CN111005832A - Dynamic balance method for water pump turbine runner - Google Patents

Dynamic balance method for water pump turbine runner Download PDF

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Publication number
CN111005832A
CN111005832A CN201911233086.1A CN201911233086A CN111005832A CN 111005832 A CN111005832 A CN 111005832A CN 201911233086 A CN201911233086 A CN 201911233086A CN 111005832 A CN111005832 A CN 111005832A
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China
Prior art keywords
rotating wheel
correction
dynamic balance
mass
runner
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CN201911233086.1A
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Chinese (zh)
Inventor
刘德民
马信武
段昌德
李宁
赵永智
吴中竟
吴伟
石清华
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Dongfang Electric Machinery Co Ltd DEC
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Dongfang Electric Machinery Co Ltd DEC
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Priority to CN201911233086.1A priority Critical patent/CN111005832A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03B—MACHINES OR ENGINES FOR LIQUIDS
    • F03B11/00—Parts or details not provided for in, or of interest apart from, the preceding groups, e.g. wear-protection couplings, between turbine and generator
    • F03B11/04—Parts or details not provided for in, or of interest apart from, the preceding groups, e.g. wear-protection couplings, between turbine and generator for diminishing cavitation or vibration, e.g. balancing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03B—MACHINES OR ENGINES FOR LIQUIDS
    • F03B11/00—Parts or details not provided for in, or of interest apart from, the preceding groups, e.g. wear-protection couplings, between turbine and generator
    • F03B11/008—Measuring or testing arrangements
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/20—Hydro energy

Abstract

The invention discloses a dynamic balancing method for a water pump turbine runner, which at least comprises the following steps: s1: based on the shape of the rotating wheel to be balanced, the distance b between two correction planes of the rotating wheel and the distances a and c between the correction planes and the left and right support bearings are measured, and the equivalent rotating radius r of the two correction planes is completed1And r2Measuring (2); s2: the rotating wheel is arranged on the dynamic balance equipment to rotate at an angular velocity omega, and when the rotating wheel rotates, the pressure F for supporting the rotating wheel left and right is completed1And F2Measuring (2); s3: when the left and right correction surfaces of the rotating wheel are respectively provided with the correction blocks to achieve dynamic balance, the resultant force and resultant moment on the rotor are zero, and the centrifugal force on the two correction blocks is measured; and S4, calculating the correction mass of the correction block based on the measured centrifugal force value and the centrifugal force calculation formula. The rotating wheel after dynamic balance of the invention is in pressure pulsation and hydraulic efficiency index of the water turbine and the rotating wheel after static balanceCompared with the prior art, the performance of the rotating wheel can be more objectively embodied.

