CN110046441A - Rotating machinery shafting fatigue strength detection method - Google Patents
Rotating machinery shafting fatigue strength detection method Download PDFInfo
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- CN110046441A CN110046441A CN201910325019.6A CN201910325019A CN110046441A CN 110046441 A CN110046441 A CN 110046441A CN 201910325019 A CN201910325019 A CN 201910325019A CN 110046441 A CN110046441 A CN 110046441A
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Abstract
The invention discloses a kind of rotating machinery shafting fatigue strength detection methods, comprising the following steps: S1: establishing the lumped mass model for torsional vibration of target shafting, obtains the equation of motion of the target shafting under dynamic force moment T effect；S2: establishing modal matrix φ and regularization factors α is calculated, and then acquires normal mode matrix φn；S3: the equation of motion is changed into normal mode equation；S4: the response and torque distribution of all shaft parts of target shafting are found out；S5: the detection of target shafting fatigue strength is carried out.The present invention only needs one measuring point of arrangement, and the torque distribution of entire shafting can be calculated, and keeps on-the-spot test process simpler efficiently, improves the efficiency of test.Any shaft part in shafting may be selected in point position in the present invention, has very strong application power in specific engineering practice, is conducive to the situation for adapting to engineering site complexity.
Description
Technical field
The present invention relates to rotating machinery shaftings, more particularly to a kind of rotating machinery shafting fatigue strength detection method.
Background technique
In thermal power plant, blower and water pump etc. are main current consuming apparatus, contain huge energy-saving potential.In recent years
Come, the continuous propulsion of the fast development of power grid and energy conservation and environmental protection work, the safety and cost of electricity-generating of power plant's operation are proposed
Increasingly higher demands, power plant must adjust subsidiary engine operational mode to adapt to the demand of power generation.Therefore, many power plants
It undergoes technological transformation using converter technique to equipment such as blower, pumps, and achieves good effect.
After many equipment implement Frequency Conversion Modifications, blade Multiple site crack is frequently occurred, that shafting twists off, shaft coupling damage etc. is former
Barrier.Caused by such failure is the twisting vibration by shafting, and there is very strong latency and concealment, there are following 2
Typical feature: (1) failure initial stage is difficult to find；(2) failure once enters middle and advanced stage, frequently can lead to big axis and leaf destruction etc.
The generation of serious accident, fault harm and caused loss are larger.
The twisting vibration failure of Frequency Conversion Modification equipment can be inhibited in terms of electrically and mechanically two, electrical aspect packet
Include setting harmonic filter, change carrier frequency etc., mechanical aspects can carry out the replacement of shaft coupling.But whether using which kind of
Mode carries out the inhibition of shafting torsional oscillation, is required to analyze the fatigue strength of equipment shafting before and after transformation, to protect
Demonstrate,prove the safe and stable operation of frequency conversion equipment.The stress distribution that shafting Fatigue Strength Analysis needs to know each shaft part is carried out, is usually adopted
Measure is to arrange measuring point in each shaft part, and directly measurement show that the stress of shafting divides by way of arranging multisensor
Cloth.But in specific test, the working environment of the equipment such as subsidiary engine is generally complex, various kinds of equipment characteristics of compact layout, often not
Has the condition in each ideal measuring point all placement sensors.
Summary of the invention
Goal of the invention: the object of the present invention is to provide a kind of rotating machinery shafting fatigue strength detection methods, it is only necessary to arrange
The stress distribution of each shaft part can be calculated with the method for the present invention, be equivalent to and arrange in each shaft part for one sensor node
Virtual-sensor, to carry out the detection of entire shafting fatigue strength.
Technical solution: to reach this purpose, the invention adopts the following technical scheme:
Rotating machinery shafting fatigue strength detection method of the present invention, comprising the following steps:
S1: establishing the lumped mass model for torsional vibration of target shafting, obtains movement of the target shafting under dynamic force moment T effect
Equation；
S2: establishing modal matrix φ and regularization factors α is calculated, and then acquires normal mode matrix φn；
S3: the equation of motion is changed into normal mode equation；
S4: the response and torque distribution of all shaft parts of target shafting are found out；
S5: the detection of target shafting fatigue strength is carried out.
