CN115266086A - Fatigue test device and fatigue test method for coupler - Google Patents
Fatigue test device and fatigue test method for coupler Download PDFInfo
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- CN115266086A CN115266086A CN202210839978.1A CN202210839978A CN115266086A CN 115266086 A CN115266086 A CN 115266086A CN 202210839978 A CN202210839978 A CN 202210839978A CN 115266086 A CN115266086 A CN 115266086A
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Abstract
The application provides a fatigue test device and fatigue test method for shaft coupling, and this fatigue test device includes: the system comprises a loading system, a connecting system and a data measuring system; the radial angular loading mechanism is used for applying radial and angular loads to the elastic coupling test piece, and the axial loading mechanism is used for applying axial loads to the elastic coupling test piece; the data measurement system is used for measuring the torque force on the transmission shaft assembly, the radial force and the angle on the radial angular loading mechanism, the axial force of the axial loading mechanism and the displacement of the elastic coupling test piece. The fatigue test device and the fatigue test method have the advantages of being high in safety in the test process, accurate in fatigue performance evaluation, suitable for complex multidirectional coupling working conditions, flexible in adjustment and accurate in control system.
Description
Technical Field
The application relates to the technical field of elastic coupling fatigue testing, in particular to a fatigue testing device and a fatigue testing method for a coupling.
Background
The coupling is also called coupling, is a key device for connecting a driving shaft and a driven shaft in a transmission system and used for transmitting power, and is mainly used for firmly connecting the driving shaft and the driven shaft in different mechanisms to rotate together. The couplings can be divided into a rigid coupling and a flexible coupling, wherein the flexible coupling can be divided into an elastic element-free flexible coupling and an elastic element-free flexible coupling, the elastic element-free flexible coupling only has the capability of compensating relative displacement of two axes but cannot buffer and damp vibration, and the common couplings comprise a slider coupling, a tooth coupling, a universal coupling, a chain coupling and the like; the flexible coupling with the elastic element has the capacity of compensating relative displacement of two axes and also has the functions of buffering and damping due to the elastic element, and common elastic sleeve pin couplings, elastic pin couplings, quincunx couplings, tire couplings, serpentine spring couplings, reed couplings and the like. However, flexible couplings with elastic elements tend to have radial, angular and axial deviations during installation or long-term use, and running in an out-of-center condition for a long time is prone to fatigue failure of the coupling elements.
At present, some fault simulation test devices related to the coupler are designed for the fatigue damage problem caused by the installation error of the coupler in the prior art, for example, an experiment device for simulating the radial error of the coupler, an experiment device for simulating the angular error of the coupler and the like, the radial, angular and axial deviations are obtained through the fault simulation test devices, the installation error of the coupler is simulated, and therefore the fatigue life of the coupler is evaluated. However, in practical engineering applications, the coupling is generally connected with a rotor, a bearing and the like to form a set of transmission system, and an elastic vibration isolation device is arranged at a system fixing position to enable the transmission system to be in a flexible support, so that dynamic misalignment can occur due to the influence of other moving parts when the coupling operates, and the dynamic misalignment can cause an elastic element of the coupling to vibrate due to external excitation and be coupled with vibration caused by static misalignment. For example, in a mission profile of large equipment such as an aircraft and a ship, because the output power of an engine changes with different working condition requirements, the vibration frequency caused by dynamic misalignment of a transmission system in a certain period may be closer to the natural frequency of a coupler, so that the frequency-doubled vibration of the coupler is more prominent, and in combination with the full life cycle of the system, the vibration stress generated by the resonance may cause accumulated damage to elastic elements in the coupler, and finally may cause vibration fatigue damage.
Therefore, in order to more fully evaluate the fatigue life of the coupling, the vibration caused by the dynamic misalignment leads to the fatigue failure of the elastic element in the coupling, which is not negligible, and thus it is necessary to design a fatigue testing device for the coupling.
Disclosure of Invention
The application provides a fatigue test device and a fatigue test method for a coupler, so as to evaluate the fatigue life of the coupler more comprehensively.
The present application provides in a first aspect a fatigue test device for a coupling, the fatigue test device comprising: the system comprises a loading system, a connecting system and a data measuring system;
the loading system comprises a driving variable frequency motor, a radial angular loading mechanism, an axial loading mechanism and a load variable frequency motor, wherein the horizontal direction of the radial angular loading mechanism is vertical to the horizontal direction of the axial loading mechanism under the condition of no load, the radial angular loading mechanism is used for applying radial and angular loads to an elastic coupling test piece, and the axial loading mechanism is used for applying axial loads to the elastic coupling test piece;
the connecting system comprises a first slide bar cross universal coupling, a second slide bar cross universal coupling and a transmission shaft assembly, wherein the first slide bar cross universal coupling is respectively connected with the driving variable frequency motor and the elastic coupling test piece through the transmission shaft assembly, and the second slide bar cross universal coupling is respectively connected with the loading variable frequency motor and the elastic coupling test piece through the transmission shaft assembly;
the data measurement system is used for measuring the torque force on the transmission shaft assembly, the radial force and the angle on the radial angular loading mechanism, the axial force of the axial loading mechanism and the displacement of the elastic coupling test piece.
Preferably, the radial angular loading mechanism comprises a first loading device, a second loading device, a first joint bearing, a radial loading bearing seat, a sliding block, a guide rail chassis and a turntable bearing;
the first loading device and the second loading device have the same structure and are both composed of a first electric cylinder and a first electric cylinder base, and the first electric cylinder base is used for supporting and fixing the first electric cylinder;
the radial loading bearing seats and the first joint bearings are arranged in two groups, the radial loading bearing seats in each group are connected with the first joint bearings on one side and the same side, the two first joint bearings are parallel to each other under the condition of no load, the axis of the two first joint bearings is perpendicular to a transmission shaft of the radial loading bearing seats, the first loading device is connected with one first joint bearing, and the second loading device is connected with the other first joint bearing;
the two groups of sliding blocks are arranged, each sliding block is connected with the radial loading bearing seat at the corresponding position, and the sliding blocks slide along the guide rail on the upper surface of the guide rail chassis under the action of force; the turntable bearing is arranged on the lower surface of the guide rail chassis and is used for the guide rail chassis to rotate under the action of force.
