CN108362586A - Resonate fatigue bending machine - Google Patents
Resonate fatigue bending machine Download PDFInfo
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- CN108362586A CN108362586A CN201810171221.3A CN201810171221A CN108362586A CN 108362586 A CN108362586 A CN 108362586A CN 201810171221 A CN201810171221 A CN 201810171221A CN 108362586 A CN108362586 A CN 108362586A
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01N—INVESTIGATING OR ANALYSING MATERIALS BY DETERMINING THEIR CHEMICAL OR PHYSICAL PROPERTIES
- G01N3/00—Investigating strength properties of solid materials by application of mechanical stress
- G01N3/32—Investigating strength properties of solid materials by application of mechanical stress by applying repeated or pulsating forces
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01N—INVESTIGATING OR ANALYSING MATERIALS BY DETERMINING THEIR CHEMICAL OR PHYSICAL PROPERTIES
- G01N2203/00—Investigating strength properties of solid materials by application of mechanical stress
- G01N2203/0001—Type of application of the stress
- G01N2203/0005—Repeated or cyclic
- G01N2203/0008—High frequencies from 10 000 Hz
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01N—INVESTIGATING OR ANALYSING MATERIALS BY DETERMINING THEIR CHEMICAL OR PHYSICAL PROPERTIES
- G01N2203/00—Investigating strength properties of solid materials by application of mechanical stress
- G01N2203/0058—Kind of property studied
- G01N2203/0069—Fatigue, creep, strain-stress relations or elastic constants
- G01N2203/0073—Fatigue
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- Investigating Strength Of Materials By Application Of Mechanical Stress (AREA)
Abstract
The present invention relates to a kind of resonance fatigue bending machines, belong to component of machine fatigue test technology field, including pedestal, left socle, intermediate support, right support, flexible support mechanism, clamping device and vibration of optical displacement monitor, left socle is identical with the structure of right support and is equipped with flexible support mechanism, clamping device and vibration of optical displacement monitor, and intermediate support is equipped with vibration of optical displacement monitor.The present invention realizes that the bending for treating test block and torsional fatigue test apply load with resonance principle, test specimen, connector, vibrator and clump weight to be measured constitute the beam of approximate ideal, under the single order formation of resonance, equivalent beam is supported using flexible support mechanism, exciting force is applied by vibrator, the structure of testing machine is simplified, and larger power output is obtained with smaller input power using resonance principle, input power when reducing fatigue test needed for testing machine.
Description
Technical field
The present invention relates to component of machine fatigue test technology fields, more particularly to a kind of resonance repeated bend test
Machine.
Background technology
The fatigue of component of machine is the main form of its operational failure, therefore fatigue test is that component of machine must not
Performance detection and Means of Ensuring that can be less.Bending and torsional load are the common loading form of fatigue test of rod piece, load
There are many ways to, such as combine the testing machine constituted with loading system by traditional upper spider and load is applied to test specimen, but
It is that traditional fatigue tester often has that volume is big, complicated and energy consumption is big, especially such as System for Large-scale Specimen
This.
Invention content
Based on this, it is necessary to there is a problem of that volume is big, complicated and energy consumption is big for traditional fatigue tester,
A kind of resonance fatigue bending machine is provided.
To solve the above problems, the present invention takes the following technical solution：
A kind of resonance fatigue bending machine, including pedestal, left socle, intermediate support, right support, flexible support mechanism,
Clamping device and vibration of optical displacement monitor, the left socle is identical with the structure of the right support and is equipped with described soft
Property supporting mechanism, the clamping device and the vibration of optical displacement monitor, the intermediate support be equipped with the optics
Vibration displacement monitoring device；
The both ends of test specimen to be measured are fixedly connected by connector with vibrator, clump weight respectively, the test specimen to be measured, described
Vibrator, the clump weight and the connector constitute equivalent beam；
The equivalent beam is connect with the left socle and the right support respectively by the flexible support mechanism, and
The left socle and the right support are connect by the linear guide with the pedestal, and the left socle and the right support being capable of edges
The axial-movement of the pedestal, so that the flexible support mechanism is fixed at the node location of the equivalent beam；
The connector when clamping device is for in non-vibration state grips；
The vibration of optical displacement monitor being arranged on the left socle and the right support is described for monitoring
The Oscillation Amplitude of connector, the vibration of optical displacement monitor being arranged on the intermediate support is for monitoring described wait for
The Oscillation Amplitude of test block, and the vibration of optical displacement monitor Oscillation Amplitude information monitored is sent to it is upper
Machine, the host computer control the energy input of the vibrator according to the Oscillation Amplitude information.
Above-mentioned resonance fatigue bending machine has the following technical effects：
(1) it with smaller input power and power, realizes high to needing to apply compared with noticeable effort or the test specimen of power input
Frequency alternating load implements high-speed test (HST)；
(2) testing machine is without test load is subjected to, and it is only necessary to undertake the gravity of mainly test specimen itself for it.Therefore, greatly
It is big to simplify and save mechanical structure, reduce cost；
(3) connector, clump weight and the vibrator having with equipment itself coordinate, and can complete the curved of multiple types test specimen
Bent, torsional fatigue test.
