invention relates to a fluid mechanical device which can be used better in partial load operation. The invention also relates to a fluid machine control for controlling a fluid machine according to the invention. In addition, the invention relates to a method for better utilization of a fluid machine in partial load operation. The invention also relates to the use of a part of the mass flow for improving the operation of a fluid mechanical device in partial load situations.
Background
Fluid mechanical devices, such as steam turbine devices, are important components in energy production. Not only do fluid mechanical devices operate individually, they are also used in power plants in a manner coupled to, for example, a steam turbine to increase the efficiency of power production. Due to energy conversion, the industry is increasingly faced with the problem of renewable generators feeding fluctuating energy power to the grid. This entails that corresponding fluctuations in the grid need to be compensated by the remaining generators. While the corresponding energy generators (e.g. fluid mechanical systems) in the past were mostly operated continuously at full load, they now have to be operated outside their optimum load for a part of the time, and in particular frequently at partial load, in order to quickly compensate as a reserve for a significant drop in the regeneratively fed power in the electrical network.
However, operation, for example, in particular at low partial loads is a great problem, in particular for steam turbine plants, since the emissions are generally increased significantly here. Below a specific preheating end temperature, the specific process can no longer be operated in the heating group, whereby, for example, a sharp increase in the emission values can be observed. At the same time, however, new and more stringent regulations regarding emissions continue to emerge.
The problem with the existing fluid-mechanical devices is therefore, on the one hand, to be able to ensure flexible operation, but, on the other hand, to overcome these challenges (e.g. stricter emission requirements) at as low a cost as possible. For example, the installation of an additional preheater for separately increasing the preheat end temperature incurs high additional costs and cannot be realized in existing plants for part of the space requirements and safety requirements.
It is therefore desirable to provide a feasible solution that can be optimized for the greatest possible bandwidth of the fluid mechanical device at the lowest possible cost in order to be able to operate these existing devices in the future.
Disclosure of Invention
These objects are achieved by the apparatus, methods and uses described herein and embodied in the claims. The dependent claims and the further description contain advantageous embodiments of the invention which provide further advantages with regard to the additional problems which can also be solved.
According to one aspect, the invention relates to a fluid mechanical device comprising: a turbine, a blade region as an integral part of the turbine, a starting region of the blade region, a heating group, a region before the heating group and a mass flow through the heating group and the turbine, wherein the fluid mechanical device is adapted to conduct a portion of the mass flow after the heating group and before an end of the starting region of the blade region out to the heating group and/or to a region before the heating group, wherein the starting region of the blade region extends over the first 44%, more preferably the first 39%, still more preferably the first 37% of the blade region with respect to the flow direction of the mass flow and the spacing between the start of the starting blade row and the end of the last blade row. In particular, it is generally preferred that a portion of the mass flow is drawn from the region after the heating group and before the overload introduction region. Surprisingly, it has been shown that particularly significant improvements can be achieved in the case of the aforementioned region in which a portion of the mass flow is drawn off. At the same time, the costs associated therewith are relatively low during retrofitting, so that existing systems can be adapted in a simple manner.
The expression "after the heating group" is referred to the direction of the mass flow. Unless otherwise indicated, additional directional or sequential terms, such as "after", "start", "last", etc., are used with reference to the direction of mass flow.
The term "preheater" in the sense of the present invention is a device which increases the temperature of the mass flow before the heating group. This enables the mass flow to reach higher temperatures in the heating group. The preheater can be actively heated, for example, by an electric heater or an external heat source, for example, in addition to a mass flow coupled out of the fluid flow. This also enables, for example, a higher efficiency of the turbomachine to be achieved when the mass flow flowing out of the turbine is used for heating in the preheater. This enables a particularly efficient operation of the fluid mechanical device.
According to one aspect, the invention relates to a turbomachine device comprising a turbine, a blade region in the region of the turbine, an overload introduction region as a constituent part of the turbine, a heating group, a region before the heating group and a mass flow through the heating group and the turbine, wherein the turbomachine device is adapted to lead off and guide a portion of the mass flow after the heating group and before the end of the overload introduction region to the heating group and/or to the region before the heating group. This surprisingly shows that it is particularly advantageous to extract a part of the mass flow in this region and achieve a particularly pronounced effect.
