CN116383995B - Basic design method of multi-rotating-speed turbine based on different shafts of compressed air energy storage power station - Google Patents
Basic design method of multi-rotating-speed turbine based on different shafts of compressed air energy storage power station Download PDFInfo
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Abstract
The invention discloses a foundation design method of a multi-rotating-speed turbine based on a different shaft of a compressed air energy storage power station, relates to the field of foundation design of power equipment, can effectively realize stable calculation of the multi-rotating-speed power equipment based on the different shaft, greatly improves design efficiency, fully utilizes existing mature general finite element software, adopts a vibration response coupling effect calculation theory, obtains actual amplitude of the foundation of the multi-rotating-speed turbine based on the different shaft by self data post-processing, has strong applicability to calculation of the power foundation of the multi-rotating-speed turbine based on the different shaft of the compressed air energy storage power station, and is suitable for popularization in actual engineering.
Description
Technical Field
The invention relates to the field of basic design of power equipment, in particular to a basic design method of a multi-rotating-speed turbine based on a different shaft of a compressed air energy storage power station.
Background
The compressed air energy storage CAES (Compressed Air Energy Storage) is a technology for storing energy and generating power by using compressed air as a medium, can solve the intermittent problem of renewable energy sources, and plays a role in regulating peaks and valleys of a power grid. Considering that the electrochemical energy storage facilities still do not form a recognized safety solution, the engineering project has potential safety hazards such as fire and explosion, and compared with the compressed air energy storage, the method has the advantages of large energy storage scale, long discharge time, long service life, higher safety and wide comprehensive utilization range of heat, cold and electricity. Therefore, there is a need to continue to enhance the technical development and application of compressed air energy storage.
Most of turbines used in conventional large and medium-sized thermal power projects at present are coaxial, namely, a generator, a high-pressure cylinder, a medium-pressure cylinder and a low-pressure cylinder bearing are all coaxially arranged, so that the rotating speeds of all parts are synchronous and coordinated, the MFSAP (functional block application program) of a power equipment foundation is adopted for direct modeling analysis, and a corresponding basic stable calculation method is mature and reliable; however, for the new model of the multi-axis multi-rotation speed turbine adopted in the compressed air energy storage power station, namely the different axis arrangement of the partial bearings of the generator, the high pressure cylinder, the medium pressure cylinder and the low pressure cylinder, the gear connection is adopted, if the MFSAP is still adopted for modeling calculation, the limitation exists, on one hand, the MFSAP software can only realize the model of the coaxial or biaxial different axis turbine, and on the other hand, the power calculation can not be realized for the model of the multi-axis different axis turbine; on the other hand, the post-treatment results of MFSAP on biaxial off-axis turbine models are not simple and intuitive enough to display.
Disclosure of Invention
The technical problem to be solved by the invention is to provide a basic design method of the multi-rotation speed turbine based on the different shaft of the compressed air energy storage power station, which is suitable for basic calculation of all the multi-rotation speed turbines with different shafts, can effectively realize stable calculation of power equipment with different shafts and multiple rotation speeds, and greatly improves the design efficiency.