Description of the drawings
Fig. 1 is the dimensional structure diagram of the present invention resonance one of embodiment of fatigue bending machine；
Fig. 2 is the side view of resonance fatigue bending machine in Fig. 1；
Fig. 3 is the structural schematic diagram of equivalent beam；
Fig. 4 is that the resonance of free restained beam is bent single order formation schematic diagram；
Fig. 5 is the sectional view at the places B-B ' in Fig. 2；
Fig. 6 is the structural schematic diagram of the first saddle support；
Fig. 7 is the structural schematic diagram of the second saddle support；
Fig. 8 is the sectional view at the places A-A ' in Fig. 2；
Fig. 9 is the side view of the first fixture block；
Figure 10 is the structural schematic diagram of vibrator；
Figure 11 is the principle schematic that vibrator generates different directions vibration.
Specific implementation mode
Technical scheme of the present invention is described in detail below in conjunction with attached drawing and preferred embodiment.
In one of the embodiments, as shown in Figs. 1-2, resonance fatigue bending machine include pedestal 1, left socle 2, in
Between holder 3, right support 4, flexible support mechanism 5, clamping device 6 and vibration of optical displacement monitor 7, left socle 2 and right branch
The structure of frame 4 is identical and is equipped with flexible support mechanism 5, clamping device 6 and vibration of optical displacement monitor 7, intermediate support 3
It is equipped with vibration of optical displacement monitor 7；
The both ends of test specimen 8-1 to be measured are fixedly connected by connector 8-4 with vibrator 8-2, clump weight 8-3 respectively, to be measured
Test specimen 8-1, vibrator 8-2, clump weight 8-3 and connector 8-4 constitute equivalent beam；
Equivalent beam is connect with left socle 2 and right support 4 respectively by flexible support mechanism 5, and left socle 2 and right branch
Frame 4 is connect by the linear guide 9 with pedestal 1, and left socle 2 and right support 4 can be along the axial-movements of pedestal 1, so that flexible prop up
Support mechanism 5 is fixed at the node location of equivalent beam；
Connector 8-4 when clamping device 6 is for in non-vibration state is gripped；
The vibration of optical displacement monitor 7 being arranged on left socle 2 and right support 4 is for monitoring shaking for connector 8-4
Dynamic amplitude, the vibration of optical displacement monitor 7 being arranged on intermediate support 3 are used to monitor the Oscillation Amplitude of test specimen 8-1 to be measured,
And the Oscillation Amplitude information monitored is sent to host computer by vibration of optical displacement monitor 7, host computer is according to Oscillation Amplitude
Information controls the energy input of vibrator 8-2.
Specifically, in the present embodiment, pedestal 1 is the brace foundation of entire testing machine, is one by ferrous matenial
Expect the overall base made, it is smooth up and down, it can be fastened by the modes such as foundation bolt and ground.Left socle 2 and right support 4 are all
The structure bare bones of the frame (as shown in Figure 8) of one truss structure, left socle 2 and right support 4 are guarantee enabling capabilities, and
Structure is simple as possible, and interference is not generated to fatigue test process, looks along connector 8-4 axis directions, left socle 2 and right branch
Some V-shaped space of the intermediate position of frame 4, the size of this segment space is not to interfere connector 8-4 as minimum dimension.
The both ends of test specimen 8-1 to be measured are fixedly connected by connector 8-4 with vibrator 8-2, clump weight 8-3 respectively, to be measured
Test specimen 8-1, connector 8-4, vibrator 8-2 and clump weight 8-3 constitute equivalent beam.As shown in figure 3, test specimen 8-1 to be measured
Both ends are fixedly connected with one end of connector 8-4 respectively by two attachment device 8-5 (such as ring flange), one of connection
The other end of part 8-4 is fixedly connected with vibrator 8-2, the other end of another connector 8-4 is fixedly connected with clump weight 8-3,
Wherein connector 8-4 is equivalent test specimen, can be cylindrical or cylindrical shape, i.e. its section can be round, can also
It is circular ring shape.The one end connecting test specimen 8-1 to be measured is provided with mark on connector 8-4, can show that the phase of circumferencial direction,
This phase position is for determining the relationship with the direction of excitation of vibrator 8-2.
Equivalent beam is connect with left socle 2 and right support 4 respectively by two flexible support mechanisms 5, and left socle 2
Connect with pedestal 1 by the linear guide 9 with right support 4, left socle 2 and right support 4 can along the axial-movement of pedestal 1, to
Adjust actual node location so that flexible support mechanism 5 is fixed at the node location of equivalent beam, so-called node position
Setting in close to the end of equivalent beam.Soft test specimen 8-1 to be measured, connector 8-4, vibrator 8-2 and clump weight 8-3 are fixed
Equivalent beam is constituted after connection, has the condition for realizing bending and/or torsional resonance, and one of outstanding feature is, when vibration
Two nodes can be formed, the theoretic displacement of the lines of the two nodes or angular displacement are zero, and the position of the two nodes is also
The installation site of flexible support mechanism 5.Equivalent beam can also be whole individual member in the present invention, by test specimen 8-1 to be measured
Both ends be directly fixedly connected with composition with vibrator 8-2, clump weight 8-3 respectively.
