CN110146280B - Experimental device and experimental method for measuring dynamic mechanical quantity of rotary machine - Google Patents
Experimental device and experimental method for measuring dynamic mechanical quantity of rotary machine Download PDFInfo
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- CN110146280B CN110146280B CN201910492214.8A CN201910492214A CN110146280B CN 110146280 B CN110146280 B CN 110146280B CN 201910492214 A CN201910492214 A CN 201910492214A CN 110146280 B CN110146280 B CN 110146280B
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Classifications
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01D—MEASURING NOT SPECIALLY ADAPTED FOR A SPECIFIC VARIABLE; ARRANGEMENTS FOR MEASURING TWO OR MORE VARIABLES NOT COVERED IN A SINGLE OTHER SUBCLASS; TARIFF METERING APPARATUS; MEASURING OR TESTING NOT OTHERWISE PROVIDED FOR
- G01D5/00—Mechanical means for transferring the output of a sensing member; Means for converting the output of a sensing member to another variable where the form or nature of the sensing member does not constrain the means for converting; Transducers not specially adapted for a specific variable
- G01D5/26—Mechanical means for transferring the output of a sensing member; Means for converting the output of a sensing member to another variable where the form or nature of the sensing member does not constrain the means for converting; Transducers not specially adapted for a specific variable characterised by optical transfer means, i.e. using infrared, visible, or ultraviolet light
- G01D5/32—Mechanical means for transferring the output of a sensing member; Means for converting the output of a sensing member to another variable where the form or nature of the sensing member does not constrain the means for converting; Transducers not specially adapted for a specific variable characterised by optical transfer means, i.e. using infrared, visible, or ultraviolet light with attenuation or whole or partial obturation of beams of light
- G01D5/34—Mechanical means for transferring the output of a sensing member; Means for converting the output of a sensing member to another variable where the form or nature of the sensing member does not constrain the means for converting; Transducers not specially adapted for a specific variable characterised by optical transfer means, i.e. using infrared, visible, or ultraviolet light with attenuation or whole or partial obturation of beams of light the beams of light being detected by photocells
- G01D5/347—Mechanical means for transferring the output of a sensing member; Means for converting the output of a sensing member to another variable where the form or nature of the sensing member does not constrain the means for converting; Transducers not specially adapted for a specific variable characterised by optical transfer means, i.e. using infrared, visible, or ultraviolet light with attenuation or whole or partial obturation of beams of light the beams of light being detected by photocells using displacement encoding scales
- G01D5/3473—Circular or rotary encoders
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M1/00—Testing static or dynamic balance of machines or structures
- G01M1/14—Determining unbalance
- G01M1/16—Determining unbalance by oscillating or rotating the body to be tested
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M1/00—Testing static or dynamic balance of machines or structures
- G01M1/14—Determining unbalance
- G01M1/16—Determining unbalance by oscillating or rotating the body to be tested
- G01M1/20—Determining unbalance by oscillating or rotating the body to be tested and applying external forces compensating forces due to unbalance
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M13/00—Testing of machine parts
- G01M13/02—Gearings; Transmission mechanisms
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M13/00—Testing of machine parts
- G01M13/02—Gearings; Transmission mechanisms
- G01M13/028—Acoustic or vibration analysis
Abstract
The invention discloses a dynamic mechanical quantity measurement experiment device and an experiment method of a rotary machine, wherein the device comprises a rotary machine base, one side of a double-shaft motor is connected with a photoelectric rotary encoder, the other side of the double-shaft motor is connected with a rotor disc rotating shaft through a flexible coupling joint, two ends of the rotor disc rotating shaft are respectively fixed through a ball bearing and a movable bearing, a rotor disc is fixed on the rotor disc rotating shaft through screws, the number of the rotor discs can be changed, the position of the rotor disc on the rotor disc rotating shaft can be adjusted, and a screw hole for installing weights is formed in the rotor disc; the two sides of the movable bearing are respectively provided with a force sensor and a fixed block, and are connected to the fixed support by bolts at the two sides, and the movable bearing is centered with the ball bearing by adjusting the positions of the bolts at the two sides; the displacement sensor bracket is fixed on the rotary machine base, and the eddy current displacement sensor is arranged on the sensor bracket; the experimental device can realize 7 experimental teaching contents, and has the advantages of strong experimental design, diversity, compact overall structure, simple operation, high integration level and the like.
Description
Technical Field
The invention relates to a mechanical experiment device, in particular to a dynamic mechanical quantity measurement experiment device and method of rotary machinery.
Background
In engineering practice, the rotation axis of the rotary machine may deviate from the central principal axis of inertia due to factors such as installation, manufacturing, or non-uniformity of the material itself. Therefore, when the rotary machine runs at a high speed, larger additional dynamic counter force is generated due to inertia force, abrasion of the bearing is increased, vibration and noise are also generated, the transmission efficiency of the machine is reduced, normal use of the machine is affected, and the service life of the machine is shortened. The change of the additional dynamic counter force of the rotary machine, the vibration amplitude of the rotary shaft and the axis locus reflect the vibration, the eccentricity and the running condition of the bearing of the rotary shaft. Therefore, in the fault diagnosis of the engineering rotary machine, monitoring of the additional dynamic reaction force of the bearing seat, the amplitude of the rotating shaft and the axis locus is very important. In teaching, in order to intuitively reflect the actual problem of engineering, it is necessary to simulate the actual working condition and develop a student experiment device with strong operability, simplicity and reliability for measuring dynamic mechanical quantity of rotary machinery.
Disclosure of Invention
In order to solve the problems in the prior art, the invention aims to provide a rotary mechanical dynamic mechanical quantity measurement experimental device and an experimental method, wherein the experimental device can realize 7 experimental teaching contents: a rotary machine single rotor disc bearing seat dynamic reaction force measurement experiment, a rotary machine multiple rotor disc bearing seat dynamic reaction force measurement experiment (2 rotor discs and more), a rotary machine single rotor disc dynamic balance experiment, a rotary machine multiple rotor disc dynamic balance experiment, a rotary machine rotating shaft vibration amplitude measurement experiment, a rotary machine rotating shaft axis track experiment, a rotary machine rotating speed, an angular velocity, an angular acceleration measurement experiment and the like. The experimental device has the advantages of strong experimental design, diversity, compact overall structure, simplicity in operation, high integration level and the like.