Preferably, the axial loading mechanism comprises a third loading device, a fourth loading device, a second joint bearing, an axial loading bearing seat, a bearing seat support frame, a linear motion bearing assembly and a fixed bearing seat assembly, and the connecting system comprises a third transmission shaft;
the third loading device and the fourth loading device have the same structure and are both composed of a second electric cylinder and a second electric cylinder base, and the second electric cylinder base is used for supporting and fixing the second electric cylinder;
the two sides of the axial loading bearing seat are respectively connected with one second joint bearing, the axes of the two second joint bearings and the linear motion bearing assembly are parallel to each other under the condition of no load, the third loading device is connected with one second joint bearing, and the fourth loading device is connected with the other second joint bearing;
the two bearing seat supporting frames are respectively positioned on two sides of the axial loading bearing seat and used for reducing the friction force of the axial loading bearing seat during axial movement;
the third transmission shaft is radially and axially constrained through the fixed bearing seat assembly, and the fixed bearing seat assembly is used for balancing radial force and moment;
the linear motion bearing assembly is arranged on the axial loading bearing seat and is connected with the fixed support bearing seat assembly through a third transmission shaft, and the linear motion bearing assembly is used for releasing the axial freedom degree of the axial loading mechanism and enabling the second slide bar cross universal coupling not to be influenced by axial force.
Preferably, the data measurement system comprises a first torsion sensor, a second torsion sensor, a first radial force sensor, a second radial force sensor, a first axial force sensor, a second axial force sensor, an eddy current displacement sensor, and an angle sensor;
the first torsion sensor is arranged on the first slide bar cross universal coupling, the second torsion sensor is arranged on the second slide bar cross universal coupling, the first radial force sensor is arranged on the first loading device, the second radial force sensor is arranged on the second loading device, the first axial force sensor is arranged on the third loading device, the second axial force sensor is arranged on the fourth loading device, the eddy current displacement sensor is arranged at the clamping position of an elastic coupling test piece, and the angle sensor is arranged on the guide rail chassis.
Preferably, the first electric cylinder base is connected with the first electric cylinder through a self-aligning roller bearing;
the actuating ends of the two first electric cylinders respectively fix the first radial force sensor and the second radial force sensor with the first joint bearing matched with each other by using a transition bolt, and the head part of the first joint bearing is hinged to the loading end of the radial loading bearing seat;
the radial loading bearing seat is internally provided with a double-row angular contact ball bearing and a first transmission shaft connected with the double-row angular contact ball bearing, the sliding block is arranged in a groove in the outer bottom surface, and the sliding block is arranged on a track of the guide rail chassis.
Preferably, the linear motion bearing assembly comprises a guide rail mounting flange, a guide rail support flange, a guide rail shaft, a linear motion ball bearing and a snap spring;
the guide rail shaft and the linear motion ball bearing are respectively fixed between the guide rail mounting flange and the guide rail support flange by using the snap springs;
the bearing seat support frame main body is H-shaped, and a cross beam of the H-shaped main body is provided with a rolling linear needle roller guide rail support.
Preferably, the second electric cylinder base is connected with the second electric cylinder through a self-aligning roller bearing;
the first axial force sensor and the second axial force sensor are respectively fixed with the matched second joint bearing by the action ends of the two second electric cylinders through transition bolts, and the head parts of the second joint bearings are hinged to the loading ends of the axial loading bearing seats;
a double-row angular contact ball bearing and a second transmission shaft connected with the double-row angular contact ball bearing are arranged in the axial loading bearing seat, and the second transmission shaft and the guide rail shaft mounting flange are fixed through bolts and splines;
and the third transmission shaft is used for connecting the second slide bar cross universal coupling, the fixed bearing seat assembly and the guide rail support flange.
Preferably, the fatigue testing device further comprises a supporting system;
the supporting system comprises a chute test platform used for adjusting and fixing the systems;
the fixed support bearing seat assembly mainly comprises a bearing seat and a double-row deep groove ball bearing, wherein the double-row deep groove ball bearing is connected with the third transmission shaft, the bottom of the bearing seat is fixedly supported on the chute test platform, and force and torque are balanced through the fixed support end of the bearing seat.
In a second aspect of the present application, a fatigue test method for a coupling is applied to any one of the above fatigue test apparatuses for a coupling, and the fatigue test method mainly includes the following steps:
s1, clamping a test piece: clamping an elastic coupling test piece in the connecting system, respectively connecting the elastic coupling test piece with a driving variable frequency motor and a load variable frequency motor through a first slide bar cross universal coupling, a second slide bar cross universal coupling and a transmission shaft assembly, and detecting the coaxiality of the connecting position in the device by using a lever dial indicator;
s2, formal test: resetting the torque force, the radial force and the angle of a sensor in the data measurement system, starting and driving the variable frequency motor to a test rated rotating speed, and carrying out balance resetting on the torque force value again; controlling a load variable frequency motor to enable the torque to reach a test set value through a feedback torque signal, acquiring various data by an acquisition and measurement system after a transmission system is stable, and selecting an external excitation state under a corresponding working condition to control each loading device according to vibration test data or a simulation result of the transmission system on a task section;
s3, signal acquisition: the method comprises the steps that a collecting and measuring system collects displacement, torsion, radial force and angle data of an elastic coupling test piece, time domain signals of the displacement data are subjected to Fourier transform (FFT) to extract characteristic values, and frequency change is detected;
and S4, finishing the test: stopping the experiment when the test is carried out for a specified number of cycles and the test piece of the elastic coupling is not damaged; or in the normal test process, when the natural frequency of the elastic coupling test piece is reduced by 0.5-1.5%, the fatigue crack is considered to be generated, and the test is stopped; or the crack of the elastic coupling test piece is not generated at the dangerous part, the elastic coupling test piece is scrapped, and the experiment is stopped.