According to a further aspect, the invention relates to a fluid machine control for controlling a fluid machine according to the invention, wherein the fluid machine control is adapted to divert a portion of the mass flow from the region between the heating group and the end of the starting region of the blade region of the turbine to the heating group and/or the region preceding the heating group in the case of a predetermined boundary value.
According to a further aspect, the invention relates to a fluid machine arrangement controller for controlling a fluid machine arrangement according to the invention, wherein the fluid machine arrangement controller is adapted to lead a portion of the mass flow from a region between the heating group and an end of a starting region of a blade region of the turbine to the heating group and/or a region preceding the heating group in case of a predetermined boundary value.
According to a further aspect, the invention relates to a method for providing a part-load optimized operation of a turbomachine, wherein the turbomachine has a turbine, a blade region which is a constituent of the turbine, a starting region of the turbine, a heating group, a region (including, for example, at least one preheater) preceding the heating group, and a mass flow which passes through the heating group and the turbine, wherein a connection between the region which follows the heating group and precedes the end of the starting region of the turbine and the heating group and/or the region which precedes the heating group is provided or retrofitted, wherein the connection is suitable for leading off a part of the mass flow in the case of part-load from a region which follows the heating group and precedes the end of the starting region of the blade region of the turbine and into the heating group and/or into the region which the heating group precedes, wherein the starting region of the blade region extends over the first 44%, more preferably the first 39%, still more preferably the first 37% of the blade region with respect to the flow direction of the mass flow and the spacing between the beginning of the starting blade row and the end of the last blade row, wherein at least two operating modes are provided, wherein in a first operating mode the mass flow is guided from the heating group completely through the starting region, preferably the mass flow is guided through the turbine, wherein in a second operating mode a part of the mass flow is guided from a region after the heating group and before the end of the starting region of the turbine to the heating group and/or to a region before the heating group. It is generally preferred to provide or to retrofit a connection between a region after the heating group and before the end of the starting region of the turbine and a region before the heating group, in particular at least one preheater.
In the sense of the present invention, the expression "guided completely through the turbine" means that the mass flow assumed for the respective turbine from the heating group flows completely through the turbine. Not included here are, in particular, unplanned losses, for example due to leakage, as a result of which small losses of mass flow can occur and the total mass flow directed from the heating group to the turbine is reduced. If a plurality of heating groups are connected in parallel to provide the required mass flow, this naturally means the total resulting mass flow of the heating groups. If there are a plurality of turbines to be connected to a heating group, the corresponding mass flow of each turbine is a proportional fraction of the mass flow obtained from the heating group for each turbine. The combination of multiple heating groups with multiple turbines is derived in a similar manner.
According to a further aspect, the invention relates to a method for operating a turbomachine according to the invention, wherein the turbomachine has an overload inlet line section as a component of a turbine, wherein the method has at least two operating modes, wherein in a first operating mode a mass flow is conducted from a container completely through the turbine, wherein in a second operating mode a part of the mass flow is conducted after a heating group and before the end of the overload inlet region to a region before the heating group and/or the heating group, preferably to a region before the heating group. The overload introduction region is preferably located in the starting region of the blade region of the turbine.
According to a further aspect, the invention relates to a method for providing or retrofitting a turbomachine according to the invention, wherein a connection is provided between a region after the heating group and before the overload introduction region and the heating group and/or a region before the heating group, preferably a region before the heating group, wherein the connection is adapted to guide a part of the mass flow from the overload introduction region to the heating group and/or a region before the heating group, preferably to a region before the heating group, more preferably to the preheater, in the event of partial load.
According to a further aspect, the invention relates to the use of a portion of the mass flow after the heating group of the turbomachine apparatus according to the invention for increasing the inlet temperature in the heating group, wherein the portion of the mass flow is led out from a region between the heating group and the end of the beginning region of the blade region of the turbine.
Drawings
For a more complete understanding of the present invention, reference is made to the following detailed description and accompanying drawings that are related thereto. The drawings described herein are to be regarded as illustrative in nature, and merely as preferred embodiments, and not as restrictive.
Fig. 1 shows a schematic representation of a fluid mechanical device according to a first variant of the invention, wherein the fluid mechanical device is not operated under partial load.
Fig. 2 shows a schematic representation of a fluid mechanical device according to the variant of the invention shown in fig. 1, wherein the fluid mechanical device is operated under partial load.