In order to solve the technical problems, the invention adopts the following technical scheme: a basic design method of a multi-rotating-speed turbine based on a different shaft of a compressed air energy storage power station comprises the following steps:
s1, presetting the section sizes of beams and columns of a turbine foundation by combining the external size requirement of the turbine, and establishing a calculation model by adopting Sap2000 software; when the generator, the low-pressure cylinder, the middle-pressure cylinder shaft and the high-pressure cylinder part of the turbine are in different shaft bearing, the different shaft bearing has different rated rotation speeds, and at least one disturbing force point is set on the generator, the low-pressure cylinder, the middle-pressure cylinder and the high-pressure cylinder respectively;
s2, under the working condition of rated rotation speed of the generator bearing, applying disturbance force values of the generator bearing at rated rotation speed to each disturbance force point of the generator, so as to obtain disturbance force values and amplitudes of each disturbance force point of the generator, the low-pressure cylinder, the medium-pressure cylinder and the high-pressure cylinder at any rotation speed of the generator bearing;
s3, under the working condition of the rated rotation speed of the low-pressure cylinder bearing, applying disturbance force values of the low-pressure cylinder bearing at the rated rotation speed of the low-pressure cylinder bearing to each disturbance force point of the low-pressure cylinder correspondingly, so as to obtain disturbance force values and amplitudes of each disturbance force point of the generator, the low-pressure cylinder, the medium-pressure cylinder and the high-pressure cylinder at any rotation speed of the low-pressure cylinder bearing;
s4, under the working condition of rated rotation speed of the medium pressure cylinder bearing, applying disturbance force values of the medium pressure cylinder bearing at rated rotation speed to each disturbance force point of the medium pressure cylinder correspondingly, so as to obtain disturbance force values and amplitudes of each disturbance force point of the generator, the low pressure cylinder, the medium pressure cylinder and the high pressure cylinder at any rotation speed of the medium pressure cylinder bearing;
s5, under the working condition of the rated rotation speed of the high-pressure cylinder bearing, applying disturbance force values of the high-pressure cylinder bearing at the rated rotation speed of the high-pressure cylinder bearing to each disturbance force point of the high-pressure cylinder correspondingly, so as to obtain disturbance force values and amplitudes of the generator, the low-pressure cylinder, the medium-pressure cylinder and each disturbance force point of the high-pressure cylinder at any rotation speed of the high-pressure cylinder bearing;
step S6, coupling the calculation result data of the steps S2 to S5 through post-processing, so as to obtain the actual amplitude of each disturbing force point of the generator, the low-pressure cylinder, the medium-pressure cylinder and the high-pressure cylinder at any rotating speed;
and S7, comparing and checking the actual amplitude of each disturbance force point of the generator, the low-pressure cylinder, the medium-pressure cylinder and the high-pressure cylinder with a maximum amplitude allowable value, if the actual amplitude of a certain disturbance force point is not satisfied, increasing the cross section size of the beam and the column of the Sap2000 model in the step S1, wherein each time of increasing is 100 mm-200 mm, and repeating the steps S2-S6 until the calculation result satisfies the requirement.
The technical scheme of the invention is further improved as follows: in the step S1, the disturbing forces of the generator, the low-pressure cylinder, the medium-pressure cylinder and the high-pressure cylinder are all distributed along the circumference of each component.
The technical scheme of the invention is further improved as follows: the calculation formulas of the disturbance force values of the generator, the low-pressure cylinder, the medium-pressure cylinder and the high-pressure cylinder at any rotation speeds of the disturbance force point bearings in the steps S2 to S5 are as follows:
wherein P is 0i The disturbance force of any rotating speed for the ith disturbance force point, P gi For the disturbance force at the rated rotation speed of the ith disturbance force point, n 0 And n is the working rotation speed.
The technical scheme of the invention is further improved as follows: the actual amplitudes of the disturbance force points on the generator, the low-pressure cylinder, the medium-pressure cylinder and the high-pressure cylinder in the step S6 under the combined action of the disturbance forces in the corresponding steps S2 to S5 at any rotating speed are as follows:
wherein: a is that j ik The amplitude generated by the kth disturbance force on the ith disturbance force point under the working condition of the rotating speed j; a is that j i The amplitude generated by the ith disturbance force point under the working condition of the rotating speed j.
The technical scheme of the invention is further improved as follows: in the step S7, the process of comparing and checking the actual amplitude and the maximum allowable amplitude of each disturbing force point on the generator, the low-pressure cylinder, the medium-pressure cylinder and the high-pressure cylinder is as follows:
when 0.75 omega 0 ≤ω j ≤1.25ω 0 In the time-course of which the first and second contact surfaces,
amplitude checking: a is that j i ≤[A]
When omega i ＜0.75ω 0 In the time-course of which the first and second contact surfaces,
amplitude checking: a is that j i ≤1.5*[A]
[A]Is 0.02mm, omega with maximum amplitude j The rotation speed r/min omega of each bearing of the generator, the low-pressure cylinder, the medium-pressure cylinder and the high-pressure cylinder is arbitrary 0 The rated rotation speed r/min of each bearing of the generator, the low-pressure cylinder, the medium-pressure cylinder and the high-pressure cylinder is set.