In order to achieve the above purpose, the invention adopts the following technical scheme:
the utility model provides a rotary machine dynamic mechanical quantity measurement experimental apparatus, includes rotary machine base 1, and biax motor 2 is fixed on rotary machine base 1, and the photoelectric rotary encoder 3 of control biax motor 2 rotational speed is connected to biax motor 2's a axle, and another axle of biax motor 2 passes through flexible coupling 4 to be connected rotor dish pivot 5, rotor dish pivot 5 one end is fixed through ball bearing 6 installed on rotary machine base 1, and the other end is fixed through movable bearing 7 installed on rotary machine base 1, and ball bearing 6 is close to biax motor 2; the rotor discs 8 are fixedly connected to the rotor disc rotating shaft 5 through screws 10, screw holes capable of being provided with weights 9 are uniformly formed in the rotor discs 8, the flexible coupling shaft joint 4 is opened, the rotor disc rotating shaft 5 is moved to one end of the movable bearing 7, namely the number of the rotor discs 8 can be increased or reduced on the rotating shaft 5, and the positions of the rotor discs 8 can be freely adjusted; the left side of the movable bearing 7 is provided with a force sensor 11 and is connected to a fixed support 13 through a left bolt 12, the right side of the movable bearing 7 is provided with a fixed block 14 and is connected to the fixed support 13 through a right bolt 15, the fixed support 13 is fixedly arranged on the rotary machine base 1, and the movable bearing 7 is centered with the ball bearing 6 through the positions of the left bolt 12 and the right bolt 15; when the axis track and the amplitude of the rotor disc rotating shaft 5 need to be measured, a displacement sensor bracket 16 is fixed on the rotary machine base 1, one or two eddy current displacement sensors 17 are installed on the displacement sensor bracket 16, the axis track of the rotor disc rotating shaft 5 can be measured by installing the two eddy current displacement sensors 17 vertically, the vibration amplitude of the rotor disc rotating shaft 5 can be measured by installing the one eddy current displacement sensor 17, and the position of the displacement sensor bracket 16 on the rotor disc rotating shaft 5 can be adjusted.
The double-shaft motor 2 is connected through flexible coupling 4 to rotor disc pivot 5 one end to fixed through ball bearing 6, the other end is fixed through movable bearing 7, and after ball bearing 6 position was confirmed, movable bearing 7 can furthest guarantee that rotor disc pivot 5 aligns with the center of double-shaft motor 2 axle, and flexible coupling 4 can guarantee the flexible connection of rotor disc pivot 5 and double-shaft motor 2 axle, in order to ensure experimental result reliability.
The rotor disc 8 is evenly provided with screw holes which can be used for installing weights 9 along the circumferential direction, so that weight quality and installation positions can be automatically designed according to different experimental requirements.
One side of the force sensor 11 is arranged on the movable bearing 7, the other side of the force sensor 11 is connected to the fixed support 13, the force sensor 11 is horizontally arranged, the influence of the gravity of the rotor disc 8 on the force measurement value is not considered, and the measurement value is the horizontal component of the dynamic reaction force of the bearing seat.
According to the experimental method of the experimental device for measuring the dynamic mechanical quantity of the rotary machine, when the rotor disc 8 is in initial dynamic balance, weights with arbitrary mass are installed at different screw hole positions of the rotor disc 8, the additional dynamic counter force of the bearing seat is measured through the force sensor 11, if the rotor disc 8 has eccentric mass, the dynamic counter force of the bearing seat can be measured in real time through adjusting the mass and the installation position of the weights, the eccentric mass position can be determined, when a plurality of rotor discs 8 are installed on the rotor disc rotating shaft 5, the dynamic balance is achieved through designing and adjusting the mass and the position of the weights, the dynamic balance experiment is carried out, the axial center track of the rotor disc rotating shaft 5 can be measured by vertically installing two eddy current sensors 17 on the displacement sensor bracket 16, and the vibration amplitude of the rotor disc rotating shaft 5 can be measured by installing one eddy current sensor 17.
The measuring bearing seat dynamic counterforce comprises a rotating machine multiple-rotor disc bearing seat dynamic counterforce measuring experiment and a rotating machine single-rotor disc bearing seat dynamic counterforce measuring experiment;
1) Dynamic reaction force measurement experiment of a plurality of rotor disc bearing seats of rotary machinery: taking two rotor discs as an example, weights 9 are arranged at any scale positions on the two rotor discs 8 which are in dynamic balance initially, the distance from the weights 9 to the center of a rotor disc rotating shaft 5 is e, and the mass of the weights 9, namely the eccentric mass, is m respectively 1 And m 2 The included angle between the two eccentric masses is theta, the rotating speed of the rotary machine is omega, and the inertia forces generated by the two eccentric masses are F respectively g1 ＝m 1 eω 2 ，F g2 ＝m 2 eω 2 The method comprises the steps of carrying out a first treatment on the surface of the According to the darebel principle, the column balance equation is as follows:
∑F x ＝F Ax +F Bx -F g2 sinθ＝0
∑F y ＝0
SF z ＝F Az +F Bz -F g1 -F g2 cosθ-G 1 -G 2 ＝0
SM Ax (F)＝F g1 l+F g2 2lcosθ+G 1 l+G 2 2l-F Bz 3l＝0
SM Ay (F)＝0
∑M Az (F)＝F Bx 3l-F g2 2lsinθ＝0
wherein F is x 、F y And F z Resultant force in x, y and z directions respectively, M Ax 、M Ay And M Az Respectively the resultant moment of forces in the directions of x, y and z to the point A, F Ax And F Bx The components of the dynamic counter force of the A, B two-point bearing seat on the rotary machine base in the x direction are respectively F Az And F Bz The components of the dynamic counter force of the A, B two-point bearing seat on the rotary machine base in the z direction are respectively G 1 For rotor disc mass and eccentric mass m 1 And, G 2 For rotor disc mass and eccentric mass m 2 And l is the distance between the rotor disks and the A, B points on the rotor disks and the rotary machine base; because the dynamic counter force is measured in the experiment, and gravity only affects the static counter force in the counter force of the support, the dynamic counter force result has no influence of gravity;
solving the equation to obtain:
then, the magnitudes of the two click reaction forces A, B of the rotary machine base 1 are respectively:
in the experiment, the force sensor 11 is arranged in the horizontal direction of the point B, so that the horizontal component of the bearing seat dynamic counterforce can be measured in real time, and the peak value of the measured value of the force sensor 11 is the magnitude of the bearing seat dynamic counterforce:
therefore, the bearing support reaction force can be measured from the mass and the mounting position of the weight 9. The experimental device measurement data are well matched with the theoretical result of the Dallange principle.