On entire fatigue tester, including two sets of same clamping devices 6, it is separately mounted to left socle 2 and right support 4
On, clamping device 6 is used to grip connector 8-4 when being in non-vibration state (or off working state), with
It avoids when test specimen 8-1 to be measured is not fixedly connected with connector 8-4, since the weight of vibrator 8-2 or clump weight 8-3 are larger
And connector 8-4 is caused to turn on one's side, and when fatigue tester being avoided to be in off working state, flexible support mechanism 5 is born
The excessive weight of equivalent beam.Clamping device 6 may be implemented that connector 8-4 is clamped or is unclamped as needed, such as
When vibrator 8-2 applies exciting force progress fatigue test to connector 8-4, clamping device 6 unclamps connector 8-4, when even
When fitting 8-4 is in non-vibration state, clamping device 6 is then by connector 8-4 clampings to position and fix equivalent beam.
Vibration of optical displacement monitor 7 (as shown in Figure 2) is mounted on left socle 2, intermediate support 3 and right support 4,
Wherein, the vibration width that the vibration of optical displacement monitor 7 on left socle 2 and right support 4 is used to monitor connector 8-4 is set
Degree, the vibration of optical displacement monitor 7 being arranged on intermediate support 3 are used to monitor the Oscillation Amplitude of test specimen 8-1 to be measured, installation
Vibration of optical displacement monitor 7 on left socle 2, right support 4 and the vibration of optical displacement on intermediate support 3
Monitoring device 7 sends out the Oscillation Amplitude information of the Oscillation Amplitude information of the connector 8-4 respectively monitored and test specimen 8-1 to be measured
It send to host computer, host computer controls the energy of vibrator 8-2 according to the Oscillation Amplitude information of connector 8-4 and test specimen 8-1 to be measured
Input, to enable vibrator 8-2 to realize adjustable, controllable linear vibration, plane torsion vibration and Plane Rotation
Vibration, and then realize the fatigue experiment for treating test block 8-1.
The resonance fatigue bending machine of the present embodiment utilizes the flexural resonance principle work of free restained beam in vibration mechanics
To make, the configuration characteristic of test specimen to be measured can be considered as the beam in mechanical meaning, using vibrator to its exciting under resonance condition, and
It is vibrated under single order formation, by changing the energy input of vibrator, the big of test specimen flexural deformation to be measured is varied and controlled in realization
It is small, to according to the stress relationship directly proportional to deformation, realize the purpose for controlling test specimen proof stress to be measured.Equivalent beam
Support is especially placed at two node locations of single order formation, and theoretically support device is not affected by vibrations, does not also hold
By the load other than equivalent beam gravity.In the resonance fatigue bending machine of the present invention, test specimen to be measured is equivalent to
Beam in mechanics realizes that the bending vibration single order formation of free restained beam, the resonance for being illustrated in figure 4 free restained beam are curved
Qu Yijie formation schematic diagrames, solid line is ideal beam in figure, it is in free restrained condition at this time, when it is in bending vibration
Single order formation when, vibration contour curve as shown in broken lines, it is expressly noted that have at the both ends of beam
Two point o1 and o2, they are static, as node in beam vibration.
The resonance fatigue bending machine that the present embodiment is proposed has the following technical effects：
(1) it with smaller input power and power, realizes high to needing to apply compared with noticeable effort or the test specimen of power input
Frequency alternating load implements high-speed test (HST)；
(2) testing machine is without test load is subjected to, and it is only necessary to undertake the gravity of mainly test specimen itself for it.Therefore, greatly
It is big to simplify and save mechanical structure, reduce cost；
(3) connector, clump weight and the vibrator having with equipment itself coordinate, and can complete the curved of multiple types test specimen
Bent, torsional fatigue test.
The resonance fatigue bending machine that the present embodiment is proposed with resonance principle realize treat test block bending and
Torsional fatigue test applies load, and test specimen to be measured constitutes the beam of approximate ideal together with connector, vibrator and clump weight,
Under the single order formation of resonance, equivalent beam is supported using flexible support mechanism, exciting force is applied by vibrator, is passed through
Cooperation between test specimen and connector to be measured, clump weight, vibrator can complete bending, the torsional fatigue of multiple types test specimen to be measured
Experiment, while testing machine, without test load is subjected to, flexible support mechanism only needs to support the gravity of equivalent beam, significantly simple
The mechanical structure for having changed testing machine further decreases cost, and since it makes use of resonance principles, can be with smaller
Input power obtains larger power output, with smaller input power and power, realizes to needing compared with noticeable effort or power input
Test specimen to be measured apply high-frequency alternating load, implement high-speed test (HST), input power when reducing fatigue test needed for testing machine,
With preferable energy-saving effect.