Preferably, the selecting the external excitation state under the corresponding working condition to control each loading device includes the following steps:
a) Working condition of elastic coupling radial vibration fatigue test
The method comprises the following steps that a radial angular loading mechanism is utilized to apply radial force to an elastic coupling test piece, the radial force needs to meet the condition that the moment at the elastic coupling test piece is zero when the radial force is coordinately loaded in a control system, and the calculation formula is as follows:
radial force equation: fr=F12-F11
The moment equation: f11(l11+l12)=F12l12
Substituting the radial force equation into the moment equation
F11(l11+l12)-(Fr+F11)l12=0
Can obtain the product
In the above formula, A is a constant, wherein F11、F12Applying two radial forces, iota, respectively, to the radial angular loading mechanism11、ι12The distances from the two radial forces to the elastic coupling test piece are respectively;
the radial force F is input in the loading control system by the above-mentioned relationrThe coordination loading of the radial angular loading mechanism can be realized, so that the elastic coupling test piece is only excited by radial force, and the dynamic application of the radial load of the elastic coupling can be realized by utilizing a load spectrum;
b) Working condition of angular vibration fatigue test of elastic coupling
Angular fatigue refers to the fact that an elastic element in an elastic coupling test piece is subjected to alternating moment (M) around a Z axisZ) The fatigue performance under influence can be realized by utilizing the radial direction to ensure that the elastic coupling test piece is only influenced by angular excitationThe angular loading mechanism applies loads with equal magnitude and opposite directions to the elastic coupling test piece, and the calculation formula is as follows:
radial force equation: f11＝F12
The moment equation: mZ＝F11(l11+l12)-F12l12
Can obtain the product
MZ＝F11l11
In the above formula F11、F12For applying two radial forces, i, in radial angular loading mechanisms, respectively11、ι12The horizontal distances from the two radial forces to the elastic coupling test piece are respectively, no additional shearing force is generated on the elastic coupling test piece in the process of applying a pair of force couples, and the dynamic application of the angular fatigue load of the elastic coupling test piece can be realized by coordinately controlling the load and the direction of the two radial forces;
c) Working condition of elastic coupling axial vibration fatigue test
The axial loading mechanism is used for applying loads with equal magnitude and same direction, and the calculation formula is as follows:
axial force equation: fx＝F21+F22
The moment equation: f21l21＝F22l22
Wherein
F21＝F22，l21＝l22
In the above formula F21、F22For applying two axial forces, iota, respectively, in the axial loading mechanism21、ι22The vertical distances from the two axial forces to the central axis of the elastic coupling test piece are respectively.
According to the technical scheme, the fatigue test device and the fatigue test method for the coupler have the following beneficial effects:
(1) In the fatigue testing device, a self-balancing mechanism is formed by the interaction of components in the loading process of each working condition, and meanwhile, the driving and loading device is connected into the testing system in a flexible connection mode, so that the driving and loading device only transmits torque and is not influenced by other acting forces to generate overload, and the safety of the testing process is ensured;
(2) Compared with a mode of directly changing the horizontal position or angle of the driving motor, the invention adopts a two-point coordination loading mode for the external load borne by the tested piece, so that the radial force and the torque can be independently acted on the tested piece, and the fatigue performance evaluation of the tested piece under the influence of single stress can be better carried out;
(3) The fatigue test device can exert the external excitation effect in three directions on the elastic coupling, realizes the simulation of the dynamic out-of-center vibration state of the transmission system under the elastic support in engineering application, and can carry out the multi-axis vibration fatigue performance test research under the conditions of same phase, same proportion or different phases, different proportions and the like by the superposition of excitation loads in all directions by combining the characteristic that each mechanism of the device can be loaded independently under the complex multi-direction coupling working condition;
(4) By utilizing the characteristics of flexible adjustment and accurate control system of the fatigue test device, radial, angular or axial installation errors can be reserved in the process of installing a tested piece, so that the invention can also be used as a test system for simulating coupler faults, and is applied to the research of a fault monitoring system by acquiring typical coupler fault signals.
Drawings
In order to more clearly illustrate the embodiments of the present application or the technical solutions in the prior art, the drawings needed to be used in the embodiments will be briefly described below, and it is obvious that the drawings in the following description are only some embodiments of the present application, and it is obvious for those skilled in the art to obtain other drawings without creative efforts.
Fig. 1 is a schematic perspective view of a fatigue testing apparatus for a coupling according to the present application;
FIG. 2 is a schematic cross-sectional view of the radial angular loading mechanism, axial loading mechanism, and a portion of the driveshaft assembly of the present application;
FIG. 3 is a schematic view of a radial angle loading mechanism of the present application;
FIG. 4 is a schematic structural view of an axial loading mechanism of the present application;
FIG. 5 is a schematic structural view of a linear motion bearing assembly of the present application;
FIG. 6 is a schematic structural view of a bearing housing support of the present application;
FIG. 7 is a schematic view of the present application illustrating load transfer under a radially loaded condition;
FIG. 8 is a schematic view of load transfer under an angular loading condition according to the present application
FIG. 9 is a schematic view of load transfer in an axial loading condition according to the present application.