Fig. 3 shows a schematic representation of a fluid mechanical device according to a second variant of the invention, wherein the fluid mechanical device is operated under partial load.
Fig. 4 shows a schematic representation of a fluid mechanical device according to a third variant of the invention, wherein the fluid mechanical device is operated under partial load.
Detailed Description
The invention enables the operation of the existing fluid-mechanical devices even at very low partial loads, wherein for example the emission values can be greatly reduced. In this case, only a slight adaptation of the existing fluid-mechanical system is required, which can be achieved not only at low cost but also with very little retrofitting time. This not only enables the continuous operation of existing fluid-mechanical plants economically justifiably, but also is an important step in order to achieve a further increase in the share of the renewable energy sources sought in the power industry.
The corresponding fluid mechanical device is for example selected from: a fluidic device based on a water-steam-fluid flow, a fluidic device based on an organic liquid fluid flow or a fluidic device based on a carbon dioxide fluid flow. Organic liquid based fluid streams are for example referred to as organic rankine cycle systems. The carbon dioxide-based fluid stream preferably utilizes carbon dioxide in a supercritical state, where very high temperatures and pressures are used. In particular, in a further embodiment it is preferred that the turbomachine plant is a steam turbine plant. In this case, particularly great improvements are achieved, in particular with regard to emissions. In this case, the heating group is a steam generator.
Furthermore, the invention surprisingly enables the operation of a fluid mechanical plant, in particular a steam turbine plant, below a minimum operating point that provides stable operating conditions, for example evaporation conditions. At the same time, although only slight modifications have been made to the known systems, excellent effects, for example in terms of efficiency, are achieved here.
In the following, some embodiments of the invention will be described, by way of example, which provide further particular advantages. The subject matter of these embodiments can also be combined with one another in any desired manner in order to provide particularly advantageous embodiments for specific applications.
In a further embodiment, it is preferred that the flow-mechanical device is adapted to guide a portion of the mass flow from the overload introduction region to the heating group and/or to a region before the heating group. Surprisingly, it has been shown that in this way improved operation at lower partial loads can be achieved, while at the same time a higher efficiency can be achieved than in the case of tapping off a part of the mass flow before the overload introduction region. This position has therefore also proved to be particularly well-modifiable, since the overload introduction region is usually characterized by the gap between the blades in the blade arrangement region. Even if, for example, only relatively small blades are used in the overload induction region in order to be able to be better introduced in the event of overload operation, it is advantageous here to install an open flow guide for discharging a portion of the mass flow according to the invention.
In a further embodiment, it is preferred that the flow-mechanical device is adapted to discharge a portion of the mass flow from the region between the heating group and the turbine and to guide the portion of the mass flow to the heating group and/or to a region before the heating group. Although generally only lower efficiencies can be achieved in this way, this makes it particularly simple to retrofit corresponding fluid mechanical devices.
However, it is preferred, in particular for the exemplary embodiment of the invention, that the fluid mechanical device has an overload inlet line. Even if, for example, additionally or alternatively, a part of the mass flow is derived from the intermediate region between the heating groups or turbines, such an overload introduction line enables, for example, a subsequent rapid adaptation to future requirements or fine-tuning, wherein existing overload introduction lines can be used.
In a further embodiment, it is also preferred that the flow machine has an overload introduction line in the overload introduction region, wherein the flow machine is suitable for conducting a portion of the mass flow from the overload introduction region through the overload introduction line to the heating group and/or to a region upstream of the heating group. It is generally preferred that at least 60% by mass, more preferably at least 80% by mass, still more preferably at least 95% by mass of the part of the mass flow directed to the heating group and/or the zone before the heating group according to the invention is directed through the overload introduction line. In particular, in a further embodiment it is preferred that all of the mass flow which is conducted to the heating group and/or to the region upstream of the heating group is conducted through the overload introduction line. This surprisingly makes it possible to operate existing fluid-mechanical devices in the method according to the invention without major retrofitting work by using existing overload lead-in lines and only slightly adapting them. For example, only some additional valves, piping and control technology components need to be installed and/or replaced.