As a kind of specific embodiment, as illustrated in figs. 5-7, flexible support mechanism 5 includes the first saddle support 5-
1, the second saddle support 5-2 and four flexible cable 5-3.Since the flexible support mechanism 5 being arranged on left socle 2 and right support 4 is complete
It is exactly the same, therefore here only by taking the flexible support mechanism 5 being arranged on right support 4 as an example, to the flexible support mechanism 5 of the present invention
Structure be specifically described：
As shown in fig. 6, two roller 5-1-1 are mounted on the first saddle support 5-1, roller 5-1-1 can be around the shaft
5-1-2 is freely rotated, and the first saddle support 5-1 is an integrated member, in addition to outputing space for installing roller 5-1-1
In addition, two ends also open up the flexible cable connecting hole 5-1-3 for connecting flexible cable 5-3, and the structure of the first saddle support 5-1
Type will not generate interference phenomenon to equivalent beam；Similarly, as shown in fig. 7, two roller 5-2-1 are mounted on second shape of a saddle
On holder 5-2, roller 5-2-1 can be freely rotated with 5-2-2 around the shaft, and the second saddle support 5-2 is also a whole structure
Part, in addition to outputing space for other than installing roller 5-2-1, two ends also to open up the flexible cable for connecting flexible cable 5-3 and connect
Hole 5-2-3, and the configuration of the second saddle support 5-2 will not generate interference phenomenon to equivalent beam.It is respectively provided with one
The the first saddle support 5-1 and the second saddle support 5-2 of roller are connect with one end of each flexible cable 5-3, each flexible cable
The other end of 5-3 is then fixedly connected with right support 4, they constitute positive V-type and reverse V-shaped planform, as shown in figure 5, the first horse
Connector 8-4, and the shaft axis of roller and connector 8-4 are placed between saddle support 5-1 and the second saddle support 5-2
Axis it is parallel, contacted with each roller line at the node location of connector 8-4, wherein constituting second shape of a saddle of positive V-type
Holder 5-2 and flexible cable 5-3 is used to bear the gravity of equivalent beam, constitutes the first reverse V-shaped saddle support 5-1 and flexible cable 5-
The 3 improper movement for avoiding equivalent beam, preferably to realize the support to equivalent beam.Present embodiment is carried
The structure and shape of this flexible support mechanism gone out can preferably realize the support to equivalent test specimen to be measured.
Preferably, the outer surface for each roller installed on the first saddle support 5-1 and the second saddle support 5-2
One layer of rubber is coated, to increase the frictional force between connector 8-4 and roller, while can effectively avoid connector 8-4
Scuffing between roller.
Preferably, the flexible cable 5-3 in the present embodiment can be that anchor chain, steel wire rope or cotton rope etc. are various forms of flexible anti-
Any one in draw piece.
As a kind of specific embodiment, as shown in figure 8, clamping device 6 includes the first fixture block 6-1, the second fixture block 6-
2, line slideway auxiliary 6-3 and screw pair 6-4, and the first fixture block 6-1 and the second fixture block 6-2 pass through line slideway auxiliary 6-3
It is connected with corresponding holder (left socle 2 or right support 4).The movement of first fixture block 6-1 and the second fixture block 6-2 are by feed screw nut
Secondary 6-4 drives, and the size and shape of the first fixture block 6-1 and the second fixture block 6-2 are identical, and the first fixture block 6-1 and the second fixture block 6-2
Mirror image installation constitutes the main body of clamping device 6, and the first fixture block 6-1 and the second fixture block 6-2 can be along perpendicular to connector 8-4's
Opposite synchronizing moving is made in the direction of axis, is oriented to by two line slideway auxiliary 6-3, is driven by a set of screw pair 6-4, wherein
Two line slideway auxiliary 6-3 are arranged in the bottom support platform (2-1) of left socle 2, and the structure of screw pair 6-4 is as follows：
A piece leading screw is axially divided into left and right two parts (two sub- leading screws), and the head number of the threads of lead screw of two parts, helical pitch are identical,
But it is oppositely oriented, the feed screw nut to match therewith is fastened on by mounting hole 6-1-1 on fixture block, can be set in one end of leading screw
The square toes or turret head applied convenient for leading screw rotation torque are set, feed screw nut has self-lock ability, and lock is arranged on leading screw
Tight spiral shell 6-5, for implementing locking when needed.Rotating threaded shaft so that between the first fixture block 6-1 and the second fixture block 6-2
Distance furthers or separate, to realize the clamping to being put into the connector 8-4 between the first fixture block 6-1 and the second fixture block 6-2
Or release.Clamping device 6 is connected by straight-line guide rail slide block mechanism (i.e. line slideway auxiliary 6-3) with corresponding holder.Driving
First fixture block 6-1 and the screw pair 6-4 of the second fixture block 6-2 movements are located in the first fixture block 6-1 and the second fixture block 6-2
Between, it is oriented to and the guide rail of connection function has two.Present embodiment is increased tired by the rational design to clamping device 9
Labor testing machine is to the fixed reliability of connector.