2) And (3) a single rotor disc bearing seat dynamic reaction force measurement experiment of the rotary machine: for a single rotor disc system of a rotary machine, weights 9 are arranged at any scale positions on the rotor disc 8, the center distance from the weights 9 to the rotor disc rotating shaft 5 is e, the mass of the weights 9, namely the eccentric mass, is m, and the rotating speed is omega, so that the generated inertia force is F g ＝m eω 2 The method comprises the steps of carrying out a first treatment on the surface of the According to the darebel principle, the column balance equation is as follows:
∑F x ＝0
∑F y ＝0
SF z ＝F Az +F Bz -F g -G＝0
∑M Ax (F)＝F g l+Gl-F Bz 2l＝0
∑M Ay (F)＝0
∑M Az (F)＝0
wherein F is x 、F y And F z Resultant force in x, y and z directions respectively, M Ax 、M Ay And M Az The resultant moment of forces in the directions of x, y and z on the rotating machine base at the point A is respectively shown as F Az And F Bz The component of the dynamic reaction force of the bearing seats at A, B points on the rotary machine base in the z direction is respectively represented by G, wherein G is the sum of the mass of the rotor disc and the eccentric mass m, and l is the distance between the rotor disc and A, B points on the rotary machine base; since the dynamic reaction force is measured in the experiment, and gravity only affects the static reaction force among the support reaction forcesTherefore, the dynamic counterforce result has no influence of gravity;
solving the equation to obtain:
then, the magnitudes of the two click reaction forces A, B of the rotary machine base 1 are respectively:
in the experiment, the force sensor 11 is arranged in the horizontal direction of the point B, so that the horizontal component of the bearing seat dynamic counterforce can be measured in real time, and the peak value of the measured value of the force sensor 11 is the magnitude of the bearing seat dynamic counterforce:
in the experiment, the mass of the weight 9 is increased, the installation position of the weight 9 is changed, and the bearing seat movement counter force can be measured. According to weight quality and mounting position, dynamic counter force value can be calculated by the Dalangbeil principle, and experimental value and theoretical value are well matched.
The dynamic balance experiment comprises a rotary machine multiple-rotor-disc dynamic balance experiment and a rotary machine single-rotor-disc dynamic balance experiment;
1) Dynamic balance experiment of a plurality of rotor discs of a rotary machine: taking three rotor disks as an example, when the rotor disks 8 are in initial dynamic balance, it is assumed that a mass m is mounted on one of the rotor disks 8 0 The position coordinates of the weight 9 of (2) are (x) 0 ,z 0 ) According to the dynamic balance condition of the rotary machine, the installation position and the mass of the weight 9 on the rotor disk 8 are adjusted by designing an experimental scheme, so that the rotor disk can reach a dynamic balance state as much as possible, namely the dynamic counter force of the bearing seat is 0; for three rotor discs, a mass m is mounted on the first rotor disc 8 1 Weight 9 of (2), position coordinates are (x 1 ,z 1 ) The second rotor disk 8 is provided with a mass m 2 Weight 9 of (2), position coordinates are (x 2 ,z 2 ) The third rotor disk 8 has a mounting mass m 3 Weight 9 of (2), position coordinates are (x 3 ,z 3 ) The method comprises the steps of carrying out a first treatment on the surface of the When the rotor disk reaches dynamic balance, the x and z coordinates of the mass center of the system are 0, namely
m 0 x 0 +m 1 x 1 +m 2 x 2 +m 3 x 3 ＝0
m 0 z 0 +m 1 z 1 +m 2 z 2 +m 3 z 3 ＝0
And the product of inertia on the rotor disk axis, i.e. y-axis, is 0, i.e
J xy ＝0,m 0 x 0 l+m 1 x 1 l+m 2 x 2 2l+m 3 x 3 3l＝0
J zy ＝0,m 0 z 0 l+m 1 z 1 l+m 2 z 2 2l+m 3 z 3 3l＝0
Wherein, l is the distance between the rotor disk and A, B points on the rotary machine base, J xy 、J zy The product of inertia of the rotor disc system in the x and z directions to the rotor disc rotating shaft, namely the y axis;
in the experiment, the force sensor 11 is arranged in the horizontal direction of the B point of the rotary machine base 1, so that the horizontal component of the dynamic reaction force of the bearing seat can be measured in real time, and only the weight 9 has the mass m 1， m 2 And m 3 Weight 9 mounting position (x) 1 ,z 1 )，(x 2 ,z 2 ) And (x) 3 ,z 3 ) Satisfying the above relation, the measured value of the force sensor 11 is 0, i.e. the rotor disk of the rotary machine reaches dynamic balance. It should be noted that the answer to this experiment may not be unique.
Similarly, when the eccentric mass exists in the rotor disc 8, the installation position and the mass of the weight 9 on the rotor disc 8 can be adjusted according to the dynamic balance principle of the rotor disc by designing an experimental scheme, so that the rotor disc reaches an equilibrium state as far as possible, namely, the dynamic counter force of the bearing seat is 0.