By adopting the technical scheme, the invention has the following technical progress:
the calculation method provided by the invention can effectively realize stable calculation of the multi-rotating-speed power equipment with different shafts, greatly improves the design efficiency, fully utilizes the existing mature general finite element software, adopts the vibration response coupling effect calculation theory, obtains the actual amplitude of the multi-rotating-speed turbine foundation with different shafts by self-processing data, has stronger applicability to calculation of the power foundation of the multi-rotating-speed turbine with different shafts based on the compressed air energy storage power station, and is suitable for popularization in actual engineering.
Drawings
FIG. 1 is a graph of turbine geometry and disturbance point distribution according to example 1 of the present invention;
FIG. 2 is a disturbance force distribution diagram of the generator, the low pressure cylinder and the medium pressure cylinder bearing 3000r/min working condition according to the embodiment 1 of the invention;
FIG. 3 is a disturbance force distribution diagram of the high pressure cylinder bearing 9200r/min in the working condition of the embodiment 1 of the present invention.
Detailed Description
The invention is further illustrated by the following examples:
a basic design method of a multi-rotating-speed turbine based on a different shaft of a compressed air energy storage power station comprises the following steps:
step S1, the turbine comprises a generator, a low-pressure cylinder, a medium-pressure cylinder and a high-pressure cylinder, and the beam and column section sizes of a turbine foundation are preset in combination with the requirements of the external dimensions of the turbine, while the larger the beam and column section sizes are, the larger the rigidity is, and the smaller the corresponding calculated amplitude is, the larger the beam and column section sizes are, the larger the concrete amount used is, the higher the engineering cost is, so that the beam and column section sizes of the smaller turbine foundation are initially set, and the beam and column section sizes are gradually increased after the calculation is not satisfied.
When the generator, the low-pressure cylinder, the medium-pressure cylinder and the high-pressure cylinder of the turbine are partially provided with different bearing shafts, the different bearing shafts have different rated rotation speeds, at least one disturbing force point is respectively set on the generator, the low-pressure cylinder, the medium-pressure cylinder and the high-pressure cylinder, and the disturbing forces of the generator, the low-pressure cylinder, the medium-pressure cylinder and the high-pressure cylinder are all arranged along the circumference of each part;
s2, under the working condition of rated rotation speed of the generator bearing, applying disturbance force values of the generator bearing at rated rotation speed to each disturbance force point of the generator, so as to obtain disturbance force values and amplitudes of each disturbance force point of the generator, the low-pressure cylinder, the medium-pressure cylinder and the high-pressure cylinder at any rotation speed of the generator bearing;
s3, under the working condition of the rated rotation speed of the low-pressure cylinder bearing, applying disturbance force values of the low-pressure cylinder bearing at the rated rotation speed of the low-pressure cylinder bearing to each disturbance force point of the low-pressure cylinder correspondingly, so as to obtain disturbance force values and amplitudes of each disturbance force point of the generator, the low-pressure cylinder, the medium-pressure cylinder and the high-pressure cylinder at any rotation speed of the low-pressure cylinder bearing;
s4, under the working condition of rated rotation speed of the medium pressure cylinder bearing, applying disturbance force values of the medium pressure cylinder bearing at rated rotation speed to each disturbance force point of the medium pressure cylinder correspondingly, so as to obtain disturbance force values and amplitudes of each disturbance force point of the generator, the low pressure cylinder, the medium pressure cylinder and the high pressure cylinder at any rotation speed of the medium pressure cylinder bearing;
s5, under the working condition of the rated rotation speed of the high-pressure cylinder bearing, applying disturbance force values of the high-pressure cylinder bearing at the rated rotation speed of the high-pressure cylinder bearing to each disturbance force point of the high-pressure cylinder correspondingly, so as to obtain disturbance force values and amplitudes of the generator, the low-pressure cylinder, the medium-pressure cylinder and each disturbance force point of the high-pressure cylinder at any rotation speed of the high-pressure cylinder bearing;
in the steps S2 to S5, the calculation formulas of the disturbance force values of the bearings of the disturbance force points of the generator, the low-pressure cylinder, the medium-pressure cylinder and the high-pressure cylinder at any rotating speed are as follows:
wherein P is 0i For the ith disturbance forcePoint disturbance force at arbitrary rotational speed, P gi For the disturbance force at the rated rotation speed of the ith disturbance force point, n 0 And n is the working rotation speed.
