CN105738100A - Hydro-pneumatic spring performance testing system and testing method - Google Patents
Hydro-pneumatic spring performance testing system and testing method Download PDFInfo
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- CN105738100A CN105738100A CN201610256693.XA CN201610256693A CN105738100A CN 105738100 A CN105738100 A CN 105738100A CN 201610256693 A CN201610256693 A CN 201610256693A CN 105738100 A CN105738100 A CN 105738100A
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Abstract
The invention discloses a hydro-pneumatic spring performance testing system and testing method. The hydro-pneumatic spring performance testing system comprises a testing stand, a servo motor, a servo driver, a fuel tank, a kinetic-hydraulic energy conversion element, two-position two-way reversing valve, a loading hydraulic cylinder, a force sensor, a displacement sensor and a control cabinet. The servo motor drives the kinetic-hydraulic energy conversion element, and the kinetic-hydraulic energy conversion element drives the loading hydraulic cylinder to load a hydro-pneumatic spring. The problem of energy loss due to proportion/servo valve throttling is solved, non-throttling movement control of the loading hydraulic cylinder is realized, and the working efficiency of the system is improved. The energy of the hydro-pneumatic spring is converted into electric energy through the loading hydraulic cylinder, the kinetic-hydraulic energy conversion element, the servo motor and the servo driver, and the electric energy is returned back to a system power grid, thereby realizing energy recovery of the hydro-pneumatic spring. The working efficiency of the system is high, good energy saving effect is realized, and hydro-pneumatic temperature rise can be effectively prevented.
Description
Technical field
The application relates to hydraulic testing platform technical field, particularly relates to a kind of hydro-pneumatic spring performance test system
System and test method.
Background technology
Hydro-pneumatic spring is the non-linear elastic element carrying out power transmission using gas as elastic fluid with fluid,
There is excellent damping behavior, be more and more applied to various vehicle, the most bridges, heavy loading car,
As vehicle suspension component, it is ensured that vehicle all can have good ride performance under various loads.Oil
The performance quality of air spring performance will directly affect the normal traveling of vehicle, and its superior and inferior evaluating is generally by two spies
Property index is evaluated: one is the resistance Changing Pattern with operating rate, referred to as speed characteristics；Two is resistance
With the Changing Pattern of stroke, referred to as indicator card.The performance of test oil air spring must be given by formation testing on request
Air spring loads.It is the loading method currently mainly used that top is loaded by ratio/servo hydraulic cylinder.
Ratio/servo hydraulic cylinder is to top loading method, and control method is ripe, but the problem being primarily present has:
The oil sources of ratio/servo hydraulic cylinder needs to determine according to tested hydro-pneumatic spring EIAJ and maximum stream flow,
And the flow of ratio/servo valve is relevant with valve pressure reduction, owing to the restriction loss of ratio/servo valve result in loading
Ratio/servo hydraulic cylinder system itself inefficient；From the point of view of hydro-pneumatic spring, although exist elastic non-
Linear characteristic, but its key property or a spring performance, i.e. absorbed by deformation and store energy,
Apply pumping signal to tested hydro-pneumatic spring by loading ratio/servo hydraulic cylinder in hydro-pneumatic spring is tested,
Absorbing and store energy from loading ratio/servo hydraulic cylinder during hydro-pneumatic spring compression, during stretching, extension, hydro-pneumatic spring is released
Exoergic is to loading ratio/servo hydraulic cylinder the heat energy that is changed to hydraulic oil by the circulation of ratio/servo valve warp knuckle
And consume, this does not only results in energy loss and also results in the rapid increase of oil temperature.
Summary of the invention
The purpose of the application is to provide a kind of hydro-pneumatic spring performance test system and test method, above-mentioned to solve
The problem that prior art exists, makes system hydro-pneumatic spring can carry out static state, dynamically and continuously load, and
And, in loading procedure, without restriction loss, energy when hydro-pneumatic spring stretches is capable of reclaiming, significantly
The restriction loss of reduction system, reduces fluid temperature rise, improves system energy utilization rate, accomplishes efficient energy-saving.
For achieving the above object, this application provides following scheme: the application provides a kind of hydro-pneumatic spring performance
Pilot system, comprising: test-bed, servomotor, servo-driver, fuel tank, kinetic energy-hydraulic energy
Conversion element, lead to reversal valve, loading hydraulic cylinder, force transducer, displacement transducer and switch board for 22；
Described servo-driver has feeding function, and described servo-driver electrically connects with described servomotor；
Described servomotor has rotating forward and drags and reversion loading function, and the output shaft of described servomotor is dynamic with described
The drive shaft of energy-hydraulic energy conversion element connects；The inlet port of described kinetic energy-hydraulic energy conversion element is connected to
Fuel tank, the delivery outlet of described kinetic energy-hydraulic energy conversion element leads to reversal valve through described 22 and adds with described
The rodless cavity hydraulic fluid port of carrier fluid cylinder pressure connects；Described loading hydraulic cylinder is arranged on described test-bed；Described 2
Position 2 leads to reversal valve and is controlled commutation by described switch board；
Described force transducer is arranged on the piston rod of described loading hydraulic cylinder；Institute's displacement sensors is embedded in
Inside loading hydraulic cylinder, or, institute's displacement sensors is arranged on described test-bed；Described force transducer
With displacement transducer, signal being fed back to described switch board, described switch board is according to described force transducer and displacement
The feedback signal of sensor controls the turning to of described servomotor, rotating speed and torsion by described servo-driver
Square.