2) Single rotor disc dynamic balance experiment of rotary machine: a rotor disk 8 is arranged on the rotor disk rotating shaft 5, and when the rotor disk 8 is in initial dynamic balance, a mass m is arranged at any scale position on the rotor disk 8 0 According to the dynamic balance principle of the rotor disc, the installation position and the mass of the weight 9 on the rotor disc 8 are adjusted by designing an experimental scheme, so that the rotor disc can reach a dynamic balance state as much as possible, namely the dynamic counter force of the bearing seat is 0. Similarly, when the eccentric mass exists in the rotor disc 8, the installation position and the mass of the weight 9 on the rotor disc 8 can be adjusted according to the dynamic balance principle of the rotor disc by designing an experimental scheme, so that the rotor disc reaches the balance state as much as possible, namely the dynamic counter force of the bearing seat is 0.
Rotational speed, angular velocity and angular acceleration measurement experiments of the rotating machine: the photoelectric rotary encoder 3 is connected with a rotary machine control and signal acquisition device, namely, the rotating speed, the angular speed and the angular acceleration of the rotary machine can be measured.
The method for measuring the vibration amplitude of the rotor disc rotating shaft comprises the following steps: the displacement sensor bracket 16 is arranged on the rotary machine base 1, an eddy current displacement sensor 17 is arranged on the displacement sensor bracket 16, and the eddy current displacement sensor 17 is connected into a rotary machine control and signal collector, namely, the vibration amplitude of the rotating shaft of the rotor disc can be measured.
The method for measuring the axis locus of the rotor disc rotating shaft comprises the following steps: the eddy current displacement sensor 17 is arranged on the displacement sensor bracket 16 in two directions which are vertical to each other, and the eddy current displacement sensor 17 is connected to a rotary machine control and signal collector, namely, the axis track of the rotating shaft of the rotor disc can be measured.
The invention has the following advantages:
1) The invention has strong designability, strong secondary development capability, multiple test working conditions and multiple test schemes, and can realize 7 kinds of experimental teaching contents under one set of experimental device and system: a rotary machine single rotor disc bearing seat dynamic reaction force measurement experiment, a rotary machine multiple rotor disc bearing seat dynamic reaction force measurement experiment (2 rotor discs and more), a rotary machine single rotor disc dynamic balance experiment, a rotary machine multiple rotor disc dynamic balance experiment, a rotary machine rotor disc rotating shaft vibration amplitude measurement experiment, a rotary machine rotor disc rotating shaft axis track experiment, a rotary machine rotating speed, an angular velocity, an angular acceleration measurement experiment and the like.
2) The invention simulates the actual engineering problem, develops the dynamic mechanical quantity measurement experimental device of the rotary machine, and has positive and important significance for strengthening the engineering practice capability culture of students, stimulating the understanding of students on dynamic balance concepts, and achieving the understanding and application aspects of the langbeie principle.
3) The experimental device is simple in design, high in reliability and strong in operability, the experimental result is high in matching degree with the theoretical value calculated by the Dalangbeil principle, and the experimental device is suitable for large-area student experiments and high in popularization.
Drawings
FIG. 1 is a front view of an experimental set-up of the invention.
Fig. 2 is a front view of the stationary support.
FIG. 3 is a front view of an experimental set-up with a displacement sensor holder according to the invention.
Fig. 4 is a front view of a rotor disc according to the invention, wherein fig. 4a and 4b are each one of two rotor discs.
Fig. 5 is a simplified diagram of a dynamic reaction force measurement model of a plurality of rotor disk bearing blocks of the present invention.
Fig. 6 is a simplified diagram of a single rotor disc bearing support dynamic reaction force measurement model of the present invention.
Fig. 7 is a simplified diagram of a dynamic balance experimental model of a plurality of rotor disks according to the present invention.
Detailed Description
The structural and operational principles of the present invention will be described in detail with reference to the accompanying drawings.
As shown in FIG. 1, the invention relates to a dynamic mechanical quantity measurement experimental device of a rotary machine, which comprises a rotary machine base 1, wherein a double-shaft motor 2 is fixed on the rotary machine base 1, one shaft of the double-shaft motor 2 is connected with a photoelectric rotary encoder 3 for controlling the rotating speed of the double-shaft motor 2, the other shaft of the double-shaft motor 2 is connected with a rotor disc rotating shaft 5 through a flexible coupling 4, one end of the rotating shaft 5 is fixed through a ball bearing 6 arranged on the rotary machine base 1, the other end of the rotating shaft 5 is fixed through a movable bearing 7 arranged on the rotary machine base 1, and the ball bearing 6 is adjacent to the double-shaft motor 2.
As shown in fig. 2, the force sensor 11 is installed on the left side of the movable bearing 7, the fixed block 14 is installed on the right side, the left side and the right side are respectively connected to the fixed support 13 through the left side bolt 12 and the right side bolt 15, the fixed support 13 is fixedly installed on the rotary machine base 1, and the movable bearing 7 adjusts the center position of the rotating shaft 5 through the left side bolt 12 and the right side bolt 15.
The rotor disc 8 is installed on the pivot 5 through screw 10, according to experimental requirement, the position of rotor disc 8 on pivot 5 can freely be adjusted to pivot 5 can install a plurality of rotor discs, and as shown in fig. 4a and 4b in fig. 4, the screw mountable weight 9 of disc 8 along circumference evenly arranged, as shown in fig. 1, open flexible coupling 4, remove pivot 5 to the fixed bolster end, can increase or reduce the quantity of rotor disc 8 in pivot 5, and the position of disc 8 can freely be adjusted.