Further, the equation of motion in the step S1 are as follows:
In formula (1), K is target shafting Torsional Stiffness Matrix, and J is moment of inertia matrix,For angular acceleration matrix, θ is angle
Transposed matrix.
Further, in the step S2, modal matrix φ is obtained according to formula (2):
In formula (2),For the amplitude of i-th of shaft part under jth first order mode, 1≤i≤n, 1≤j≤n, n are in target shafting
The sum of shaft part；
Regularization factors α is obtained according to formula (3):
In formula (3), J is moment of inertia matrix；
Normal mode matrix φnIt is obtained according to formula (4):
φn=φ α (4).
Further, in the step S3, the equation of motion is changed into the process of normal mode equation are as follows: with normal mode matrix
φnCoordinate conversion is carried out to the equation of motion as transformation matrix, new canoncial coordinates q is obtained, canonical is then obtained according to formula (5)
Modal equations:
In formula (5),θ is angular displacement matrix,For the acceleration matrix under canoncial coordinates, N is intrinsic frequency
Diagonal matrix composed by square value, N are obtained according to formula (6)；
In formula (6),For square of target shafting s rank intrinsic frequency.
Further, in the step S4, the response of all shaft parts of target shafting and torque distribution are asked by following procedure
: arbitrarily facilitate the shaft part of placement sensor measuring point to arrange foil gauge in target shafting, carries out the torque of shaft part in target shafting
Calculating, obtain the torque of shaft part；The dynamic torque of shaft part is acquired by the response of shaft part two sides.
Further, in the step S5, the process of target shafting fatigue strength detection are as follows: by calculating the antitorque of each shaft part
Section factor obtains the stress distribution of each shaft part, to carry out the detection of target shafting fatigue strength.
The utility model has the advantages that the invention discloses a kind of rotating machinery shafting fatigue strength detection methods, compared with prior art,
With following the utility model has the advantages that
1) present invention only needs one measuring point of arrangement, and the torque distribution of entire shafting can be calculated, make on-the-spot test
Journey is simpler efficiently, improves the efficiency of test；
2) any shaft part in shafting may be selected in point position in the present invention, has in specific engineering practice very strong
Application power is conducive to the situation for adapting to engineering site complexity.
Detailed description of the invention
Fig. 1 is the schematic diagram of four mass block models of specific embodiment of the invention center shafting；
Fig. 2 is point layout and the schematic diagram of the torque being calculated distribution in the specific embodiment of the invention；
Fig. 3 is the flow chart of method in the specific embodiment of the invention.
Specific embodiment
Technical solution of the present invention is further introduced With reference to embodiment.
Present embodiment discloses a kind of rotating machinery shafting fatigue strength detection method, as shown in figure 3, include with
Lower step:
S1: establishing the lumped mass model for torsional vibration of target shafting, obtains movement of the target shafting under dynamic force moment T effect
Equation；
S2: establishing modal matrix φ and regularization factors α is calculated, and then acquires normal mode matrix φn；
S3: the equation of motion is changed into normal mode equation；
S4: the response and torque distribution of all shaft parts of target shafting are found out；
S5: the detection of target shafting fatigue strength is carried out.
The equation of motion in step S1 are as follows:
In formula (1), K is target shafting Torsional Stiffness Matrix, and J is moment of inertia matrix,For angular acceleration matrix, θ is angle
Transposed matrix.
In step S2, modal matrix φ is obtained according to formula (2):
In formula (2),For the amplitude of i-th of shaft part under jth first order mode,It is by enabling T=0 in formula (1) acquire；
1≤i≤n, 1≤j≤n, n are the sum of shaft part in target shafting；
Regularization factors α is obtained according to formula (3):
In formula (3), J is moment of inertia matrix；
Normal mode matrix φnIt is obtained according to formula (4):
φn=φ α (4).