Detailed Description
The first aspect of the present application provides a fatigue testing device for a coupling, the structure of the fatigue testing device can refer to the schematic diagram shown in fig. 1, and the specific structure thereof includes: loading system 100, connection system 200, and data measurement system 400; the loading system 100 comprises a driving variable frequency motor 101, a radial angular loading mechanism 110, an axial loading mechanism 120 and a load variable frequency motor 102, wherein the horizontal direction of the radial angular loading mechanism 110 is vertical to the horizontal direction of the axial loading mechanism 120 under the condition of no load, the radial angular loading mechanism 110 is used for applying radial and angular loads to an elastic coupling test piece 300, and the axial loading mechanism 120 is used for applying axial loads to the elastic coupling test piece 300; the connecting system 200 comprises a first slide bar cross universal joint 201, a second slide bar cross universal joint 202 and a transmission shaft assembly, wherein the first slide bar cross universal joint 201 is respectively connected with the driving variable frequency motor 101 and the elastic coupling test piece 300 through the transmission shaft assembly, and the second slide bar cross universal joint 202 is respectively connected with the loading variable frequency motor 102 and the elastic coupling test piece 300 through the transmission shaft assembly; the data measurement system 400 is used to measure the torque on the drive shaft assembly, the radial force and angle on the radial angular loading mechanism 110, the axial force of the axial loading mechanism 120, and the displacement of the resilient coupling test piece 300.
After the radial angular loading mechanism 110, the axial loading mechanism 120 and a part of the transmission shaft assembly are matched, reference is made to the schematic diagram shown in fig. 2, wherein the specific structure of the radial angular loading mechanism 110 can refer to the schematic diagram shown in fig. 3, and the specific structure includes a first loading device, a second loading device, a first joint bearing 113, a radial loading bearing seat 114, a slider 115, a guide rail chassis 116 and a turntable bearing 117; the first loading device and the second loading device have the same structure and are both composed of a first electric cylinder 111 and a first electric cylinder base 112, and the first electric cylinder base 112 is used for supporting and fixing the first electric cylinder 111; the sliding blocks 115 are connected with the radial loading bearing seats 114, two groups of sliding blocks 115 are arranged, each sliding block 115 is connected with the radial loading bearing seat 114 at the corresponding position, and the sliding blocks 115 slide along the guide rail on the upper surface of the guide rail chassis 116 under the action of force; the turntable bearing 117 is mounted on the lower surface of the guide rail chassis 116, and is used for the guide rail chassis 116 to rotate under the action of force; the radial loading bearing seat 114 with first joint bearing 113 is provided with two sets ofly, is in every group radial loading bearing seat 114 be unilateral homonymy with first joint bearing 113 connects, promptly radial loading mechanism in the radial angular loading mechanism 110 includes two radial loading bearing seats 114, every loading bearing seat 114 all is the joint bearing and the electric jar that correspond at unilateral homonymy connection, two under the unloaded condition during the use first joint bearing 113 is parallel to each other and the axis is perpendicular with the transmission shaft of radial loading bearing seat 114, first loading device with one of them first joint bearing 113 connects, the second loading device with another first joint bearing 113 connects. The first electric cylinder base 112 is connected with the first electric cylinder 111 through a self-aligning roller bearing; the first radial force sensor 403 and the second radial force sensor 404 are respectively fixed with the first joint bearing 113 matched with each other by using a transition bolt at the actuating ends of the two first electric cylinders 111, and the head of the first joint bearing 113 is hinged to the loading end of the radial loading bearing seat 114; the radial loading bearing seat 114 is internally provided with a double-row angular contact ball bearing and a first transmission shaft 211 connected with the double-row angular contact ball bearing, the sliding block 115 is arranged in a groove on the outer bottom surface, and the sliding block 115 is arranged on a track of the guide rail chassis 116.
The specific working principle of the radial angular loading mechanism 110 is as follows: the electric cylinder assemblies in the radial angular loading mechanism 110 are two sets of electric cylinder assemblies with the same model and connection mode, the radial and angular degrees of freedom are released through the combination form of the sliding block 115, the guide rail chassis 116 and the turntable bearing 117, when the two electric cylinders simultaneously apply forces with equal magnitude and opposite directions, the two sets of loading devices can slightly rotate relative to the midpoint of the connecting line of the two sets of loading devices, and then the two sets of loading devices can be regarded as a pair of force couples acting on the midpoint of the connecting line of the loading devices, so that the elastic coupling test piece 300 is only influenced by angular moment, when the two electric cylinders respectively apply a set of force, the moment relative to the connection position of the elastic coupling test piece 300 is zero, and when the received radial force is the difference of the loading values of the two electric cylinders, the elastic coupling test piece 300 can be regarded as only acted by the radial force.
The structure of the axial loading mechanism 120 can refer to the schematic diagram shown in fig. 4, and the specific structure thereof includes a third loading device, a fourth loading device, a second knuckle bearing 123, an axial loading bearing seat 124, a bearing seat support frame 125, a linear motion bearing assembly 126 and a fixed bearing seat assembly (220), the connecting system (200) includes a third transmission shaft (213); the third loading device and the fourth loading device have the same structure and are both composed of a second electric cylinder 121 and a second electric cylinder base 122, and the second electric cylinder base 122 is used for supporting and fixing the second electric cylinder 121; one second knuckle bearing 123 is connected to each side of the axial loading bearing seat 124, the axes of the two second knuckle bearings 123 and the linear motion bearing assembly 126 are parallel to each other under the condition of no load, the third loading device is connected with one second knuckle bearing 123, and the fourth loading device is connected with the other second knuckle bearing 123; the two bearing seat support frames 125 are respectively positioned at two sides of the axial loading bearing seat 124 and used for reducing the friction force of the axial loading bearing seat 124 during axial movement; the third transmission shaft 213 is constrained axially and radially by the fixed bearing block assembly 220, and the fixed bearing block assembly 220 is used for balancing radial force and moment; the linear motion bearing assembly 126 is mounted on the axial loading bearing seat 124, the linear motion bearing assembly 126 is connected with the fixed support bearing seat assembly 220 through the third transmission shaft 213, and the linear motion bearing assembly 126 is used for releasing the axial loading bearing seat
Specifically, the structure of the linear motion bearing assembly 126 can be seen in the schematic diagram shown in fig. 5, and specifically includes a rail mounting flange 1261, a rail support flange 1262, a rail shaft 1263, a linear motion ball bearing 1264, and a clamp spring 1265; the rail shaft 1263 and the linear motion ball bearing 1264 are secured between the rail mounting flange 1261 and the rail mount flange 1262, respectively, using the clamp spring 1265; the bearing seat support frame 125 can refer to the schematic diagram shown in fig. 6, the main body of the bearing seat support frame is H-shaped, and a rolling linear needle roller guide support 1251 is arranged on a cross beam of the H-shaped main body. In addition, the second electric cylinder base 122 is connected with the second electric cylinder 121 through a self-aligning roller bearing; the actuating ends of the two second electric cylinders 121 respectively fix a first axial force sensor 405 and a second axial force sensor 406 to the second joint bearings 123 which are matched with each other by using transition bolts, and the heads of the second joint bearings 123 are hinged to the loading ends of the axial loading bearing seats 124; a double-row angular contact ball bearing and a second transmission shaft 212 connected with the double-row angular contact ball bearing are arranged in the axial loading bearing seat 124, and the second transmission shaft 212 and the guide rail shaft mounting flange 1261 are fixed through bolts and splines; the third transmission shaft 213 is used to connect the second slide bar cross-point universal joint 202, the solid support bearing block assembly 220, and the rail mount flange 1262.