It is to be measured for being clamped in addition to being equipped on the first fixture block 6-1 and the second fixture block 6-2 as a kind of specific embodiment
Other than working face needed for equivalent test specimen, it is further opened with observation fenestra 6-1-2, as shown in figure 9, being clamped to be conveniently operated personnel
Observation of the mechanism 6 when being clamped or unclamping connector 8-4 to connector 8-4, in addition, the first fixture block 6-1 and the second fixture block 6-2
It is additionally provided with the peace of the mounting hole 6-1-1 for installing feed screw nut and the straight-line guide rail slide block for installing line slideway auxiliary 6-3
Tankage 6-1-3.
As a kind of specific embodiment, due to the vibration of optical being arranged on left socle 2, intermediate support 3 and right support 4
Displacement monitor 7 is identical, therefore here only by taking the vibration of optical displacement monitor 7 being arranged on right support 4 as an example,
The structure of vibration of optical displacement monitor 7 is specifically described：
As shown in figure 5, vibration of optical displacement monitor 7 includes background board 7-1 and optical displacement monitoring modular 7-2,
Optical displacement monitoring modular 7-2 is installed on the side frame of right support 4, background board 7-1 is installed in opposite another side frame,
Wherein background board 7-1 is a kind of special wall of vibration of optical displacement monitoring, background board 7-1 and optical displacement monitoring modular 7-
2 cooperate, and can monitor the vibration of the connector 8-4 between background board 7-1 and optical displacement monitoring modular 7-2 in real time
Amplitude situation, obtains the Oscillation Amplitude information of connector 8-4, and Oscillation Amplitude information is sent to host computer.Analogously, if
The Oscillation Amplitude of test specimen 8-1 to be measured can be monitored and will shake in real time by setting the vibration of optical displacement monitor 7 on intermediate support 3
Dynamic amplitude information is sent to host computer.Vibrator 8-2 and upper mechatronics, host computer is according to vibration of optical displacement monitor
The energy input of the 7 Oscillation Amplitude information control vibrator 8-2 sent, it is adjustable, controllable to enable vibrator 8-2 to realize
Linear vibration, plane torsion vibration and Plane Rotation vibration, and then realize the fatigue experiment for treating test block 8-1.
As a kind of specific embodiment, as illustrated in figures 1 and 8, the bottom of left socle 2 and right support 4 is equipped with drive
Dynamic screw pair 10, driving screw pair 10 include fixing nut and driving leading screw, and fixing nut is fixed with pedestal 1 to be connected
It connects, driving leading screw is connect with merga pass bearing with left socle 2 or right support 4 with fixing nut.Left socle 2 and right support 4
Bottom two the linear guides 9 are set, for the axis that connect and realize left socle 2 and right support 4 with pedestal 1 along equivalent beam
Line direction moves in a straight line, and the driving mechanism and mode of the linear motion of left socle 2 and right support 4 are using driving screw pair
10, driving screw pair 10 includes fixing nut and driving leading screw, and wherein fixing nut is fixedly connected with pedestal 1, drives silk
Thick stick is then connect by bearing with left socle 2 or right support 4, and driving leading screw is threaded through in fixing nut, and driving leading screw can turn
It is dynamic, but cannot move axially, and drive leading screw can be with self-locking, while it further includes additional locking screw to drive screw pair 10
It is female.
As a kind of specific embodiment, vibrator 8-2 is the inertia vibration generator of automatically controlled automatic amplitude modulationfrequency modulation, and inertia swashs
The device that shakes includes identical a pair of of structure and the slewing equipment 8-2-1 with eccentric mass that is fixedly secured to one another and a pair of for driving back
The synchronous servo motor driver 8-2-2 of rotary device.The structure of vibrator 8-2 is as shown in Figure 10, the installation site of vibrator 8-2
As shown in Figure 1-Figure 3, the vibrator 8-2 in present embodiment is inertia vibration generator, and specially automatically controlled automatic amplitude modulationfrequency modulation is used to
Property vibrator, structure includes vibrator main body, and vibrator main body is by a pair of completely identical in structure revolution with eccentric mass
Device is formed by fixedly connecting, and two slewing equipments are driven by a motor servo driver respectively, and two servo motors drive
Dynamic device is fully synchronized.
Figure 11 show the principle schematic that vibrator 8-2 generates different directions vibration, in the revolution of two slewing equipments
The heart is located at the centre position of two slewing equipment line of centres a, i.e. o points in Figure 11 (a)~(c), F1 in Figure 11 (a)~(c)
Indicate the centrifugal force of centrifugal-block in two slewing equipments respectively with F2；Two motor servo drivers move synchronously forever,
Reach different exciting output by changing steering and the phase of the slewing equipment with eccentric mass.
As shown in Figure 11 (a), bi-motor rotating Vortex, eccentric mass phase initial position is identical, realizes that Plane Rotation shakes
Dynamic, exciting force is located in x/y plane, i.e.,
Fx=2F0cos ω t
Fy=2F0sin ω t
M=0
Wherein, Fx is x to component, and Fy is y to component, and ω is angular velocity of rotation, and t is the time, and M is couple in plane.It is aobvious
Right Fx, Fy constitute an equation of a circle, are with joint efforts
F=2F0
Wherein, F0=mr ω2, m is the quality of equivalent particle, and r is the equivalent radius of gyration.The direction of power is in the faces xy.