Description

Dynamic balance method for water pump turbine runner
Technical Field
The invention belongs to the technical field of fluid machinery power generation, and particularly relates to a dynamic balance method for a water pump turbine runner.
Background
The rotating speed of the water pump water turbine model rotating wheel is mostly about 1000 revolutions per minute due to the working characteristics, if the rotating speed is lower than 500r/min, the unbalanced distribution of the rotor mass cannot change along with the change of the rotating speed, and if the rotating speed is higher than 500r/min, the unbalanced distribution of the rotor mass can change along with the change of the rotating speed, so that the objectivity of a test result is greatly influenced.
Conventional static balancing methods can balance the unbalanced mass of the rotor within certain limits, but the accuracy is not high. Dynamic balancing is a good way to balance the rotor. The unbalanced mass of the rotor can be controlled to a very small extent. The rotor with qualified dynamic balance can keep a balance state at any other rotating speed.
Disclosure of Invention
The invention aims to: by applying the dynamic balancing method of the rotating wheel, the unbalanced mass of the rotating wheel caused by processing is reduced as much as possible, so that the rotating unbalance caused by the mass unbalance is reduced, and the testing accuracy of the hydraulic performance parameters is further influenced.
The purpose of the invention is realized by the following technical scheme:
a dynamic balancing method for a water pump turbine runner at least comprises the following steps:
s1: based on the shape of the rotating wheel to be balanced, the distance b between two correction planes of the rotating wheel and the distances a and c between the correction planes and the left and right support bearings are measured, and the equivalent rotating radius r of the two correction planes is completed1And r2Measuring (2);
s2: the rotating wheel is arranged on the dynamic balance equipment to rotate at an angular velocity omega, and when the rotating wheel rotates, the pressure F for supporting the rotating wheel left and right is completed1And F2Measuring (2);
s3: when the runner is equipped with the proof mass respectively and reaches dynamic balance about the correction surface, then satisfy resultant force and the resultant moment that the rotor received and be zero, promptly:
F1+F2-f1-f2＝0
a·F1+b·f2-(b+c)·F2＝0，
measure f1And f2And f is1And f2The centrifugal force to which the two correction blocks are respectively subjected;
s4-based on the measured f1And f2And m based on the corrected mass1And m2The formula for calculating the centrifugal force of the correction block is as follows:
f1＝m1·r1 2·ω2
f2＝m2·r2 2·ω2
obtaining the correction masses m of the two correction blocks1And m2Whereby the dynamic set mass is m1And m2The correcting block realizes the dynamic balance of the rotating wheel.
According to a preferred embodiment, the correction mass m is the mass of two correction blocks1And m2The rotating wheel realizes dynamic balance when the residual unbalance is smaller than the allowable residual unbalance of the rotating wheel.
According to a preferred embodiment, the allowable residual unbalance of the runner is 50.16 g.
The main scheme and the further selection schemes can be freely combined to form a plurality of schemes which are all adopted and claimed by the invention; in the invention, the selection (each non-conflict selection) and other selections can be freely combined. The skilled person in the art can understand that there are many combinations, which are all the technical solutions to be protected by the present invention, according to the prior art and the common general knowledge after understanding the scheme of the present invention, and the technical solutions are not exhaustive herein.
The invention has the beneficial effects that: the dynamic balance method is suitable for the vertical model water pump turbine runner, and the runner after dynamic balance is improved in pressure pulsation and hydraulic efficiency indexes of the water turbine compared with the runner after static balance, so that the performance of the runner can be more objectively embodied.
Drawings
FIG. 1 is a schematic diagram of a test structure of the dynamic balancing method of the rotating wheel of the present invention;
FIG. 2 is a schematic diagram of a static balance test structure of a model runner;
FIG. 3 is a graph of the effect of a dynamically and statically balanced rotor on pressure pulsations;
fig. 4 is a graph of the effect of a dynamically and statically balanced runner on the hydraulic efficiency of a turbine.
Detailed Description
The following non-limiting examples serve to illustrate the invention.
Example 1:
referring to fig. 1, a schematic diagram of a test structure of the dynamic balancing method of the rotating wheel of the present invention is shown.
A dynamic balancing method for a water pump turbine runner at least comprises the following steps:
step S1: based on the shape of the rotating wheel to be balanced, the distance b between two correction planes of the rotating wheel and the distances a and c between the correction planes and the left and right support bearings are measured, and the equivalent rotating radius r of the two correction planes is completed1And r2The measurement of (2).
Step S2: the rotating wheel is arranged on the dynamic balance equipment to rotate at an angular velocity omega, and when the rotating wheel rotates, the pressure F for supporting the rotating wheel left and right is completed1And F2The measurement of (2).
Step S3: when the left and right correction surfaces of the rotating wheel are respectively provided with the correction blocks to achieve dynamic balance, the resultant force and resultant moment on the rotor are zero,
∑F＝0,∑M＝0 (1)
namely:
F1+F2-f1-f2＝0 (2)
a·F1+b·f2-(b+c)·F2＝0 (3)
wherein, the formula (3) can be used for obtaining:
Figure BDA0002304101830000031
substituting formula (4) into formula (2) yields:
Figure BDA0002304101830000032
thus, f is measured1And f2And f is1And f2The centrifugal force to which the two correction blocks are respectively subjected.
Step S4, based on the measured f1And f2And m based on the corrected mass1And m2The formula for calculating the centrifugal force of the correction block is as follows:
f1＝m1·r1 2·ω2(6)
f2＝m2·r2 2·ω2(7)
obtaining the correction masses m of the two correction blocks1And m2，
Figure BDA0002304101830000033
Figure BDA0002304101830000034
Thereby setting the mass m of the moving blade1And m2The correcting block realizes the dynamic balance of the rotating wheel.
Preferably, the correction mass m of the two correction blocks is1And m2The rotating wheel realizes dynamic balance when the residual unbalance is smaller than the allowable residual unbalance of the rotating wheel. Further, the allowable residual unbalance amount of the runner is 50.16 g.
Preferably, the allowable residual unbalance amount of the pump turbine runner according to the present invention can be obtained by:
assuming that the mass of the correction block is M, the mass of the model runner is M, the distance between the center of gravity and the rotating axis is R, and the distance between the correction block and the rotating axis is R, in order to meet the static balance requirement, the resultant force of inertial centrifugal force is zero, namely:
Figure BDA0002304101830000041
the resultant force of inertial centrifugal force generated by the static balance correction block is zero, the model rotating wheel achieves static balance, but the moment of inertia couple generated by the static balance correction block to the rotating shaft is not zero, namely the couple is unbalanced. Couple imbalance needs to be corrected using dynamic balancing methods, especially for rigid rotors.
The critical speed is the speed at which the rotor vibrates strongly, and if the operating speed of the rotor system is below the first-order critical speed, the deflection of the rotor caused by the centrifugal force generated by the mass unbalance is negligible, and this kind of rotor is a rigid rotor. If the rotor is rigid, the unbalanced distribution of the rotor mass will not change with the change of the rotation speed, so that the rotor with qualified dynamic balance can keep a balanced state at any other rotation speed.
In addition, the weight of the pumped storage model runner is about 100kg, the diameter D is about 600mm, the axial length b is about 200mm, the width ratio D/b of the runner diameter is 3, the working rotating speed is about 1000 revolutions per minute, and according to the test condition of the single-stage water pump impeller rotor, when the width ratio D/b is less than 6, the dynamic balance test effect is best.
Couple imbalance is the imbalance condition where the principal axis of inertia of the rotor intersects the axis of rotation at the center of gravity, the principal vector being 0 and the principal moment being other than 0. The couple imbalance may be represented by a pair of vectors of equal magnitude and opposite direction, as shown in fig. 1. This unbalance needs to be corrected by a set of correction amounts of the same size and opposite directions on the two correction planes.
Assuming a model rotor with mass M and eccentricity e, when the rotor rotates at angular velocity ωWill generate centrifugal force
Figure BDA0002304101830000042
The size is as follows:
Figure BDA0002304101830000043
to balance the model wheel, a calibration mass m is added to the other side of the eccentricity, at a distance r from the axis of rotation, to generate a centrifugal force of:
Figure BDA0002304101830000044
i.e. the centrifugal force of inertia
Figure BDA0002304101830000045
Equal in size, opposite in direction:
M·e·ω2＝m·r·ω2(13)
namely:
M·e＝m·r (14)
the degree of unbalance e of the rotor is often expressed in engineering terms by dividing the amount of unbalance by the rotor mass:
Figure BDA0002304101830000046
the international standardization organization generally adopts the unbalanced intensity Su as a measurement standard of dynamic balance precision, the measurement means is also used in the national standard, and the calculation mode of the Su is as follows:
Su＝ε·ω (16)
the balance precision required by the water pump impeller is G6.3, namely Su 1001/5And the balance precision is approximately equal to 6.3mm/s, and in order to meet the balance precision requirement, a special dynamic balance device is required to perform dynamic balance test and correction on the model runner.
According to the requirement of the dynamic balance test precision grade of the water pump rotor specified by the national standard, the allowable residual unbalance of the model runner can be calculated by the formulas (15) and (16) as follows:
Figure BDA0002304101830000051
example 2
The comparison between the dynamic balance method of the present invention and the conventional static balance method is accomplished by this embodiment.
Referring to fig. 2, the static balance test and correction process (fig. 2) for the model runner according to the static balance principle is as follows:
(1) the model runner 1 is firstly installed on the mandrel 2 and then placed on a static balance test support 3 with adjusted level, two cylindrical rails are arranged on the support, and the mandrel can freely roll on the cylindrical rails.
(2) And recording the overweight side of the model runner. If the mass distribution of the model runner is not uniform, the heavier part always automatically turns to the lower part. The correction block is added to the heavier (i.e., lighter) side until the model wheel is stationary at any position.
(3) The proof mass is weighed out (proof mass), i.e. the amount of significant unbalance.
(4) And removing the weight at the position of the model rotating wheel with the unbalanced weight, which is close to the outer edge, generally by using a drilling mode, wherein the removed weight is consistent with the weight of the correction block.
The table 1 is the statistics of the significant unbalance of the three pumped storage hydraulic test model rotating wheels after static balance.
TABLE 1 model significant unbalance after static Balancing of the rotor
Figure BDA0002304101830000052
Wherein the unbalance is greater than the significant unbalance for the runner 3.
The data of the three model rotating wheels subjected to the dynamic balance test by the dynamic balance method of the invention for the rotating wheel 1, the rotating wheel 2 and the rotating wheel 3 are shown in table 2.
TABLE 2 dynamic balance of model rotor
Figure BDA0002304101830000061
It can be seen that the calibration masses m of the three test model wheels1And m2Less than 50.16g of allowable residual unbalance, i.e. the correction mass m1And m2And the residual unbalance is smaller than the allowable residual unbalance, so that the rotating wheel can be directly put into use without performing quality correction on the rotating wheel. The dynamic balance precision can better meet the use requirement of the hydraulic performance test of the model runner.
Further, taking the runner 3 as an example, the test result shows that the runner subjected to dynamic balance correction reduces the pressure pulsation amplitude by 1.5% and improves the hydraulic efficiency of the water turbine by 0.2% compared with the runner subjected to static balance correction, as shown in fig. 3 and 4.
The foregoing basic embodiments of the invention and their various further alternatives can be freely combined to form multiple embodiments, all of which are contemplated and claimed herein. In the scheme of the invention, each selection example can be combined with any other basic example and selection example at will. Numerous combinations will be known to those skilled in the art.
The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the invention, and any modifications, equivalents and improvements made within the spirit and principle of the present invention are intended to be included within the scope of the present invention.