In step S3, the equation of motion is changed into the process of normal mode equation are as follows: with normal mode matrix φnAs transformation
Matrix carries out coordinate conversion to the equation of motion, obtains new canoncial coordinates q, then obtains normal mode equation according to formula (5):
In formula (5),θ is angular displacement matrix,For the acceleration matrix under canoncial coordinates, N is intrinsic frequency
Diagonal matrix composed by square value, N are obtained according to formula (6)；
In formula (6),For square of target shafting s rank intrinsic frequency.Intrinsic frequency is by enabling T=0 in formula (1)
It acquires.
In step S4, the response of all shaft parts of target shafting and torque distribution are acquired by following procedure: in target axis
It is any shaft part arrangement foil gauge for facilitating placement sensor measuring point, carries out the calculating of the torque of shaft part in target shafting, obtain
The torque of shaft part；The dynamic torque of shaft part is acquired by the response of shaft part two sides.
In step S5, the process of target shafting fatigue strength detection are as follows: the Torsion Section coefficient by calculating each shaft part obtains
To the stress distribution of each shaft part, to carry out the detection of target shafting fatigue strength.
Embodiment 1:
The present embodiment constructs a four mass block models, only arranges a measuring point to each shaft part stress point at the second shaft segment
Cloth is calculated, and to carry out the detection of fatigue strength, referring to Fig.1~3, the specific method is as follows:
(1) four mass block analysis model of shafting is established as shown in Figure 1, in J1Apply torque T at mass blocke.Four matter in figure
The rotary inertia of gauge block is respectively J1、J2、J3And J4, the torsion stiffness of three shaft parts is respectively K1、K2、K3, θ1、θ2、θ3、θ4Respectively
Indicate each section of relative angular displacement.It is as follows that shafting dynamics equation is established according to Fig. 1:
In formula:
It enablesSolution obtains shafting torsional natural frequency ωn1、ωn2、ωn3、ωn4And each first order mode.
(2) it establishes modal matrix φ and regularization factors α is calculated, and then acquire normal mode matrix φn:
(3) coordinate dehorn is carried out to original equation using normal mode matrix, original system equation is become into normal mode equation:
Wherein, q is new canoncial coordinates:
It is integrated using Duhamel to normal mode equation solution, is obtained:
Pass through linear transformation θ=φ againnQ obtains each section of relative angular displacement θ1、θ2、θ3、θ4。
It (4) is T according to the torque that the sensor of arrangement measures the second shaft part2, then T2=K2(θ2-θ3)。θ2With θ3It is to close
In TeFunction, solve can obtain motor application torque Te, and then acquire system response θ1、θ2、θ3、θ4.Each section of torque of shafting point
Cloth is as follows, as shown in Figure 2.
T1=K1(θ1-θ2)；T2=K2(θ2-θ3)；T3=K3(θ3-θ4)
(5) according to torsional stress calculation formulaEach stress distribution can be calculated and then carry out shafting intensity
Detection.
Claims (6)
1. rotating machinery shafting fatigue strength detection method, it is characterised in that: the following steps are included:
S1: establishing the lumped mass model for torsional vibration of target shafting, obtains movement side of the target shafting under dynamic force moment T effect
Journey；
S2: establishing modal matrix φ and regularization factors α is calculated, and then acquires normal mode matrix φn；
S3: the equation of motion is changed into normal mode equation；
S4: the response and torque distribution of all shaft parts of target shafting are found out；
S5: the detection of target shafting fatigue strength is carried out.
2. rotating machinery shafting fatigue strength detection method according to claim 1, it is characterised in that: in the step S1
The equation of motion are as follows:
In formula (1), K is target shafting Torsional Stiffness Matrix, and J is moment of inertia matrix,For angular acceleration matrix, θ is angular displacement
Matrix.