As shown in fig. 3, when the axis locus and the amplitude of the rotor disc rotating shaft 5 need to be measured, a displacement sensor bracket 16 is fixed on the rotary machine base 1, one or two eddy current displacement sensors 17 are installed on the displacement sensor bracket 16, the axis locus of the rotor disc rotating shaft 5 can be measured by installing two eddy current displacement sensors 17 vertically, the vibration amplitude of the rotor disc rotating shaft 5 can be measured by installing one eddy current displacement sensor 17, and the position of the displacement sensor bracket 16 on the rotor disc rotating shaft 5 can be adjusted.
According to the experimental method of the dynamic mechanical quantity measuring experimental device of the rotary machine, when the rotor disc 8 is in initial dynamic balance, weights with arbitrary mass are arranged at different screw hole positions of the rotor disc 8, the additional dynamic counter force of the bearing seat is measured through the force sensor 11, if the rotor disc 8 has eccentric mass, the dynamic counter force of the bearing seat is measured in real time through adjusting the mass and the installation position of the weights, the eccentric mass position can be determined, when a plurality of rotor discs 8 are arranged on the rotor disc rotating shaft 5, the dynamic balance of the experimental device is achieved through designing and adjusting the mass and the position of the weights, dynamic balance experiments are carried out, the axial center track of the rotor disc rotating shaft 5 can be measured by vertically installing two eddy current sensors 17 on the displacement sensor bracket 16, and the vibration amplitude of the rotor disc rotating shaft 5 can be measured by installing one eddy current sensor 17.
The specific experimental method is as follows:
1) Dynamic reaction force measurement experiment of a plurality of rotor disc bearing seats of rotary machinery: taking a double-disc rotor as an example, when the rotor discs are in initial dynamic balance, weights 9 are arranged at any scale positions on the two rotor discs 8 as shown in fig. 1, the distance from the weights 9 to the center of the rotor disc rotating shaft 5 is e as shown in fig. 5, and the mass of the weights 9, namely the eccentric mass, is m respectively 1 And m 2 The included angle between the two eccentric masses is theta, the rotating speed of the rotary machine is omega, and the inertia forces generated by the two eccentric masses are F respectively g1 ＝m 1 eω 2 ，F g2 ＝m 2 eω 2 . According to the darebel principle, the column balance equation is as follows:
∑F x ＝F Ax +F Bx -F g2 sinθ＝0
∑F y ＝0
∑F z ＝F Az +F Bz -F g1 -F g2 cosθ-G 1 -G 2 ＝0
∑M Ax (F)＝F g1 l+F g2 2lcosθ+G 1 l+G 2 2l-F Bz 3l＝0
∑M Ay (F)＝0
SM Az (F)＝F Bx 3l-F g2 2lsinθ＝0
wherein F is x 、F y And F z Resultant force in x, y and z directions respectively, M Ax 、M Ay And M Az The resultant moment of forces in the directions of x, y and z on the rotating machine base at the point A is respectively shown as F Ax And F Bx The components of the dynamic counter force of the A, B two-point bearing seat on the rotary machine base in the x direction are respectively F Az And F Bz The components of the dynamic counter force of the A, B two-point bearing seat on the rotary machine base in the z direction are respectively G 1 For rotor disc mass and eccentric mass m 1 And, G 2 For rotor disc mass and eccentric mass m 2 A kind of electronic device. Since the dynamic reaction force is measured in the experiment, and the gravity only affects the static reaction force in the support reaction force, the dynamic reaction force result has no influence of the gravity. As shown in fig. 5, l is the distance between the rotor disks and the point of the rotor disk to the support A, B.
Solving the equation can be:
then, the two click reaction forces A, B of the rotary machine base 1 are respectively:
in the experiment, the force sensor 11 is arranged in the horizontal direction of the point B, so that the horizontal component of the bearing seat dynamic counterforce can be measured in real time, and the peak value of the measured value of the force sensor 11 is the magnitude of the bearing seat dynamic counterforce:
therefore, the bearing seat reaction force can be measured according to the weight mass and the installation position. The measurement result of the experimental device is well matched with the theoretical result of the Dalangbeil principle.
2) And (3) a single rotor disc bearing seat dynamic reaction force measurement experiment of the rotary machine: for a single rotor disc system of the rotary machine, weights 9 are arranged at any scale positions on the rotor disc 8, the dynamic counter force of a bearing seat can be measured, the mass of the weights 9 is increased in an experiment, the installation positions of the weights 9 are changed, and the change of the dynamic counter force is observed. The dynamic counter force value can be calculated according to the Dalangbeie principle, and the experimental value is well matched with the theoretical value.
As shown in fig. 6, for a single rotor disc system of a rotary machine, weights 9 are installed at any scale positions on the rotor disc 8, the center distance from the weights 9 to the rotor disc rotating shaft 5 is e, the mass of the weights 9, namely, the eccentric mass is m, the rotating speed is ω, and the generated inertia force is F g ＝m eω 2 The method comprises the steps of carrying out a first treatment on the surface of the According to the darebel principle, the column balance equation is as follows:
∑F x ＝0
∑F y ＝0
∑F z ＝F Az +F Bz -F g -G＝0
∑M Ax (F)＝F g l+Gl-F Bz 2l＝0
∑M Ay (F)＝0
∑M Az (F)＝0
wherein F is x 、F y And F z Resultant force in x, y and z directions respectively, M Ax 、M Ay And M Az Respectively the resultant moment of forces in the directions of x, y and z to the point A, F Az And F Bz The components of the dynamic reaction force of the bearing seats at the two points A, B on the rotary machine base in the z direction are respectively shown, G is the sum of the mass of the rotor disc and the eccentric mass m, and l is the distance between the rotor disc and the A, B points on the rotary machine base as shown in fig. 6; because the dynamic reaction force is measured in the experiment, and the gravity only affects the branchThe static reaction force among the seat reaction forces is not influenced by gravity in the dynamic reaction force result.