And S6, coupling the calculated result data of the steps S2 to S5 through post-processing, so as to obtain the actual amplitude of each disturbing force point of the generator, the low-pressure cylinder, the medium-pressure cylinder and the high-pressure cylinder at any rotating speed, wherein the formula is as follows:
wherein: a is that j ik The amplitude generated by the kth disturbance force on the ith disturbance force point under the working condition of the rotating speed j; a is that j i The amplitude generated by the ith disturbance force point under the working condition of the rotating speed j.
S7, comparing the actual amplitude of each disturbing force point of the generator, the low-pressure cylinder, the medium-pressure cylinder and the high-pressure cylinder with a maximum amplitude allowable value, and checking to calculate:
when 0.75 omega 0 ≤ω j ≤1.25ω 0 In the time-course of which the first and second contact surfaces,
amplitude checking: a is that j i ≤[A]
When omega i ＜0.75ω 0 In the time-course of which the first and second contact surfaces,
amplitude checking: a is that j i ≤1.5*[A]
[A]Is 0.02mm, omega with maximum amplitude j The rotation speed r/min omega of each bearing of the generator, the low-pressure cylinder, the medium-pressure cylinder and the high-pressure cylinder is arbitrary 0 The rated rotation speed r/min of each bearing of the generator, the low-pressure cylinder, the medium-pressure cylinder and the high-pressure cylinder is set.
If the actual amplitude of a certain disturbance force point is not satisfied, the cross section size of the beam and the column of the Sap2000 model in the step S1 is required to be increased, the increase is 100 mm-200 mm each time, and the steps S2-S6 are repeated until the calculation result satisfies the requirement.
Example 1
Taking a certain compressed air energy storage project as an example, the generator of the turbine is coaxial with the middle-low pressure cylinder bearing and is in different shaft with the high pressure cylinder bearing, and the generator and the middle-low pressure cylinder bearing are connected through an intermediate gear to realize cooperative work, wherein the rated rotation speed of the high pressure cylinder bearing is 9200r/min, and the rated rotation speeds of the generator, the low pressure cylinder and the middle pressure cylinder bearing are 3000r/min.
And modeling by adopting Sap2000 software in basic power calculation, calculating the amplitude of each disturbance force point under the action of different rotating speeds, and coupling the vibration responses of different rotating speeds to obtain the actual integral vibration response of the turbine foundation. The specific operation steps are as follows:
1) Establishing a calculation model by using Sap2000 software, wherein the preset cross section sizes of beams and columns of a turbine foundation and each disturbing force point (A1-A6) are shown in FIG. 1; the vertical column member sizes are 400x400mm and 500x500mm, the horizontal beam member sizes 535mmx1220mm, 835mmx1220mm, 675mmx1220mm and the like are preset according to the equipment appearance, A1 and A2 are power generator disturbing points, A3 and A4 are medium-low pressure cylinder disturbing points, and A5 and A6 are high pressure cylinder disturbing points.