As shown in Figure 11 (b), bi-motor rotating Vortex, eccentric mass phase initial position reverse phase realizes that plane torsion shakes
Dynamic, exciting force is located in x/y plane, i.e.,
Fx=0
Fy=0
M=2aF0sin ω t
Wherein, Fx is x to component, and Fy is y to component, and ω is angular velocity of rotation, and t is the time, and M is couple in plane, F0
=mr ω2, m is the quality of equivalent particle, and r is the equivalent radius of gyration, centered on a away from.Couple is located in the faces xy.
As shown in Figure 11 (c), bi-motor reversely rotates, and eccentric mass phase initial position is identical, realizes that plane and straight line is double
To vibration, exciting force is located in y-axis, i.e.,
Fx=0
Fy=2F0sin ω t
M=0
Wherein, Fx is x to component, and Fy is y to component, and ω is angular velocity of rotation, and t is the time, and M is couple in plane, F0
=mr ω2, m is the quality of equivalent particle, and r is the equivalent radius of gyration.Couple is located in y-axis.
It can be seen that steering and phase by changing the slewing equipment with eccentric mass, can realize different excitings
Output：Bi-motor rotating Vortex, eccentric mass phase initial position is identical, it can be achieved that Plane Rotation vibrates；Bi-motor revolves in the same direction
Turn, eccentric mass phase initial phase difference 180 degree is, it can be achieved that plane torsion vibrates；Bi-motor reversely rotates, eccentric mass phase
Initial position is identical, it can be achieved that plane and straight line direction vibration.It realizes that bending vibration includes straight line direction vibration and plane vibration, borrows
Vibrator is helped, when eligible by the equivalent beam constituted based on test specimen to be measured, the torsion for treating test block can also be completed
Rotational oscillation is dynamic.
Each technical characteristic of embodiment described above can be combined arbitrarily, to keep description succinct, not to above-mentioned reality
It applies all possible combination of each technical characteristic in example to be all described, as long as however, the combination of these technical characteristics is not deposited
In contradiction, it is all considered to be the range of this specification record.
Several embodiments of the invention above described embodiment only expresses, the description thereof is more specific and detailed, but simultaneously
It cannot therefore be construed as limiting the scope of the patent.It should be pointed out that coming for those of ordinary skill in the art
It says, without departing from the inventive concept of the premise, various modifications and improvements can be made, these belong to the protection of the present invention
Range.Therefore, the protection domain of patent of the present invention should be determined by the appended claims.
Claims (10)
1. a kind of resonance fatigue bending machine, which is characterized in that including pedestal (1), left socle (2), intermediate support (3), the right side
Holder (4), flexible support mechanism (5), clamping device (6) and vibration of optical displacement monitor (7), the left socle (2) and
The structure of the right support (4) is identical and is equipped with the flexible support mechanism (5), the clamping device (6) and the optics
Vibration displacement monitoring device (7), the intermediate support (3) are equipped with the vibration of optical displacement monitor (7)；
The both ends of test specimen (8-1) to be measured are fixedly connected by connector (8-4) with vibrator (8-2), clump weight (8-3) respectively,
The test specimen to be measured (8-1), the vibrator (8-2), the clump weight (8-3) and the connector (8-4) constitute Equivalent Beam
Component；
The equivalent beam is connected with the left socle (2) and the right support (4) respectively by the flexible support mechanism (5)
It connects, and the left socle (2) and the right support (4) are connect by the linear guide (9) with the pedestal (1), the left socle
(2) and the right support (4) can be along the axial-movement of the pedestal (1), so that the flexible support mechanism (5) is fixed on institute
At the node location for stating equivalent beam；
The connector (8-4) when the clamping device (6) is for in non-vibration state grips；
The vibration of optical displacement monitor (7) being arranged on the left socle (2) and the right support (4) is for monitoring
The Oscillation Amplitude of the connector (8-4), the vibration of optical displacement monitor being arranged on the intermediate support (3)
(7) it is used to monitor the Oscillation Amplitude of the test specimen to be measured (8-1), and the vibration of optical displacement monitor (7) will monitor
Oscillation Amplitude information be sent to host computer, the host computer controls the vibrator (8-2) according to the Oscillation Amplitude information
Energy input.
2. resonance fatigue bending machine according to claim 1, which is characterized in that
The flexible support mechanism (5) includes the first saddle support (5-1), the second saddle support (5-2) and four flexible cables
(5-3)；
The both ends of first saddle support (5-1) and second saddle support (5-2) are both provided with flexible cable connecting hole,
By the flexible cable connecting hole and two flexible cables (5-3) that first saddle support (5-1) is fixedly connected respectively with it is corresponding
The lower part of holder be fixedly connected, two be fixedly connected with second saddle support (5-2) by the flexible cable connecting hole
Root flexible cable (5-3) is fixedly connected with the top of corresponding holder respectively；
A pair is mounted on first saddle support (5-1) and second saddle support (5-2) can around the shaft certainly
By the roller rotated, the connection is placed between first saddle support (5-1) and second saddle support (5-2)
Part (8-4), and the shaft axis of the roller is parallel with the axis of the connector (8-4), the section of the connector (8-4)
Point contacts at position with each roller line.