Whenever reference is made to mass percentage of mass flow in the context of the present invention, this refers to a portion of the mass flow that is directed to the zone before the heating group, unless otherwise specified. This part of the mass flow is drawn from the total mass of the mass flow directed from the heating group to the turbine. If there are a plurality of turbines to be connected to a heating group, the corresponding mass flow of each turbine is a proportional fraction of the mass flow obtained from the heating group for each turbine. If a plurality of heating groups are used to provide a mass flow for one turbine, the total mass naturally refers to the total mass flow of the heating groups. The further combinations are derived in a logical manner.
In a further embodiment, it is preferred that the flow machine has at least one preheater before the heating group, wherein a portion of the mass flow is introduced into the at least one preheater and/or between the at least one preheater and the heating group, preferably into the at least one preheater. Surprisingly, it has been shown that the feed lines to these locations can be modified in a particularly simple manner. For example, it may be particularly preferred that a part of the mass flow is directed to the same preheater into which also a mass flow originating from a component of the turbine located further downstream and/or a region after the turbine may be introduced. For example, it may additionally be provided that the mass flow can be directed to the preheater after the first 50%, more preferably after the first 70%, of the blade region. For example, the mass flow from the turbine can be used to heat the preheater after the turbine area under normal conditions. In contrast, in partial load operation, additionally or alternatively, the mass flow from the beginning region of the turbine is introduced into the same preheater. In this case, for typical use cases, existing components of the device can be used, as a result of which the system according to the invention can be provided quickly, inexpensively and reliably.
In a further embodiment, it is preferred that the flow machine arrangement has at least one preheater before the heating group, wherein a portion of the mass flow is at least partially, more preferably up to at least 50% by mass, still more preferably at least 80% by mass, and still more preferably all, conducted into the at least one preheater. The mass flow is preferably directed to the last preheater before the heating train. If the turbomachine has only one preheater before the heating group, it is the last preheater. This also simplifies the upgrading of existing fluid-mechanical plants, since the working operation on the respective preheater is less labour-intensive and crisis-safe. In addition, in this way, a particularly uniform flow of the mass flow can be achieved, which is surprisingly advantageous for further heating of the mass flow in the heating group.
According to another aspect, the invention relates to a fluid mechanical device controller as described above.
In a further embodiment, the predetermined limit value is a lower limit with respect to power. It is observed that a good regulation of the device is possible in particular, since this is a variable which is usually detected in fluid-mechanical devices and is easy to monitor. At the same time, other parameters, such as emissions, can thus be predicted with generally high enough accuracy.
In a further embodiment, it is preferred that the predetermined limit value is an upper limit of the emission. In particular, as already explained, optimization and improvement of the emission values can be achieved with the invention even in the case of lower power of the fluid mechanical device. In view of the ever increasing demands in terms of emissions, it has proven to be particularly advantageous to implement a direct coupling of the controller with the emissions measurement. In particular, the invention has proven to be advantageous with regard to monitoring and regulating NOx emissions. For example, the NOx limit value can be taken into account in this way.
According to another aspect, the invention relates to a method for operating a fluid mechanical device as described above.
In a further embodiment, it is preferred that in the first operating mode a portion of the mass flow is not introduced directly into the overload introduction region of the turbine. For example, the first operating mode is preferably an operating mode optimized for the respective fluid mechanical device, which operating mode is designed for the respective fluid mechanical device according to an optimum efficiency. This is generally the mode of operation with the highest efficiency.
In a further embodiment, it is preferred that the turbomachine has an overload inlet line and that the method has a third operating mode, wherein in the third operating mode a portion of the mass flow is conducted from the heating group via the overload inlet line into the turbine. It is generally preferred that the fluid mechanical device should be operated in a manner exceeding the optimum range with increasing load. This makes it possible, for example, to balance the increased energy demand in a short time.
In a further embodiment, it is preferred that a part of the mass flow is at least partially conducted from the overload introduction region to the heating group and/or to a region upstream of the heating group, preferably to a region upstream of the heating group. This generally enables a higher efficiency of the fluid mechanical device to be achieved even in the case of low partial loads.
In a further embodiment, it is preferred that the flow machine has an overload introduction line, wherein a portion of the mass flow is guided at least partially, preferably up to at least 50% by weight, more preferably up to at least 70% by mass, even more preferably up to at least 90% by mass, through the overload introduction line to the heating group and/or to a region before the heating group. In particular, it is generally preferred that a portion of the mass flow is guided completely through the overload introduction line.