2) Under the working condition of the rated rotating speed of 3000r/min, as shown in figure 2, the disturbing force P under the rated rotating speed is correspondingly applied to the positions of the disturbing force points A1, A2, A3 and A4 of the generator and the middle and low pressure cylinders g1 、P g2 、P g3 、P g4 ，P g1 ＝4.901kN，P g2 ＝4.901kN，P g3 ＝14.686kN，P g4 ＝14.686kN，
According to the following formula, calculating the disturbance force value P of the generator and the middle-low pressure cylinder bearing within the range of 0 r/min-3750 r/min 01 ～P 04 ：
Disturbance force value P of generator, middle-low pressure cylinder under different rotation speeds 0i (N)
The disturbance force P corresponding to the disturbance force points A1 to A6 of the generator, the low-pressure cylinder, the medium-pressure cylinder and the high-pressure cylinder respectively at 0r/min to 3750r/min of the bearing of the generator, the medium-pressure cylinder and the low-pressure cylinder is obtained through calculation by Sap2000 software 01 ～P 04 Amplitude A under action ik 。
Amplitude value A of each point of generator, middle and low pressure cylinder under different rotating speeds i (um)
3) Under the working condition of rated rotation speed 9200r/min, as shown in figure 3, the disturbing force P under the rated rotation speed is correspondingly applied to the positions of the disturbing force points A5 and A6 of the high-pressure cylinder bearing g5 、P g6 ，P g5 ＝1.216kN，P g6 =1.216 kN, and according to the following formula, calculating the disturbance force value P of bearing rotating speed of high-pressure cylinder within the range of 0 r/min-11500 r/min 05 ～P 06 ：
Disturbing force value P of high-pressure cylinder at different rotating speeds 0i (N)
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The disturbance force P corresponding to each disturbance force point A1-A6 of the generator, the low-pressure cylinder, the medium-pressure cylinder and the high-pressure cylinder at 0 r/min-11500 r/min of the high-pressure cylinder bearing is obtained through calculation by Sap2000 software 05 ～P 06 Amplitude A under action ik 。
Amplitude value A of each point of high-pressure cylinder at different rotating speeds i (um)
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4) The disturbance force points A1 to A6 are calculated according to the following formula, and the disturbance force P corresponding to 0r/min to 3750r/min (0 r/min to 11500 r/min) of the bearing of the middle-low pressure cylinder of the generator is calculated 01 ～P 06 Final actual amplitude A under coaction i The calculation formula is as follows:
actual amplitude value A of each point at different rotation speeds i (um)
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5) The actual amplitude of each disturbing force point is compared and checked by combining with the requirements of the specifications of the technical regulations of civil engineering structures of thermal power plants, DL 5022-2012, the allowable vibration standard of constructional engineering, GB50868-2013 and the specifications of the mechanical vibration of measuring and evaluating machines on non-rotating parts, GB/T6075.3-2001:
the rotating speed of the generator, the middle and low pressure cylinders is 0r/min<ω j <2250r/min (corresponding to a high pressure cylinder rotation speed of 0 r/min)<ω j <6900 r/min) of the total weight of the product,
A 1max ＝8.6um<1.5*0.02*1000＝30um
A 2max ＝8.6um<1.5*0.02*1000＝30um
A 3max ＝5.1um<1.5*0.02*1000＝30um
A 4max ＝6.7um<1.5*0.02*1000＝30um
A 5max ＝1.3um<1.5*0.02*1000＝30um
A 6max ＝0.82um<1.5*0.02*1000＝30um
the rotating speed of the generator, the middle-low pressure cylinder is 2250r/min less than or equal to omega j 3750r/min (corresponding to the rotation speed of 6900r/min omega) j Not more than 11500 r/min),
A 1max ＝4.9um<0.02*1000＝20um
A 2max ＝4.9um<0.02*1000＝20um
A 3max ＝11.5um<0.02*1000＝20um
A 4max ＝11.4um<0.02*1000＝20um
A 5max ＝4.7um<0.02*1000＝20um
A 6max ＝6.1um<0.02*1000＝20um
from the above, it can be seen that the vibration of each point of the turbine foundation of a certain compressed air energy storage power station meets the standard requirement.
Claims (4)
1. The basic design method of the multi-rotating-speed turbine based on the different shafts of the compressed air energy storage power station is characterized by comprising the following steps of: the method comprises the following steps:
s1, presetting the cross section sizes of a beam and a column of the turbine by combining the external dimension requirements of the turbine, and establishing a calculation model by adopting Sap2000 software; when the bearing of one part or two parts of the four parts of the generator, the low-pressure cylinder, the medium-pressure cylinder and the high-pressure cylinder of the turbine is different from the bearing of the other part, the rated rotation speed of the different-shaft bearing is different, and at least one disturbing force point is set on the generator, the low-pressure cylinder, the medium-pressure cylinder and the high-pressure cylinder respectively;
s2, under the working condition of rated rotation speed of the generator bearing, applying disturbance force values of the generator bearing at rated rotation speed to each disturbance force point of the generator, so as to obtain disturbance force values and amplitudes of each disturbance force point of the generator, the low-pressure cylinder, the medium-pressure cylinder and the high-pressure cylinder at any rotation speed of the generator bearing;