3) Dynamic balance experiment of a plurality of rotor discs of a rotary machine: a plurality of (at least 2) rotor discs 8 are mounted on the rotor disc shaft 5,
taking three rotor disks as an example, when the rotor disks 8 are in initial dynamic balance, it is assumed that a mass m is mounted on one of the rotor disks 8 0 The position coordinates of the weight 9 of (2) are (x) 0 ,z 0 ) According to the dynamic balance condition of the rotary machine, the installation position and the mass of the weight 9 on the rotor disk 8 are adjusted by designing an experimental scheme, so that the rotor disk can reach a dynamic balance state as much as possible, namely the dynamic counter force of the bearing seat is 0; for three rotor discs, a mass m is mounted on the first rotor disc 8 1 Weight 9 of (2), position coordinates are (x 1 ,z 1 ) The second rotor disk 8 is provided with a mass m 2 Weight 9 of (2), position coordinates are (x 2 ,z 2 ) The third rotor disk 8 has a mounting mass m 3 Weight 9 of (2), position coordinates are (x 3 ,z 3 ) The method comprises the steps of carrying out a first treatment on the surface of the When the rotor disk reaches dynamic balance, the x and z coordinates of the mass center of the system are 0, namely
m 0 x 0 +m 1 x 1 +m 2 x 2 +m 3 x 3 ＝0
m 0 z 0 +m 1 z 1 +m 2 z 2 +m 3 z 3 ＝0
And the product of inertia on the rotor disk axis, i.e. y-axis, is 0, i.e
J xy ＝0,m 0 x 0 l+m 1 x 1 l+m 2 x 2 2l+m 3 x 3 3l＝0
J zy ＝0,m 0 z 0 l+m 1 z 1 l+m 2 z 2 2l+m 3 z 3 3l＝0
In the formula, as shown in FIG. 7, l is the distance between the rotor disk and A, B points on the rotary machine base, J xy 、J zy The x and z directions are the products of inertia of the rotor disk system about the rotor disk axis, i.e., the y-axis.
In the experiment, the force sensor 11 is arranged in the horizontal direction of the B point of the rotary machine base 1, so that the horizontal component of the dynamic reaction force of the bearing seat can be measured in real time, and only the weight 9 has the mass m 1 ，m 2 And m 3 Weight 9 mounting position (x) 1 ,z 1 )，(x 2 ,z 2 ) And (x) 3 ,z 3 ) The above relation is satisfied, the measured value of the force sensor 11 is 0, i.e. the rotary machine rotor disc reaches dynamic balance. It should be noted that the answer to this experiment may not be unique.
Similarly, when the eccentric mass exists in the rotor disc 8, the installation position and the mass of the weight 9 on the rotor disc 8 can be adjusted according to the dynamic balance principle by designing an experimental scheme, so that the rotor disc reaches the balance state as much as possible, namely the dynamic counter force of the bearing seat is 0.
4) Single rotor disc dynamic balance experiment of rotary machine: a rotor disk 8 is arranged on the rotor disk rotating shaft 5, and when the rotor disk is in initial dynamic balance, a mass m is arranged at any scale position on the disk 0 According to the dynamic balance principle, the installation position of the weight 9 on the rotor disc 8 and the weight mass are adjusted by designing an experimental scheme, so that the rotor disc reaches an equilibrium state as far as possible, namely, the dynamic counter force of the bearing seat is close to 0. Similarly, when the eccentric mass exists in the rotor disc 8, the installation position of the weight 9 on the rotor disc 8 and the weight mass can be adjusted according to the dynamic balance principle by designing an experimental scheme, so that the rotor disc reaches the balance state as much as possible, namely the dynamic counter force of the bearing seat is close to 0.
5) Rotational speed, angular velocity and angular acceleration measurement experiments of rotating machinery: as shown in fig. 1, the photoelectric rotary encoder 3 is connected to a rotary machine control and signal collector, so that the rotation speed, the angular velocity and the angular acceleration of the rotary machine can be measured.
6) Rotor disc rotating shaft vibration amplitude measurement experiment: as shown in fig. 3, an eddy current displacement sensor 17 is mounted on the displacement sensor bracket 16, and the eddy current displacement sensor 17 is connected to a rotary machine control and signal collector to measure the vibration amplitude of the rotary machine shaft.
7) Rotor disc rotating shaft axis track experiment: as shown in fig. 3, an eddy current displacement sensor 17 is mounted on the displacement sensor bracket 16 in two directions perpendicular to each other, and the eddy current displacement sensor 17 is connected to a rotary machine control and signal collector to measure the axis track of the rotor disc rotating shaft.
Claims (9)
1. The utility model provides a rotary machine dynamic mechanical quantity measurement experimental apparatus, includes rotary machine base (1), and biax motor (2) are fixed on rotary machine base (1), and one hub connection of biax motor (2) controls photoelectric rotary encoder (3) of biax motor (2) rotational speed, and another axle of biax motor (2) is connected rotor dish pivot (5) through flexible coupling (4), rotor dish pivot (5) one end is fixed through ball bearing (6) of installing on rotary machine base (1), and the other end is fixed through movable bearing (7) of installing on rotary machine base (1), and ball bearing (6) are close to biax motor (2); the rotor discs (8) are fixedly connected to the rotor disc rotating shaft (5) through screws (10), screw holes capable of being provided with weights (9) are uniformly formed in the rotor discs (8), the flexible coupling (4) is opened, the rotor disc rotating shaft (5) is moved to one end of the movable bearing (7), namely the number of the rotor discs (8) can be increased or reduced on the rotating shaft (5), and the positions of the rotor discs (8) can be freely adjusted; the left side of the movable bearing (7) is provided with a force sensor (11), the left side of the movable bearing is connected with a fixed support (13) through a left side bolt (12), the right side of the movable bearing (7) is provided with a fixed block (14), the right side of the movable bearing is connected with the fixed support (13) through a right side bolt (15), the fixed support (13) is fixedly arranged on the rotary machine base (1), and the position of the movable bearing (7) is adjusted to be centered with the ball bearing (6) through the left side bolt (12) and the right side bolt (15); when the axis track and the amplitude of the rotor disc rotating shaft (5) need to be measured, a displacement sensor bracket (16) is fixed on the rotary machine base (1), one or two eddy current sensors (17) are vertically arranged on the displacement sensor bracket (16), the axis track of the rotor disc rotating shaft (5) can be measured by arranging the two eddy current sensors (17), the vibration amplitude of the rotor disc rotating shaft (5) can be measured by arranging the eddy current sensor (17), and the position of the displacement sensor bracket (16) on the rotor disc rotating shaft (5) can be adjusted;
one side of the force sensor (11) is arranged on the movable bearing (7), the other side of the force sensor is connected to the fixed support (13), the force sensor (11) is horizontally arranged, the influence of the gravity of the rotor disc (8) on the bearing seat moving counter force measured value is not considered, and the measured value is the horizontal component of the bearing seat moving counter force.