In a further embodiment, it is preferred that the second operating mode is a partial load operation of the turbomachine. In particular, particularly good results are achieved here by means of the method according to the invention. In particular, in this case, in spite of the deterioration of the conditions, particularly good emission values are obtained, for example with regard to NOx emissions.
In a further embodiment, it is preferred that the partial load is in the range of 15% to 50%, more preferably in the range of 18% to 38%, still more preferably in the range of 20% to 33% of the optimum load of the fluid mechanical device. Surprisingly, even in these ranges, good emission values can be obtained by means of the process according to the invention. In the case of the above-described more preferred embodiments, the improvement of the optimized power and emission combination is particularly significant here.
In a further embodiment, it is preferred to provide a connection between the region after the heating group and before the end of the overload introduction region and the heating group and/or the region before the heating group, preferably between the region after the heating group and before the end of the overload introduction region and the region before the heating group, wherein the connection is adapted to guide a part of the reduced mass flow from the overload introduction region into the heating group and/or the region before the heating group in the event of partial load. Surprisingly, a particularly good efficiency of the fluid mechanical device is achieved in particular here.
In a further embodiment, it is preferred that the flow machine has at least one preheater in the region before the heating group, wherein a portion, preferably up to at least 50% by mass, even more preferably at least 80% by mass, and even more preferably completely, of the mass flow is conducted to the at least one preheater.
According to another aspect, the invention relates to a use as embodied above.
In a further embodiment, the invention relates to the use according to the invention, wherein the flow machine device has an overload introduction region and wherein the tapping of a part of the mass flow takes place from a region between the heating group and an end of the overload introduction region.
In a further embodiment, it is preferred that a portion of the mass flow is led out of the overload introduction region and wherein a portion of the mass flow is led through the overload introduction line to the region before the heating train. It is generally preferred that the flow mechanism has at least one preheater and that a part of the mass flow is directed at least partially, preferably up to at least 50% by mass, more preferably up to at least 70% by mass, still more preferably up to at least 90% by mass to the at least one preheater, preferably to the last preheater.
Fig. 1 shows a schematic representation of a fluid mechanical device according to a first variant of the invention, wherein the fluid mechanical device is not operated under partial load. The turbomachine is here a steam turbine plant. Here, the heating group is a steam generator.
The steam turbine plant has a turbine, an overload introduction zone as a constituent of the turbine, a heating group, an overload introduction line, a plurality of preheaters 5 in the zone upstream of the heating group 1, and a mass flow through the heating group 1 and the turbine 2. The mass flow is here introduced into the turbine 2 via a mass flow introduction line 7. The variant shown in fig. 1 also has a connection 6 between the turbine outlet and the preheater in order to be able to utilize the lower-quality mass flow obtained here for the preheater 5 even if, for example, it is not operating at partial load.
The steam turbine installation is also adapted to leading a portion of the mass flow out of the turbine 2 via an overload introduction line 3 in the overload introduction region. This part of the mass flow is led completely via the connection 4 between the overload introduction line 3 and the preheater 5 to the last preheater 5. This part of the mass flow is used here to increase the inlet temperature of the heating group, since the high-quality steam from the line region of the turbine 2 is fed into the preheater 5 and in this way also a higher-quality mass flow can be fed into the heating group 1. In this way, the operating conditions of the heating group can be optimized in order to improve the emission values, in particular, considerably in partial-load operation.
The control of the steam turbine system is effected by means of a steam turbine system which, at a predetermined limit value, directs a portion of the mass flow from the turbine 2 via the overload inlet line 3 to the last preheater 5. The load of the steam turbine plant is used here, for example, as a limit value. For example, if the load drops below 45% due to operation, a portion of the mass flow may be automatically directed to the preheater 5. In this case, the quantity of the tapped mass flow can be adapted to the respective load of the steam turbine plant on the basis of previous calculations or measured values. Further, alternatively and/or additionally, the adjustment is based on an emission value. Such emission values are preferably determined continuously during the operation of the steam turbine plant. Preferably, the emission values comprise NOx values. As soon as the corresponding emission value rises above a predetermined value in the event of a reduction in the load of the steam turbine system, the steam turbine system can automatically divert a portion of the mass flow in order to adapt the process conditions and reduce the emission value.