3. rotating machinery shafting fatigue strength detection method according to claim 1, it is characterised in that: the step S2
In, modal matrix φ is obtained according to formula (2):
In formula (2),For the amplitude of i-th of shaft part under jth first order mode, 1≤i≤n, 1≤j≤n, n are lumped mass torsional oscillation mould
The sum of shaft part in type；
Regularization factors α is obtained according to formula (3):
In formula (3), J is moment of inertia matrix；
Normal mode matrix φnIt is obtained according to formula (4):
φn=φ α (4).
4. rotating machinery shafting fatigue strength detection method according to claim 1, it is characterised in that: the step S3
In, the equation of motion is changed into the process of normal mode equation are as follows: with normal mode matrix φnAs transformation matrix to the equation of motion
Coordinate conversion is carried out, new canoncial coordinates q is obtained, normal mode equation is then obtained according to formula (5):
In formula (5), q=φn -1θ, θ are angular displacement matrix,For the acceleration matrix under canoncial coordinates, N is the flat of intrinsic frequency
Side is worth composed diagonal matrix, and N is obtained according to formula (6)；
In formula (6),For square of target shafting s rank intrinsic frequency.
5. rotating machinery shafting fatigue strength detection method according to claim 1, it is characterised in that: the step S4
In, the response of all shaft parts of target shafting and torque distribution are acquired by following procedure: arbitrarily facilitating arrangement in target shafting
The shaft part of Sensor arranges foil gauge, carries out the calculating of the torque of shaft part in target shafting, obtains the torque of shaft part；Pass through
The response of shaft part two sides acquires the dynamic torque of shaft part.
6. rotating machinery shafting fatigue strength detection method according to claim 1, it is characterised in that: the step S5
In, the process of target shafting fatigue strength detection are as follows: the Torsion Section coefficient by calculating each shaft part obtains the stress of each shaft part
Distribution, to carry out the detection of target shafting fatigue strength.
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| CN201910325019.6A CN110046441B (en) | 2019-04-22 | 2019-04-22 | Fatigue strength detection method for rotary mechanical shafting |
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| CN201910325019.6A CN110046441B (en) | 2019-04-22 | 2019-04-22 | Fatigue strength detection method for rotary mechanical shafting |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111159940A (en) * | 2019-12-25 | 2020-05-15 | 中国石油天然气集团有限公司 | Fatigue life analysis method for drill rod of horizontal directional drill |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101173877A (en) * | 2007-12-04 | 2008-05-07 | 四方电气(集团)有限公司 | Method for measuring mechanical fatigue of steam turbine generator unit shaft system |
| CN101603855A (en) * | 2009-07-16 | 2009-12-16 | 华北电力大学 | The analytical approach of shafting torsional vibration of turbo-generator set |
| CN104236705A (en) * | 2014-09-19 | 2014-12-24 | 华北电力大学 | Method and system for monitoring large disturbance transient impact torsional vibration of turbine-generator shaft system |
-
2019
- 2019-04-22 CN CN201910325019.6A patent/CN110046441B/en active Active
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101173877A (en) * | 2007-12-04 | 2008-05-07 | 四方电气(集团)有限公司 | Method for measuring mechanical fatigue of steam turbine generator unit shaft system |
| CN101603855A (en) * | 2009-07-16 | 2009-12-16 | 华北电力大学 | The analytical approach of shafting torsional vibration of turbo-generator set |
| CN104236705A (en) * | 2014-09-19 | 2014-12-24 | 华北电力大学 | Method and system for monitoring large disturbance transient impact torsional vibration of turbine-generator shaft system |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111159940A (en) * | 2019-12-25 | 2020-05-15 | 中国石油天然气集团有限公司 | Fatigue life analysis method for drill rod of horizontal directional drill |
| CN111159940B (en) * | 2019-12-25 | 2020-09-01 | 中国石油天然气集团有限公司 | Fatigue life analysis method for drill rod of horizontal directional drill |
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