2. The rotary machine dynamic mechanical quantity measurement experiment device according to claim 1, wherein: the double-shaft motor (2) is connected through flexible coupling (4) to rotor disk pivot (5) one end to fixed through ball bearing (6), the other end is fixed through movable bearing (7), and after ball bearing (6) position determination, movable bearing (7) can furthest guarantee that rotor disk pivot (5) aligns with the center of double-shaft motor (2) axle, and flexible coupling (4) can guarantee the flexible connection of rotor disk pivot (5) and double-shaft motor (2) axle, in order to ensure experimental result reliability.
3. The rotary machine dynamic mechanical quantity measurement experiment device according to claim 1, wherein: the rotor disc (8) is evenly provided with screw holes capable of being provided with weights (9) along the circumferential direction, so that weight quality and installation positions can be automatically designed according to different experimental requirements.
4. A method of testing a rotary machine dynamic mechanical quantity measurement test apparatus according to any one of claims 1 to 3, characterized by: when the rotor disc (8) is in initial dynamic balance, any mass weight is installed at different screw hole positions of the rotor disc (8), the bearing seat additional dynamic counterforce is measured through the force sensor (11), if eccentric mass exists in the rotor disc (8), the bearing seat dynamic counterforce can be measured in real time through adjusting the mass and the installation position of the weight by the force sensor (11), the eccentric mass position can be determined, when a plurality of rotor discs (8) are installed on the rotor disc rotating shaft (5), the experimental device achieves dynamic balance through design adjustment of the mass and the position of the weight, the two eddy current sensors (17) are vertically installed on the displacement sensor support (16), namely the axis track of the rotor disc rotating shaft (5) can be measured, and the vibration amplitude of the rotor disc rotating shaft (5) can be measured by installing one eddy current sensor (17).
5. The method of claim 4, wherein: the measuring bearing seat dynamic counterforce comprises a rotating machine multiple-rotor disc bearing seat dynamic counterforce measuring experiment and a rotating machine single-rotor disc bearing seat dynamic counterforce measuring experiment;
1) Dynamic reaction force measurement experiment of a plurality of rotor disc bearing seats of rotary machinery: for the two rotor disks, when the rotor disks are in initial dynamic balance, weights (9) are arranged at any scale positions on the two rotor disks (8), the distance from the weights (9) to the rotor disk rotating shaft (5) is e, and the mass of the weights (9), namely the eccentric mass, is m respectively 1 And m 2 The included angle between the two eccentric masses is theta, the rotating speed of the rotary machine is omega, and the inertia forces generated by the two eccentric masses are F respectively g1 ＝m 1 eω 2 ，F g2 ＝m 2 eω 2 The method comprises the steps of carrying out a first treatment on the surface of the According to the darebel principle, the column balance equation is as follows:
ΣF x ＝F Ax +F Bx -F g2 sinθ＝0
ΣF y ＝0
ΣF z ＝F Az +F Bz -F g1 -F g2 cosθ-G 1 -G 2 ＝0
ΣM Ax (F)＝F g1 l+F g2 2l cosθ+G 1 l+G 2 2l-F Bz 3l＝0
ΣM Ay (F)＝0
ΣM Az (F)＝F Bx 3l-F g2 2l sinθ＝0
wherein F is x 、F y And F z Resultant force in x, y and z directions respectively, M Ax 、M Ay And M Az The resultant moment of forces in the directions of x, y and z on the rotating machine base at the point A is respectively shown as F Ax And F Bx Two-point shaft of A, B on rotary machine baseThe bearing moving counter-force being in the x-direction component, F Az And F Bz The components of the dynamic counter force of the A, B two-point bearing seat on the rotary machine base in the z direction are respectively G 1 For rotor disc mass and eccentric mass m 1 And, G 2 For rotor disc mass and eccentric mass m 2 And l is the distance between the rotor disks and the A, B points on the rotor disks and the rotary machine base; because the dynamic counter force is measured in the experiment, and gravity only affects the static counter force in the counter force of the support, the dynamic counter force result has no influence of gravity;
solving the equation to obtain:
then, the magnitudes of the two click reaction forces A, B of the rotary machine base (1) are respectively:
in the experiment, the force sensor (11) is arranged in the horizontal direction of the point B, so that the horizontal component of the bearing seat dynamic counterforce can be measured in real time, and the peak value of the measured value of the force sensor (11), namely the magnitude of the bearing seat dynamic counterforce:
therefore, the bearing seat movement reaction force can be measured according to the mass and the installation position of the weight (9);
2) And (3) a single rotor disc bearing seat dynamic reaction force measurement experiment of the rotary machine: for a single rotor disc system of a rotary machine, weights (9) are arranged at any scale positions on the rotor disc (8), the distance from each weight (9) to a rotor disc rotating shaft (5) is e, the mass of each weight (9), namely the eccentric mass, is m, the rotating speed is omega, and the generated inertia force is F g ＝m eω 2 The method comprises the steps of carrying out a first treatment on the surface of the According to the darebel principle, the column balance equation is as follows:
ΣF x ＝0
ΣF y ＝0
ΣF z ＝F Az +F Bz -F g -G＝0
ΣM Ax (F)＝F g l+Gl-F Bz 2l＝0
ΣM Ay (F)＝0
ΣM Az (F)＝0
wherein F is x 、F y And F z Resultant force in x, y and z directions respectively, M Ax 、M Ay And M Az Respectively the resultant moment of forces in the directions of x, y and z to the point A, F Az And F Bz The component of the dynamic reaction force of the bearing seats at A, B points on the rotary machine base in the z direction is respectively represented by G, wherein G is the sum of the mass of the rotor disc and the eccentric mass m, and l is the distance between the rotor disc and A, B points on the rotary machine base; because the dynamic counter force is measured in the experiment, and gravity only affects the static counter force in the counter force of the support, the dynamic counter force result has no influence of gravity; solving the equation to obtain:
then, the magnitudes of the two click reaction forces A, B of the rotary machine base (1) are respectively:
in the experiment, the force sensor (11) is arranged in the horizontal direction of the point B, so that the horizontal component of the bearing seat dynamic counterforce can be measured in real time, and the peak value of the measured value of the force sensor (11), namely the magnitude of the bearing seat dynamic counterforce:
in the experiment, the mass of the weight (9) is increased, the installation position of the weight (9) is changed, and the bearing seat moving counter force can be measured.