The electric cylinder components in the axial loading mechanism 120 are two sets of electric cylinder components with the same model and connection mode, the application of the axial load to the elastic coupling test piece 300 is realized through the synchronous loading of the two electric cylinders, and meanwhile, due to the use of the linear motion bearing component 126, the fixed bearing seat component 220 at the rear section of the mechanism and the second slide bar cross universal coupling 202 are not influenced by the axial force.
Further illustrating that the data measurement system comprises a first torsion sensor 401, a second torsion sensor 402, a first radial force sensor 403, a second radial force sensor 404, a first axial force sensor 405, a second axial force sensor 406, an eddy current displacement sensor 407 and an angle sensor 408; the first torsion sensor 401 is disposed on the first sliding rod cross universal joint 201, the second torsion sensor 402 is disposed on the second sliding rod cross universal joint 202, the first radial force sensor 403 is disposed on the first loading device, the second radial force sensor 404 is disposed on the second loading device, the first axial force sensor 405 is disposed on the third loading device, the second axial force sensor 406 is disposed on the fourth loading device, the eddy current displacement sensor 407 is disposed at the loading position of the elastic coupling test piece 300, and the angle sensor 408 is disposed on the guide rail chassis 116.
The fatigue testing apparatus further comprises a support system 500; the support system 500 includes a chute test platform 501 for adjustment and fixation of the systems. When the radial angular loading mechanism 110 applies a radial force to the elastic coupling test piece 300, the radial force is transmitted to the rear section of the mechanism through the linear motion bearing assembly 126, in order to ensure that the test device does not have large deformation and deflection to influence the test result, a group of fixing assemblies are required to be installed in the device to radially and axially restrain the third transmission shaft 213, so that a group of fixed bearing seat assemblies 220 are arranged at the rear section of the mechanism to balance the radial force and the moment, the fixed bearing seat assemblies 220 mainly comprise a bearing seat 221 and a double-row deep groove ball bearing 222, wherein the double-row deep groove ball bearing 222 is connected with the third transmission shaft 213, the bottom of the bearing seat 221 is fixedly supported on the chute test platform 501, and the force and the moment are balanced through the fixed supporting end of the bearing seat 221.
The equilibrium relationship between force and moment is as follows:
(1) The load diagram for the radial loading condition can refer to the diagram shown in fig. 7, and the balance equation of the device under the condition is as follows:
force balance formula: f31＝F12-F11
Moment balanceThe formula: f12(l12+l31)-F11(l11+l12+l31)＝M31
F12(l12+l31)-F11(l11+l12+l31)＝M31
The moment of the elastic coupling is ensured to be zero when radial force is applied, i.e.
F12l12-F11(l11+l12)＝0
Can obtain the product
(F12-F11)l31＝M31
In the above formula, F11、F12For applying two radial forces, i, in radial angular loading mechanisms, respectively11、ι12Respectively the distance, M, from two radial forces to the test piece of the elastic coupling31To fix the moment of the bearing-housing assembly31The distance from the moment of fixedly supporting the bearing seat assembly to the elastic coupling test piece is obtained.
(2) The load diagram of the angular loading condition can refer to the diagram shown in fig. 8, when the radial angular loading mechanism 110 applies a pair of force couples, the radial force is a pair of balancing forces, and the moment is balanced by two electric cylinders in the axial loading mechanism 120, where the device balance equation is:
force balance formula: f11＝F12，F21＝F22
Moment balance formula: f11l11＝2F21l21
In FIG. 8, F11、F12For applying two radial forces, i, in radial angular loading mechanisms, respectively11、ι12The distances from the two radial forces to the elastic coupling test piece are respectively; f21、F22For applying two axial forces, iota, respectively, in the axial loading mechanism21、ι22The distances from the two axial directions to the elastic coupling test piece are respectively.
(3) The schematic load diagram of the axial loading condition can refer to the schematic diagram shown in fig. 9, and when the axial loading mechanism 120 applies an axial force, the load is transmitted to the guide rail chassis 116 in the radial angular loading mechanism 110 by using the characteristic that the double-row angular contact ball bearing can transmit a large axial force, and is balanced by the turntable fixedly supported on the supporting platform. The device balance equation under this condition is:
force balance formula: f21+F22＝F2
F2＝F1
Can obtain the product
Moment balance formula: f21l21＝F22l22
In the above formula, F21、F22For applying two axial forces, iota, respectively, in the axial loading mechanism21、ι22Respectively the distance between two axial directions and the elastic coupling test piece, and F2 is F21And F22F1 is the force to which the first drive shaft is subjected.