This allows the steam turbine plant to be operated with minimal adaptation in an operation optimized for part load. Likewise, in the context of, for example, maintenance, the corresponding refurbishment process is significantly simplified, since only such additional connections 4 and also a small number of components (for example additional valves and control components) have to be repaired or replaced between the overload inlet line 3 and the preheater 5.
The state shown in the figure is the third of the at least two operating modes, in which the mass flow is conducted from the heating group 1 via the mass flow inlet line 7 and the overload inlet line 3 of the turbine 2 into the turbine 2.
If the turbine 2 is to be operated in a first of the at least two operating modes (not shown in the figure), the valve of the overload introduction line 3 is closed, so that mass flow will be directed into the turbine 2 only via the mass flow introduction line 7 of the turbine 2.
Fig. 2 shows a schematic illustration of a steam turbine plant according to the variant of the invention shown in fig. 1, wherein the steam turbine plant is operated at partial load. This is the second mode of operation of the method according to the invention.
In contrast to the operating mode shown in fig. 1, a part of the mass flow is guided from the supply line region of the steam turbine plant via the overload inlet line 3 and the connection 4 between the overload inlet line 3 and the preheater 5 to the preheater 5. As already discussed with reference to fig. 1, the higher-quality steam from the overload introduction zone is used here to generate a high-quality mass flow in the last preheater 5, which mass flow is in turn fed into the heating group 1.
Thereby changing the operating conditions in the heating group 1 and, for example, significantly reducing emissions. Surprisingly, a very high efficiency can nevertheless be achieved, so that the highly flexible operation required for the steam turbine plant is still associated with a high degree of economy.
Fig. 3 shows a schematic representation of a steam turbine plant according to a second variant of the invention, wherein the steam turbine plant is operated at partial load.
In this second variant of the invention, a steam turbine plant construction similar to the first variant is provided. The steam turbine plant has a turbine 2 ', an overload introduction region as a component of the turbine 2 ', a heating group, a plurality of preheaters 5 ' in the region upstream of the heating group 1 ', and a mass flow through the heating group 1 ' and the turbine. Here, too, the mass flow is introduced into the turbine via a mass flow introduction line 7'. Similarly to the first variant, there is also a connection 6 'between the turbine outlet and the preheater 5'.
In contrast to the first variant, the steam turbine plant is suitable for removing a portion of the mass flow from the region between the heating group 1' and the turbine. This part of the mass flow is led entirely via the connection 8 ' interconnecting the heating group 1 ' with the intermediate zone of the turbine and the preheater 5 '. This part of the mass flow is used here to increase the inlet temperature of the heating group, since the high-quality steam from the delivery line region of the turbine is fed to the preheater 5 ', and with this the higher-quality mass flow can also be delivered to the heating group 1'.
Fig. 4 shows a schematic representation of a steam turbine plant according to a third variant of the invention, wherein the steam turbine plant is operated at partial load.
In a third variant of the invention, a steam turbine plant construction similar to the first variant is provided. The steam turbine plant has a turbine 2 ", an overload induction zone as a component of the turbine 2", a heating group 1 ", a plurality of preheaters in the region upstream of the heating group 1", and a mass flow through the heating group 1 "and the turbine 2". Here, too, the mass flow is introduced into the turbine via a mass flow introduction line 7 ". Similarly to the first variant, there is also a connection 6 "between the turbine outlet and the preheater 5".
Similar to the first variant, the steam turbine installation is suitable for tapping a portion of the mass flow from the turbine 2 ″. However, this part of the mass flow is not drawn off via the overload inlet line 3 ", but via an additional draw-off point which is after approximately 30% of the blade area. The part or all of the tapped-off mass flow is guided through a connection 9 "which interconnects the overload lead-in region of the turbine 2" with the preheater. Here, this part of the mass flow is used to increase the inlet temperature in the heating group 1 ", since the high-quality steam from the delivery line region of the turbine 2" is fed into the preheater and thus a higher-quality mass flow can be delivered to the heating group 1 ".
For the purpose of explanation, the present invention has been described in more detail based on exemplary embodiments. However, the present invention is not intended to be limited to the specific configurations of these exemplary embodiments. Rather, the scope of the invention is limited only by the attached claims.