6. The method of claim 4, wherein: the experiment for achieving dynamic balance of the experimental device comprises a rotary machine multiple-rotor-disc dynamic balance experiment and a rotary machine single-rotor-disc dynamic balance experiment;
1) Dynamic balance experiment of a plurality of rotor discs of a rotary machine: for three rotor disks, when the rotor disks (8) are in initial dynamic balance, it is assumed that a mass m is mounted on one of the rotor disks (8) 0 Weight (9) of (2) and the position coordinates are (x 0 ,z 0 ) According to the dynamic balance condition of the rotary machine, the installation position and the mass of the weight (9) on the rotor disc (8) are adjusted by designing an experimental scheme, so that the rotor disc can reach a dynamic balance state as much as possible, namely the dynamic counter force of the bearing seat is 0; for three rotor disks, a mass m is mounted on the first rotor disk (8) 1 Weight (9) of (2) and the position coordinates are (x 1 ,z 1 ) The second rotor disk (8) is provided with a mass m 2 Weight (9) of (2) and the position coordinates are (x 2 ,z 2 ) The third rotor disk (8) has a mounting mass of m 3 Weight (9) of (2) and the position coordinates are (x 3 ,z 3 ) The method comprises the steps of carrying out a first treatment on the surface of the When the rotor disk reaches dynamic balanceThe x and z coordinates of the mass center of the system are 0, namely
m 0 x 0 +m 1 x 1 +m 2 x 2 +m 3 x 3 ＝0
m 0 z 0 +m 1 z 1 +m 2 z 2 +m 3 z 3 ＝0
And the product of inertia on the rotor disk axis, i.e. y-axis, is 0, i.e
J xy ＝0,m 0 x 0 l+m 1 x 1 l+m 2 x 2 2l+m 3 x 3 3l＝0
J zy ＝0,m 0 z 0 l+m 1 z 1 l+m 2 z 2 2l+m 3 z 3 3l＝0
Wherein, l is the distance between the rotor disk and A, B points on the rotary machine base, J xy 、J zy The x and z directions are the inertia products of the rotor disc system on the rotor disc rotating shaft, namely the y axis;
in the experiment, a force sensor (11) is arranged in the horizontal direction of the B point of a rotary machine base (1), so that the horizontal component of the dynamic reaction force of a bearing seat can be measured in real time, and only the mass m of a weight (9) 1 ，m 2 ，m 3 And the weight (9) mounting position (x 1 ,z 1 )，(x 2 ,z 2 )，(x 3 ,z 3 ) When the relation is satisfied, the measured value of the force sensor (11) is 0, namely the rotor disc of the rotary machine reaches dynamic balance;
when the eccentric mass exists in the rotor disc (8), the installation position and the mass of the weight (9) on the rotor disc (8) can be adjusted according to the dynamic balance principle of the rotor disc by designing an experimental scheme, so that the rotor disc reaches a balanced state as much as possible, namely the dynamic counter force of the bearing seat is 0;
2) Single rotor disc dynamic balance experiment of rotary machine: a rotor disc (8) is arranged on the rotor disc rotating shaft (5), and when the rotor disc (8) is in initial dynamic balance, a mass m is arranged at any scale position on the rotor disc (8) 0 According to dynamic balance principle, by designing experimental scheme, adjusting weightThe code (9) is arranged on the rotor disc (8) in position and with mass, so that the rotor disc can reach a dynamic balance state as far as possible, namely, the dynamic counter force of the bearing seat is 0; when the rotor disc (8) has eccentric mass, the installation position and the mass of the weight (9) on the rotor disc (8) can be adjusted according to the dynamic balance principle by designing an experimental scheme, so that the rotor disc can reach an equilibrium state as much as possible, namely, the dynamic counter force of the bearing seat is 0.
7. The experimental method according to claim 4, the rotational speed, angular velocity and angular acceleration measurement experiment of the rotary machine: the photoelectric rotary encoder (3) is connected with a rotary machine control and signal acquisition device, namely, the rotating speed, the angular speed and the angular acceleration of the rotary machine can be measured.
8. The experimental method according to claim 4, wherein the method for measuring the vibration amplitude of the rotor disc shaft comprises the following steps: a displacement sensor bracket (16) is arranged on a rotary machine base (1), an eddy current sensor (17) is arranged on the displacement sensor bracket (16), and the eddy current sensor (17) is connected into a rotary machine control and signal collector, namely, the vibration amplitude of a rotor disc rotating shaft can be measured.
9. The experimental method according to claim 4, wherein the method for measuring the axial locus of the rotor disc shaft comprises the following steps: and (3) respectively mounting an eddy current sensor (17) in two directions which are vertical to each other on the displacement sensor bracket (16), and connecting the eddy current sensor (17) into a rotary machine control and signal collector, namely, measuring the axis track of the rotating shaft of the rotor disc.
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