In a second aspect, the present application provides a fatigue test method for a coupling, which is applied to any one of the above fatigue test apparatuses for a coupling, and mainly includes the following steps:
s1, clamping a test piece: and clamping an elastic coupling test piece in the connecting system, respectively connecting the elastic coupling test piece with a driving variable frequency motor and a load variable frequency motor through a first slide bar cross universal coupling, a second slide bar cross universal coupling and a transmission shaft assembly, and detecting the coaxiality of the connecting position in the device by using a lever dial indicator.
In addition, after the test system is installed, eddy current displacement sensors are installed at the horizontal position and the vertical position of the elastic coupling test piece, and an angle sensor is installed at the center of the guide rail chassis and is used for measuring signals of displacement and rotation angle respectively
S2, formal test: resetting the torque force, the radial force and the angle of a sensor in a data measurement system, starting a driving variable frequency motor to a test rated rotating speed, and resetting the torque force value in a balanced manner; controlling a load variable frequency motor to enable the torque to reach a test set value through a feedback torque signal, acquiring various data by an acquisition and measurement system after a transmission system is stable, and selecting an external excitation state under a corresponding working condition to control each loading device according to vibration test data or a simulation result of the transmission system on a task section;
s3, signal acquisition: the acquisition and measurement system acquires displacement, torsion, radial force and angle data of the elastic coupling test piece, performs Fourier transform (FFT) on a time domain signal of the displacement data to extract a characteristic value, and detects frequency change.
Displacement data acquired by the eddy current displacement sensor are time domain signals, in order to monitor the vibration fatigue test more clearly, the time domain signals need to be subjected to Fourier transform (FFT) in a control system to extract characteristic values, and frequency change is monitored; the influence of the elastic coupling test piece on the transmission efficiency under different test working conditions can be obtained through the measured values of the first torsion sensor and the second torsion sensor; and correcting the load of the elastic coupling test piece which is subjected to large deformation in the loading process of the radial angular loading mechanism according to the measurement value of the angle sensor on the guide rail chassis.
And S4, finishing the test: stopping the test when the specified cycle number is tested and the elastic coupling test piece 300 is not damaged; or in the normal test process, when the natural frequency of the elastic coupling test piece is reduced by 0.5-1.5% (preferably 1%), the fatigue crack is considered to be generated, and the test is stopped; or the crack of the elastic coupling test piece is not generated at the dangerous part, the elastic coupling test piece is scrapped, and the experiment is stopped.
Before the experiment of the elastic coupling, the test piece of the elastic coupling can be arranged in a fixed tool, the natural frequency of the coupling structure is tested independently by using a hammering method, and frequency response curves in all directions are recorded; according to the clamping mode of the modal test, a coupler dynamic model is established in finite element software, modal analysis is carried out, the resonant frequency and the vibration mode are extracted, the accuracy of the finite element model is verified according to the comparison result of simulation calculation and the modal test, and finally the established coupler model is connected into a finite element model of a transmission system for analysis, and the structural dangerous part is determined.
The step of selecting the external excitation state under the corresponding working condition to control each loading device comprises the following steps:
a) Working condition of elastic coupling radial vibration fatigue test
The method comprises the following steps of applying a radial force to an elastic coupling test piece by using a radial angular loading mechanism, wherein the force needs to meet the condition that the moment at the elastic coupling test piece is zero when the force is coordinately loaded in a control system, and the calculation formula is as follows:
radial force equation: fr＝F12-F11
The moment equation: f11(l11+l12)＝F12l12
Substituting the radial force equation into the moment equation
F11(l11+l12)-(Fr+F11)l12＝0
Can obtain the product
In the above formula, A is a constant, wherein F11、F12Applying two radial forces, iota, respectively, to the radial angular loading mechanism11、ι12The distances from the two radial forces to the elastic coupling test piece are respectively;
the radial force F is input in the loading control system by the above-mentioned relationrThe coordination loading of the radial angular loading mechanism can be realized, so that the elastic coupling test piece is only excited by radial force, and the dynamic application of the radial load of the elastic coupling can be realized by utilizing a load spectrum;
b) Working condition of angular vibration fatigue test of elastic coupling
Angular fatigue refers to the fact that an elastic element in an elastic coupling test piece is subjected to alternating moment (M) around a Z axisZ) In order to realize that the elastic coupling test piece is only affected by angular excitation, the fatigue performance under the influence can utilize a radial angular loading mechanism to apply loads with equal magnitude and opposite directions to the elastic coupling test piece, and the calculation formula is as follows:
radial force equation: f11＝F12
The moment equation: mZ＝F11(l11+l12)-F12l12
Can obtain the product
MZ＝F11l11
In the above formula F11、F12For applying two radial forces, i, in radial angular loading mechanisms, respectively11、ι12The horizontal distances from the two radial forces to the elastic coupling test piece are respectively, no additional shearing force is generated on the elastic coupling test piece in the process of applying a pair of force couples, and the dynamic application of the angular fatigue load of the elastic coupling test piece can be realized by coordinately controlling the load and the direction of the two radial forces;
c) Working condition of elastic coupling axial vibration fatigue test
The axial loading mechanism is used for applying loads with equal magnitude and same direction, and the calculation formula is as follows:
axial force equation: fx＝F21+F22
The moment equation: f21l21＝F22l22
Wherein
F21＝F22，l21＝l22
In the above formula F21、F22For applying two axial forces, iota, respectively, in the axial loading mechanism21、ι22The vertical distances from the two axial forces to the central axis of the elastic coupling test piece are respectively.
The present application has been described in detail with reference to specific embodiments and illustrative examples, but the description is not intended to limit the application. Those skilled in the art will appreciate that various equivalent substitutions, modifications or improvements may be made to the presently disclosed embodiments and implementations thereof without departing from the spirit and scope of the present disclosure, and these fall within the scope of the present disclosure. The protection scope of this application is subject to the appended claims.