Claims (15)
1. A fluid mechanical device comprising: a turbine (2, 2 ', 2 "), a blade region as a constituent of the turbine (2, 2', 2"), a starting region of the blade region, a heating group (1, 1 ', 1 "), a region preceding the heating group (1, 1', 1") and a mass flow through the heating group (1, 1 ', 1 ") and the turbine (2, 2', 2"),
wherein the fluid mechanical device is adapted to lead out a part of the mass flow after the heating group (1, 1 ', 1 ") and before the end of the start region of the blade region and to the heating group (1, 1 ', 1") and/or to the region before the heating group (1, 1 ', 1 "),
wherein the starting region of the vane region extends over the first 44% of the vane region, with reference to the direction of flow of the mass flow and the spacing between the start of the starting vane row and the end of the last vane row.
2. The hydromechanical apparatus according to claim 1, wherein said hydromechanical apparatus is a steam turbine apparatus.
3. The flow machine device according to one of claims 1 to 2, wherein the flow machine device has an overload introduction area,
wherein the fluid mechanical device is adapted to direct a portion of the mass flow from the overload introduction region to the heating group (1, 1 ', 1 ") and/or to the region before the heating group (1, 1', 1").
4. The hydromechanical device according to any of claims 1 to 3, wherein the hydromechanical device is adapted to direct a portion of the mass flow out of a region between the heating group (1, 1 ', 1 ") and the turbine (2, 2', 2") and to the heating group (1, 1 ', 1 ") and/or to the region before the heating group (1, 1', 1").
5. The hydromechanical device according to any of claims 1 to 4, wherein the hydromechanical device has one overload lead-in line (3, 3') in the overload lead-in area,
wherein the fluid mechanical device is adapted to conduct a portion of the mass flow from the overload introduction zone through the overload introduction line (3, 3 ') to the heating group (1, 1 ') and/or to the zone preceding the heating group (1, 1 ').
6. The hydromechanical device according to any of claims 1 to 5, wherein the hydromechanical device has at least one preheater (5, 5 ', 5 ") before the heating group (1, 1', 1"),
wherein the portion of the mass flow is at least partially directed into the at least one preheater (5, 5').
7. A fluid machine arrangement controller for controlling a fluid machine arrangement according to any one of claims 1-6, wherein the fluid machine arrangement controller is adapted to divert a portion of a mass flow from a region between a heating group (1, 1 ', 1 ") and an end of the starting region of the blade region of the turbine (2, 2', 2") to the heating group (1, 1 ', 1 ") and/or the region preceding the heating group (1, 1', 1") in case of a predetermined boundary value.
8. The fluid mechanical device controller of claim 7, wherein the predetermined boundary value is an upper limit of emissions.
9. A method for providing a part-load optimized operation of a fluid mechanical device,
wherein the turbomachine has a turbine (2, 2 ', 2 "), a blade region as a constituent of the turbine (2, 2 ', 2"), a starting region of the turbine (2, 2 ', 2 "), a heating group (1, 1 ', 1"), a region preceding the heating group (1, 1 ', 1 "), and a mass flow through the heating group (1, 1 ', 1") and the turbine (2, 2 ', 2 "),
wherein a connection (4, 8 ', 9') between a region after the heating group (1, 1 ') and before an end of the starting region of the turbine (2, 2') and the region before the heating group (1, 1 ') and/or the heating group (1, 1') is provided or reworked,
wherein the connection (4, 8 ', 9') is adapted to leading out a part of the mass flow in the region after the heating group (1, 1 ') and before the end of the start region of the blade region of the turbine (2, 2') and into the heating group (1, 1 ') and/or into the region before the heating group (1, 1') in the case of partial load,
wherein the starting region of the vane region extends over the first 44% of the vane region with reference to the flow direction of the mass flow and the spacing between the start of the starting vane row and the end of the last vane row,
in which at least two modes of operation are provided,
wherein in a first operating mode the mass flow is conducted from the heating group (1, 1 ') completely through the starting region, preferably through the turbine (2, 2'),
wherein in a second operating mode a portion of the mass flow is conducted from the region after the heating group (1, 1 ', 1 ") and before the end of the starting region of the turbine (2, 2', 2") to the heating group (1, 1 ', 1 ") and/or to the region before the heating group (1, 1', 1").
10. The method according to claim 9, wherein the fluid mechanical device has an overload intake line (3, 3'), wherein the method has a third operating mode,
wherein in the third operating mode a portion of the mass flow is conducted from the heating group (1, 1 ', 1 ") via the overload introduction line (3, 3 ') into the turbine (2, 2 ', 2").