Claims (3)

1. A method for dynamically balancing a water pump turbine runner is characterized by at least comprising the following steps:
s1: based on the shape of the rotating wheel to be balanced, the distance b between two correction planes of the rotating wheel and the distances a and c between the correction planes and the left and right support bearings are measured, and the equivalent rotating radius r of the two correction planes is completed1And r2Measuring (2);
s2: the rotating wheel is arranged on the dynamic balance equipment to rotate at an angular velocity omega, and when the rotating wheel rotates, the pressure F for supporting the rotating wheel left and right is completed1And F2Measuring (2);
s3: when the runner is equipped with the proof mass respectively and reaches dynamic balance about the correction surface, then satisfy resultant force and the resultant moment that the rotor received and be zero, promptly:
F1+F2-f1-f2＝0
a·F1+b·f2-(b+c)·F2＝0，
measure f1And f2And f is1And f2The centrifugal force to which the two correction blocks are respectively subjected;
s4-based on the measured f1And f2And m based on the corrected mass1And m2The formula for calculating the centrifugal force of the correction block is as follows:
f1＝m1·r12·ω2
f2＝m2·r22·ω2
obtaining the correction masses m of the two correction blocks1And m2Whereby the dynamic set mass is m1And m2The correcting block realizes the dynamic balance of the rotating wheel.
2. The method of claim 1, wherein the correcting mass m of the two correcting blocks is set as m1And m2The rotating wheel realizes dynamic balance when the residual unbalance is smaller than the allowable residual unbalance of the rotating wheel.
3. The method of claim 1, wherein the allowable residual unbalance amount of the runner is 50.16 g.
CN201911233086.1A 2019-12-05 2019-12-05 Dynamic balance method for water pump turbine runner Pending CN111005832A (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111898238A (en) * 2020-06-09 2020-11-06 天津大学 Constraint high-speed dynamic balance mechanics resolving method

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Publication number Priority date Publication date Assignee Title
JPH11270479A (en) * 1998-03-25 1999-10-05 Taiko Kikai Industries Co Ltd Screw rotor for vacuum pump
CN202622274U (en) * 2012-06-29 2012-12-26 宁夏青龙塑料管材有限公司 Vacuum pump impeller dynamic balance alignment device
CN110319976A (en) * 2019-07-04 2019-10-11 重庆水轮机厂有限责任公司 A kind of francis turbine runner dynamic balance running method

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH11270479A (en) * 1998-03-25 1999-10-05 Taiko Kikai Industries Co Ltd Screw rotor for vacuum pump
CN202622274U (en) * 2012-06-29 2012-12-26 宁夏青龙塑料管材有限公司 Vacuum pump impeller dynamic balance alignment device
CN110319976A (en) * 2019-07-04 2019-10-11 重庆水轮机厂有限责任公司 A kind of francis turbine runner dynamic balance running method

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111898238A (en) * 2020-06-09 2020-11-06 天津大学 Constraint high-speed dynamic balance mechanics resolving method
CN111898238B (en) * 2020-06-09 2022-09-27 天津大学 Constraint high-speed dynamic balance mechanics resolving method

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Application publication date: 20200414