Claims (10)
1. A fatigue test device for a coupling, characterized in that the fatigue test device comprises: a loading system (100), a connection system (200), and a data measurement system (400);
the loading system (100) comprises a driving variable frequency motor (101), a radial angular loading mechanism (110), an axial loading mechanism (120) and a load variable frequency motor (102), wherein the horizontal direction of the radial angular loading mechanism (110) is vertical to the horizontal direction of the axial loading mechanism (120) under the condition of no load, the radial angular loading mechanism (110) is used for applying radial and angular loads to an elastic coupling test piece, and the axial loading mechanism (120) is used for applying axial loads to the elastic coupling test piece;
the connecting system (200) comprises a first slide bar cross universal coupling (201), a second slide bar cross universal coupling (202) and a transmission shaft assembly, wherein the first slide bar cross universal coupling (201) is respectively connected with the driving variable frequency motor (101) and the elastic coupling test piece through the transmission shaft assembly, and the second slide bar cross universal coupling (202) is respectively connected with the loading variable frequency motor (102) and the elastic coupling test piece through the transmission shaft assembly;
the data measurement system (400) is used for measuring the torque force on the transmission shaft assembly, the radial force and the angle on the radial angular loading mechanism (110), the axial force of the axial loading mechanism (120) and the displacement of the elastic coupling test piece.
2. A fatigue testing device for a coupling according to claim 1, wherein the radial angular loading mechanism (110) comprises a first loading device, a second loading device, a first knuckle bearing (113), a radial loading bearing seat (114), a slider (115), a guide rail chassis (116) and a turntable bearing (117);
the first loading device and the second loading device have the same structure and are respectively composed of a first electric cylinder (111) and a first electric cylinder base (112), and the first electric cylinder base (112) is used for supporting and fixing the first electric cylinder (111);
the radial loading bearing seats (114) and the first knuckle bearings (113) are arranged in two groups, each group is formed by connecting the radial loading bearing seats (114) with the first knuckle bearing (113) on one side and on the same side, the two first knuckle bearings (113) are parallel to each other under the condition of no load, the axis of the first knuckle bearing is vertical to a transmission shaft of the radial loading bearing seat (114), the first loading device is connected with one first knuckle bearing (113), and the second loading device is connected with the other first knuckle bearing (113);
the two groups of sliding blocks (115) are arranged, each sliding block (115) is connected with the radial loading bearing seat (114) at the corresponding position, and the sliding blocks (115) slide along a guide rail on the upper surface of the guide rail chassis (116) under the action of force; the turntable bearing (117) is arranged on the lower surface of the guide rail chassis (116) and is used for the guide rail chassis (116) to rotate under the action of force.
3. The fatigue testing device for a coupling according to claim 2, wherein the axial loading mechanism (120) comprises a third loading device, a fourth loading device, a second joint bearing (123), an axial loading bearing seat (124), a bearing seat support frame (125), a linear motion bearing assembly (126) and a solid bearing seat assembly (220), and the connecting system (200) comprises a third transmission shaft (213);
the third loading device and the fourth loading device are identical in structure and both consist of a second electric cylinder (121) and a second electric cylinder base (122), and the second electric cylinder base (122) is used for supporting and fixing the second electric cylinder (121);
the two sides of the axial loading bearing seat (124) are respectively connected with one second joint bearing (123), the axes of the two second joint bearings (123) and the linear motion bearing assembly (126) are parallel to each other under the condition of no load, the third loading device is connected with one second joint bearing (123), and the fourth loading device is connected with the other second joint bearing (123);
the two bearing seat supporting frames (125) are respectively positioned at two sides of the axial loading bearing seat (124) and used for reducing the friction force of the axial loading bearing seat (124) during axial movement;
the third transmission shaft (213) is radially and axially constrained through the fixed support bearing seat assembly (220), and the fixed support bearing seat assembly (220) is used for balancing radial force and moment;
the linear motion bearing assembly (126) is arranged on the axial loading bearing seat (124), the linear motion bearing assembly (126) is connected with the fixed support bearing seat assembly (220) through a third transmission shaft (213), and the linear motion bearing assembly (126) is used for releasing the axial freedom degree of the axial loading mechanism (120) and enabling the second sliding rod cross universal coupling (202) not to be influenced by axial force.
4. A fatigue testing device for a coupling according to claim 3, wherein the data measuring system comprises a first torsion sensor (401), a second torsion sensor (402), a first radial force sensor (403), a second radial force sensor (404), a first axial force sensor (405), a second axial force sensor (406), an eddy current displacement sensor (407) and an angle sensor (408);
the first torsion sensor (401) is arranged on the first slide bar cross universal joint (201), the second torsion sensor (402) is arranged on the second slide bar cross universal joint (202), the first radial force sensor (403) is arranged on the first loading device, the second radial force sensor (404) is arranged on the second loading device, the first axial force sensor (405) is arranged on the third loading device, the second axial force sensor (406) is arranged on the fourth loading device, the eddy current displacement sensor (407) is arranged at an elastic joint test piece loading position, and the angle sensor (408) is arranged on the guide rail chassis (116).
5. The fatigue testing device for the coupling according to claim 4, wherein the first electric cylinder base (112) is connected with the first electric cylinder (111) through a self-aligning roller bearing;
the actuating ends of the two first electric cylinders (111) are respectively fixed with the first radial force sensor (403) and the second radial force sensor (404) and the first joint bearing (113)) which is matched with the first electric cylinders respectively by using transition bolts, and the head parts of the first joint bearings (113) are hinged to the loading ends of the radial loading bearing seats (114);
the radial loading bearing seat (114) is internally provided with a double-row angular contact ball bearing and a first transmission shaft (211) connected with the double-row angular contact ball bearing, the sliding block (115) is installed in a groove on the outer bottom surface, and the sliding block (115) is installed on a track of the guide rail chassis (116).