11. Method according to any of claims 9 to 10, wherein the fluid mechanical device has one overload introduction line (3, 3 ') and one overload introduction area, wherein the part of the mass flow is at least partially directed from the overload introduction area to the heating groups (1, 1 ', 1 ") and/or to the area between the heating groups (1, 1 ', 1").
12. Method according to any of claims 9 to 11, wherein the fluid mechanical device has one overload lead-in line (3, 3'),
wherein the portion of the mass flow is at least partially guided through the overload introduction line (3, 3 ') to the heating groups (1, 1 ') and/or to the region between the heating groups (1, 1 ').
13. Method according to any of claims 9 to 12, wherein the second mode of operation is part load operation of the fluid mechanical device.
14. The method according to any of claims 9 to 13, wherein the part load operation is in the range of 15% to 50% of the optimum load of the fluid mechanical device.
15. Use of a portion of the mass flow after a heating group (1, 1 ', 1 ") of a fluid mechanical device according to any of claims 1 to 6 for increasing the inlet temperature in the heating group (1, 1 ', 1"), wherein the portion of the mass flow is drawn from a region between the heating group (1, 1 ', 1 ") and an end of the starting region of the blade region of the turbine.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102018216566 | 2018-09-27 | ||
| DE102018216566.1 | 2018-09-27 | ||
| PCT/EP2019/074814 WO2020064419A1 (en) | 2018-09-27 | 2019-09-17 | Turbomachine system and method for operating a turbomachine system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN112805454A true CN112805454A (en) | 2021-05-14 |
Family
ID=68072329
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201980063798.5A Pending CN112805454A (en) | 2018-09-27 | 2019-09-17 | Fluid mechanical device and method for operating a fluid mechanical device |
Country Status (3)
| Country | Link |
|---|---|
| EP (1) | EP3810906A1 (en) |
| CN (1) | CN112805454A (en) |
| WO (1) | WO2020064419A1 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113638779B (en) * | 2021-07-05 | 2024-03-12 | 西安热工研究院有限公司 | Direct air cooling unit additionally provided with combined cycle peak regulation and frequency modulation and operation method thereof |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1035728A (en) * | 1963-12-03 | 1966-07-13 | Simmering Graz Pauker Ag | Condensing steam turbine plant comprising a controlled secondary circuit |
| GB1214758A (en) * | 1968-08-28 | 1970-12-02 | Sulzer Ag | Supercharged steam generators |
| CN103649474A (en) * | 2011-07-14 | 2014-03-19 | 西门子公司 | Steam turbine installation and method for operating the steam turbine installation |
| CN203756252U (en) * | 2014-03-20 | 2014-08-06 | 王振宇 | Turbine regenerative system of ultra supercritical unit |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4164848A (en) * | 1976-12-21 | 1979-08-21 | Paul Viktor Gilli | Method and apparatus for peak-load coverage and stop-gap reserve in steam power plants |
| DE102011078193A1 (en) * | 2011-06-28 | 2013-01-03 | Siemens Aktiengesellschaft | Additional control tap for a preheater to improve the system dynamics and frequency control in a steam power plant |
-
2019
- 2019-09-17 CN CN201980063798.5A patent/CN112805454A/en active Pending
- 2019-09-17 WO PCT/EP2019/074814 patent/WO2020064419A1/en unknown
- 2019-09-17 EP EP19778865.6A patent/EP3810906A1/en not_active Withdrawn
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1035728A (en) * | 1963-12-03 | 1966-07-13 | Simmering Graz Pauker Ag | Condensing steam turbine plant comprising a controlled secondary circuit |
| GB1214758A (en) * | 1968-08-28 | 1970-12-02 | Sulzer Ag | Supercharged steam generators |
| CN103649474A (en) * | 2011-07-14 | 2014-03-19 | 西门子公司 | Steam turbine installation and method for operating the steam turbine installation |
| CN203756252U (en) * | 2014-03-20 | 2014-08-06 | 王振宇 | Turbine regenerative system of ultra supercritical unit |
Also Published As
| Publication number | Publication date |
|---|---|
| EP3810906A1 (en) | 2021-04-28 |
| WO2020064419A1 (en) | 2020-04-02 |
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