3. resonance fatigue bending machine according to claim 2, which is characterized in that
The outer surface of each roller coats one layer of rubber.
4. resonance fatigue bending machine according to claim 2 or 3, which is characterized in that
The flexible cable (5-3) is any one in anchor chain, steel wire rope or cotton rope.
5. the resonance fatigue bending machine according to claims 1 to 3 any one, which is characterized in that
The clamping device (6) includes the first fixture block (6-1), the second fixture block (6-2), line slideway auxiliary (6-3) and feed screw nut
Secondary (6-4)；
First fixture block (6-1) and second fixture block (6-2) are equipped with the work for the connector (8-4) to be clamped
Face, and first fixture block (6-1) and second fixture block (6-2) pass through the line slideway auxiliary (6-3) and corresponding holder
Connection；
The screw pair (6-4) includes leading screw, feed screw nut and the locking nut for being locked to the lead screw, institute
It includes oppositely oriented and helical pitch and the identical two sub- leading screws of head number to state leading screw, and the feed screw nut is mounted on first fixture block
On (6-1) and second fixture block (6-2), described two sub- leading screws coordinate with the feed screw nut and pass through mounting hole (6-1-
1) it is mounted on first fixture block (6-1) and the second fixture block (6-2), the locking nut is arranged on the sub- leading screw.
6. resonance fatigue bending machine according to claim 5, which is characterized in that
First fixture block (6-1) and second fixture block (6-2) are equipped with observation fenestra (6-1-2).
7. the resonance fatigue bending machine according to claims 1 to 3 any one, which is characterized in that
The vibration of optical displacement monitor (7) includes background board (7-1) and optical displacement monitoring modular (7-2), and described
Background board (7-1) and the optical displacement monitoring modular (7-2) are oppositely arranged on the both sides of corresponding holder, the test specimen to be measured
(8-1) or the connector (8-4) are placed between the background board (7-1) and the optical displacement monitoring modular (7-2).
8. the resonance fatigue bending machine according to claims 1 to 3 any one, which is characterized in that
The bottom of the left socle (2) and the right support (4) is equipped with driving screw pair (10), the driving leading screw spiral shell
Female pair (10) includes fixing nut and driving leading screw, and the fixing nut is fixedly connected with the pedestal (1), the driving leading screw
It is connect with the left socle (2) or the right support (4) with merga pass bearing with the fixing nut.
9. the resonance fatigue bending machine according to claims 1 to 3 any one, which is characterized in that
The vibrator (8-2) is the inertia vibration generator of automatically controlled automatic amplitude modulationfrequency modulation, and the inertia vibration generator includes a pair of of structure
The slewing equipment (8-2-1) with eccentric mass and a pair identical and be fixedly secured to one another are used to drive the same of the slewing equipment
Walk motor servo driver (8-2-2).
10. the resonance fatigue bending machine according to claims 1 to 3 any one, which is characterized in that
The connector (8-4) is cylindrical or cylindrical shape.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810171221.3A CN108362586B (en) | 2018-03-01 | 2018-03-01 | Resonance bending fatigue testing machine |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810171221.3A CN108362586B (en) | 2018-03-01 | 2018-03-01 | Resonance bending fatigue testing machine |
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| CN108362586B CN108362586B (en) | 2020-05-05 |
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Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109900790A (en) * | 2019-03-22 | 2019-06-18 | 东北大学 | It is a kind of based on the composite material dynamic fatigue test device and method reversely to resonate |
| CN110174226A (en) * | 2019-06-17 | 2019-08-27 | 中机试验装备股份有限公司 | A kind of pipeline resonance fatigue test board |
| CN111458241A (en) * | 2020-03-11 | 2020-07-28 | 天津大学 | Servo coaxial dual-drive inertia vibration exciter |
| CN112051043A (en) * | 2020-08-28 | 2020-12-08 | 江西理工大学 | Fatigue test system for compliant mechanism |
| CN113496644A (en) * | 2021-07-07 | 2021-10-12 | 吉林大学 | Portable vibration teaching experiment table |
| CN113514355A (en) * | 2021-04-23 | 2021-10-19 | 中国石油大学(华东) | Resonance bending fatigue testing machine for oil-gas pipe column |