6. The fatigue testing apparatus for a coupling according to claim 5, wherein the linear motion bearing assembly (126) comprises a rail mounting flange (1261), a rail mounting flange (1262), a rail shaft (1263), a linear motion ball bearing (1264), and a clamp spring (1265);
the guide rail shaft (1263) and the linear motion ball bearing (1264) are fixed between the guide rail mounting flange (1261) and the guide rail support flange (1262) using the clamp spring (1265), respectively;
the bearing seat support frame (125) is H-shaped, and a cross beam of the H-shaped main body is provided with a rolling linear needle roller guide rail support (1251).
7. The fatigue testing device for the coupling according to claim 6, wherein the second electric cylinder base (122) is connected with the second electric cylinder (121) through a self-aligning roller bearing;
the actuating ends of the two second electric cylinders (121) respectively fix a first axial force sensor (405) and a second axial force sensor (406) with the matched second joint bearing (123) by using transition bolts, and the head parts of the second joint bearings (123) are hinged to the loading ends of the axial loading bearing seats (124);
a double-row angular contact ball bearing and a second transmission shaft (212) connected with the double-row angular contact ball bearing are arranged in the axial loading bearing seat (124), and the second transmission shaft (212) and the guide rail shaft mounting flange plate (1261) are fixed through bolts and splines;
the third transmission shaft (213) is used for connecting the second slide bar cross universal joint (202), the fixed bearing seat assembly (220) and the guide rail support flange plate (1262).
8. A fatigue testing device for a coupling according to any of claims 2-7, further comprising a support system (500);
the supporting system (500) comprises a chute test platform (501) used for adjusting and fixing the systems;
the fixedly supported bearing block assembly (220) mainly comprises a bearing block (221) and a double-row deep groove ball bearing (222), wherein the double-row deep groove ball bearing (222) is connected with the third transmission shaft (213), the bottom of the bearing block (221) is fixedly supported on the chute test platform (501), and force and moment are balanced through a fixedly supported end of the bearing block (221).
9. A fatigue test method of a coupling, which is applied to the fatigue test device for the coupling according to any one of claims 1 to 8, and which mainly comprises the following steps:
s1, clamping a test piece: clamping an elastic coupling test piece in the connecting system, respectively connecting the elastic coupling test piece with a driving variable frequency motor and a load variable frequency motor through a first slide bar cross universal coupling, a second slide bar cross universal coupling and a transmission shaft assembly, and detecting the coaxiality of the connecting position in the device by using a lever dial indicator;
s2, formal test: resetting the torque force, the radial force and the angle of a sensor in the data measurement system, starting and driving the variable frequency motor to a test rated rotating speed, and carrying out balance resetting on the torque force value again; controlling a load variable frequency motor to enable the torque to reach a test set value through a feedback torque signal, acquiring various data by an acquisition and measurement system after a transmission system is stable, and selecting an external excitation state under a corresponding working condition to control each loading device according to vibration test data or a simulation result of the transmission system on a task section;
s3, signal acquisition: the method comprises the steps that a collecting and measuring system collects displacement, torsion, radial force and angle data of an elastic coupling test piece, time domain signals of the displacement data are subjected to Fourier transform (FFT) to extract characteristic values, and frequency change is detected;
and S4, finishing the test: stopping the experiment when the specified cycle number is tested and the elastic coupling test piece is not damaged; or in the normal test process, when the natural frequency of the elastic coupling test piece is reduced by 0.5-1.5%, the fatigue crack is considered to be generated, and the test is stopped; or the crack of the elastic coupling test piece is not generated at the dangerous part, the elastic coupling test piece is scrapped, and the experiment is stopped.
10. A fatigue testing method for a coupling according to claim 9, wherein said selecting an external excitation state under a corresponding condition to control each loading device comprises the steps of:
a) Working condition of elastic coupling radial vibration fatigue test
The method comprises the following steps that a radial angular loading mechanism is utilized to apply radial force to an elastic coupling test piece, the radial force needs to meet the condition that the moment at the elastic coupling test piece is zero when the radial force is coordinately loaded in a control system, and the calculation formula is as follows:
radial force equation: fr＝F12-F11
The moment equation: f11(l11+l12)=F12l12
Substituting the radial force equation into the moment equation
F11(l11+l12)-(Fr+F11)l12＝0
Can obtain the product
In the above formula, A is a constant, wherein F11、F12Applying two radial forces in radial angular loading mechanisms respectively，ι11、ι12The distances from the two radial forces to the elastic coupling test piece are respectively;
the radial force M is input in the loading control system by the above-described relationrThe coordination loading of the radial angular loading mechanism can be realized, so that the elastic coupling test piece is only excited by radial force, and the dynamic application of the radial load of the elastic coupling can be realized by utilizing a load spectrum;
b) Working condition of angular vibration fatigue test of elastic coupling
Angular fatigue refers to the fact that an elastic element in an elastic coupling test piece is subjected to alternating moment (M) around a Z axisZ) In order to realize that the elastic coupling test piece is only affected by angular excitation, the fatigue performance under the influence can utilize a radial angular loading mechanism to apply loads with equal magnitude and opposite directions to the elastic coupling test piece, and the calculation formula is as follows:
radial force equation: f11＝F12
The moment equation: mz＝F11(l11+l22)-F12l12
Can obtain the product
MZ＝F11l11
In the above formula F11、F12For applying two radial forces, i, in radial angular loading mechanisms, respectively11、ι12The horizontal distances from the two radial forces to the elastic coupling test piece are respectively, no additional shearing force is generated on the elastic coupling test piece in the process of applying a pair of force couples, and the dynamic application of the angular fatigue load of the elastic coupling test piece can be realized by coordinately controlling the load and the direction of the two radial forces;
c) Working condition of elastic coupling axial vibration fatigue test
The axial loading mechanism is used for applying loads with equal magnitude and same direction, and the calculation formula is as follows:
axial force equation: fx＝F21+F22
The moment equation: f21l21＝F22l22
Wherein
F21=F22,l21=l22
In the above formula F21、F22For applying two axial forces, iota, respectively, in the axial loading mechanism21、ι22The vertical distances from the two axial forces to the central axis of the test piece of the elastic coupling are respectively.
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