s3, under the working condition of the rated rotation speed of the low-pressure cylinder bearing, applying disturbance force values of the low-pressure cylinder bearing at the rated rotation speed of the low-pressure cylinder bearing to each disturbance force point of the low-pressure cylinder correspondingly, so as to obtain disturbance force values and amplitudes of each disturbance force point of the generator, the low-pressure cylinder, the medium-pressure cylinder and the high-pressure cylinder at any rotation speed of the low-pressure cylinder bearing;
s4, under the working condition of rated rotation speed of the medium pressure cylinder bearing, applying disturbance force values of the medium pressure cylinder bearing at rated rotation speed to each disturbance force point of the medium pressure cylinder correspondingly, so as to obtain disturbance force values and amplitudes of each disturbance force point of the generator, the low pressure cylinder, the medium pressure cylinder and the high pressure cylinder at any rotation speed of the medium pressure cylinder bearing;
s5, under the working condition of the rated rotation speed of the high-pressure cylinder bearing, applying disturbance force values of the high-pressure cylinder bearing at the rated rotation speed of the high-pressure cylinder bearing to each disturbance force point of the high-pressure cylinder correspondingly, so as to obtain disturbance force values and amplitudes of the generator, the low-pressure cylinder, the medium-pressure cylinder and each disturbance force point of the high-pressure cylinder at any rotation speed of the high-pressure cylinder bearing;
in the steps S2 to S5, the calculation formulas of the disturbance force values of the disturbance force points of the generator, the low-pressure cylinder, the medium-pressure cylinder and the high-pressure cylinder at any rotating speed of the bearing are as follows:
wherein P is 0i The disturbance force of any rotating speed for the ith disturbance force point, P gi For the disturbance force at the rated rotation speed of the ith disturbance force point, n 0 The rotation speed is arbitrary, and n is the working rotation speed;
step S6, coupling the calculation result data of the steps S2 to S5 through post-processing, so as to obtain the actual amplitude of each disturbing force point of the generator, the low-pressure cylinder, the medium-pressure cylinder and the high-pressure cylinder at any rotating speed;
and S7, comparing and checking the actual amplitude of each disturbance force point of the generator, the low-pressure cylinder, the medium-pressure cylinder and the high-pressure cylinder with a maximum amplitude allowable value, if the actual amplitude of a certain disturbance force point is not satisfied, increasing the cross section size of the beam and the column of the Sap2000 model in the step S1, wherein each time of increasing is 100 mm-200 mm, and repeating the steps S2-S6 until the calculation result satisfies the requirement.
2. The basic design method of the multi-rotating-speed turbine based on the different shafts of the compressed air energy storage power station is characterized by comprising the following steps of: in the step S1, each disturbing force point of the generator, the low pressure cylinder, the medium pressure cylinder and the high pressure cylinder is arranged along the circumference of each component.
3. The basic design method of the multi-rotating-speed turbine based on the different shafts of the compressed air energy storage power station is characterized by comprising the following steps of: in the step S6, the actual amplitudes of the disturbance force points on the generator, the low-pressure cylinder, the medium-pressure cylinder and the high-pressure cylinder under the combined action of the disturbance forces in the corresponding steps S2 to S5 at any rotating speed are as follows:
wherein: a is that j ik The amplitude generated by the kth disturbance force on the ith disturbance force point under the working condition of the rotating speed j; a is that j i To be under the working condition of the rotating speed jAmplitude of the disturbance force point.
4. The basic design method of the multi-rotating-speed turbine based on the different shafts of the compressed air energy storage power station, which is characterized in that: in step S7, the process of comparing and checking the actual amplitude and the maximum allowable amplitude of each disturbing force point on the generator, the low pressure cylinder, the medium pressure cylinder and the high pressure cylinder is as follows:
when 0.75 omega 0 ≤ω j ≤1.25ω 0 In the time-course of which the first and second contact surfaces,
amplitude checking: a is that j i ≤[A]
When omega j ＜0.75ω 0 In the time-course of which the first and second contact surfaces,
amplitude checking: a is that j i ≤1.5*[A]
[A]Is 0.02mm, omega with maximum amplitude j The rotation speed r/min omega of each bearing of the generator, the low-pressure cylinder, the medium-pressure cylinder and the high-pressure cylinder is arbitrary 0 The rated rotation speed r/min of each bearing of the generator, the low-pressure cylinder, the medium-pressure cylinder and the high-pressure cylinder is set.
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