| CN113899617A (en) * | 2021-09-28 | 2022-01-07 | 天津大学 | Fulcrum position adjusting device for full-size pipeline resonance bending fatigue testing machine |
| CN114942192A (en) * | 2022-05-30 | 2022-08-26 | 赋桦科技(深圳)有限公司 | Automatic detection device for PCB pressure test |
Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2009005678A1 (en) * | 2007-06-27 | 2009-01-08 | Corning Incorporated | Methods and apparatus for measuring elastic modulus of non-solid ceramic materials by resonance |
| CN101666730A (en) * | 2009-09-14 | 2010-03-10 | 中国人民解放军海军工程大学 | Equipment for testing vibration performance of air spring and method of using the same for testing |
| CN202562796U (en) * | 2012-05-16 | 2012-11-28 | 杭州欧佩亚海洋工程有限公司 | Resonance bending type fatigue testing machine |
| CN203178147U (en) * | 2013-02-05 | 2013-09-04 | 天津天东恒科技发展有限公司 | Sub-ultrasonic high frequency fatigue testing machine |
| CN203421109U (en) * | 2013-08-07 | 2014-02-05 | 李涛 | Flexible supporting structure for ultrasonic transducer |
| CN203465164U (en) * | 2013-09-06 | 2014-03-05 | 宝鸡石油机械有限责任公司 | Steel pipe bending fatigue testing machine |
| CN103926154A (en) * | 2014-04-25 | 2014-07-16 | 西安利尔石油工程技术有限公司 | Device for testing bending fatigue of oil casing under complex load |
| WO2014161858A1 (en) * | 2013-04-03 | 2014-10-09 | Onderzoekscentrum Voor Aanwending Van Staal N.V. | Fatigue testing of a test specimen |
| CN106248509A (en) * | 2016-08-30 | 2016-12-21 | 吉林大学 | Resonant sleeper fatigue bending machine and application thereof |
| CN106442133A (en) * | 2016-10-08 | 2017-02-22 | 大连理工大学 | Oceanographic engineering flexible tube cable stretching bending combination experimental facility and experimental method |
-
2018
- 2018-03-01 CN CN201810171221.3A patent/CN108362586B/en not_active Expired - Fee Related
Patent Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2009005678A1 (en) * | 2007-06-27 | 2009-01-08 | Corning Incorporated | Methods and apparatus for measuring elastic modulus of non-solid ceramic materials by resonance |
| CN101666730A (en) * | 2009-09-14 | 2010-03-10 | 中国人民解放军海军工程大学 | Equipment for testing vibration performance of air spring and method of using the same for testing |
| CN202562796U (en) * | 2012-05-16 | 2012-11-28 | 杭州欧佩亚海洋工程有限公司 | Resonance bending type fatigue testing machine |
| CN203178147U (en) * | 2013-02-05 | 2013-09-04 | 天津天东恒科技发展有限公司 | Sub-ultrasonic high frequency fatigue testing machine |
| WO2014161858A1 (en) * | 2013-04-03 | 2014-10-09 | Onderzoekscentrum Voor Aanwending Van Staal N.V. | Fatigue testing of a test specimen |
| CN203421109U (en) * | 2013-08-07 | 2014-02-05 | 李涛 | Flexible supporting structure for ultrasonic transducer |
| CN203465164U (en) * | 2013-09-06 | 2014-03-05 | 宝鸡石油机械有限责任公司 | Steel pipe bending fatigue testing machine |
| CN103926154A (en) * | 2014-04-25 | 2014-07-16 | 西安利尔石油工程技术有限公司 | Device for testing bending fatigue of oil casing under complex load |
| CN106248509A (en) * | 2016-08-30 | 2016-12-21 | 吉林大学 | Resonant sleeper fatigue bending machine and application thereof |
| CN106442133A (en) * | 2016-10-08 | 2017-02-22 | 大连理工大学 | Oceanographic engineering flexible tube cable stretching bending combination experimental facility and experimental method |
Non-Patent Citations (1)
| Title |
|---|
| 刘学飞: "梁形构件的弯曲共振实现方法及应用研究", 《中国优秀硕士学位论文全文数据库 工程科技Ⅱ辑》 * |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109900790A (en) * | 2019-03-22 | 2019-06-18 | 东北大学 | It is a kind of based on the composite material dynamic fatigue test device and method reversely to resonate |
| CN110174226A (en) * | 2019-06-17 | 2019-08-27 | 中机试验装备股份有限公司 | A kind of pipeline resonance fatigue test board |
| CN111458241A (en) * | 2020-03-11 | 2020-07-28 | 天津大学 | Servo coaxial dual-drive inertia vibration exciter |
| CN112051043A (en) * | 2020-08-28 | 2020-12-08 | 江西理工大学 | Fatigue test system for compliant mechanism |
| CN113514355A (en) * | 2021-04-23 | 2021-10-19 | 中国石油大学(华东) | Resonance bending fatigue testing machine for oil-gas pipe column |
| CN113496644A (en) * | 2021-07-07 | 2021-10-12 | 吉林大学 | Portable vibration teaching experiment table |
| CN113496644B (en) * | 2021-07-07 | 2022-10-11 | 吉林大学 | Portable vibration teaching experiment table |
| CN113899617A (en) * | 2021-09-28 | 2022-01-07 | 天津大学 | Fulcrum position adjusting device for full-size pipeline resonance bending fatigue testing machine |
| CN114942192A (en) * | 2022-05-30 | 2022-08-26 | 赋桦科技(深圳)有限公司 | Automatic detection device for PCB pressure test |
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