As a preferred version, described hydro-pneumatic spring performance test system also includes: low discharge auxiliary feed-oil
Loop, described low discharge auxiliary feed-oil loop includes: auxiliary feed-oil hydraulic pump, 23 lead to reversal valve,
One relief valve and pressure transducer；The inlet port of described auxiliary feed-oil hydraulic pump is connected to described fuel tank, described
The delivery outlet of auxiliary feed-oil hydraulic pump is through described 23 rod chambers leading to reversal valve and described loading hydraulic cylinder
Hydraulic fluid port connects；Described pressure transducer is arranged on the rod chamber oil port of described loading hydraulic cylinder, described pressure
Signal is fed back to described switch board by sensor；Described first relief valve is arranged on described 23 and leads to reversal valve
And on the pipeline between described loading hydraulic cylinder rod chamber hydraulic fluid port, the drain tap of described first relief valve is with described
Fuel tank connects, and the safety value of described first relief valve is fed back according to described pressure transducer by described switch board
Signal is set；Described 23 lead to reversal valve by the control commutation of described switch board.
As a preferred version, described hydro-pneumatic spring performance test system also includes loop of boosting, described dynamic
The inlet port of energy-hydraulic energy conversion element is connected to described fuel tank by described boosting loop；Described liter pushes back
Road includes: the second relief valve, check valve and boosting hydraulic pump；The inlet port of described boosting hydraulic pump is connected to
Described fuel tank, the delivery outlet of described boosting hydraulic pump is through described check valve and described kinetic energy-hydraulic energy conversion
The inlet port of element connects；Described second relief valve is arranged on described check valve and turns with described kinetic energy-hydraulic energy
Changing on the pipeline between element, the drain tap of described relief valve is connected with described fuel tank.
As a preferred version, described hydro-pneumatic spring performance test system also includes the 3rd relief valve, described
3rd relief valve be arranged on the delivery outlet of described kinetic energy-hydraulic energy conversion element and 22 lead between reversal valve
Pipeline on, the drain tap of described 3rd relief valve is connected with described fuel tank, the safety of described 3rd relief valve
Value is set by described switch board.
Further, described kinetic energy-hydraulic energy conversion element is hydraulic pump, hydraulic motor or hydraulic pressure Quadratic Finite Element
Any one of part.
Further, described loading hydraulic cylinder is single rod asymmetrical cylinder.
Further, described servomotor is AC servo motor, alternating-current variable frequency motor or DC servo motor,
Described servo-driver and described servomotor type matching.
Use a kind of hydro-pneumatic spring method for testing performance of above-mentioned hydro-pneumatic spring performance test system, including as follows
Step:
Pilot system starts: switch board powers on, and 22 lead to reversal valve and are in power failure state, start servo and drive
Dynamic device, sets the rotating speed of servomotor as 0 rev/min；
Compressed oil air spring: switch board controls 22 to lead to reversal valve and obtains electric, and switch board passes through servo-driver
Controlling servomotor to rotate forward, driven by servomotor kinetic energy-hydraulic energy conversion element rotates forward, and kinetic energy-hydraulic energy turns
Change element drives fluid and lead to reversal valve to loading hydraulic cylinder rodless cavity, loading hydraulic cylinder driving work through 22
Stopper rod rises, and piston rod makes hydro-pneumatic spring be compressed to setting position, and system converts electrical energy in this course
For the potential energy of hydro-pneumatic spring, force transducer and displacement transducer, measurement signal is fed back to switch board；
Extension oil air spring: switch board controls 22 to lead to reversal valve and obtains electric, and loading hydraulic cylinder piston rod is at oil
Declining under the pressure effect of air spring, fluid leads to reversal valve through 22 and drives kinetic energy-hydraulic energy conversion first
Part inverts, and kinetic energy-hydraulic energy conversion element drives servomotor reversion generating, meanwhile, according to oil gas
The rate of stretch requirement of spring, switch board controls the rotating speed of servomotor by servo-driver, in this mistake
In journey, to be electric energy by the potential energy of hydro-pneumatic spring fed back to electrical network by servo-driver to system, force transducer and
Measurement signal is fed back to switch board by displacement transducer；
Circulating pressure is tested: switch board is according to compressed oil air spring and the mode of operation of extension oil air spring, instead
Compound compression and extension oil air spring；Switch board does with the FREQUENCY CONTROL hydro-pneumatic spring of 3-4 beat/min and comes and goes fortune
Dynamic, the measurement signal that switch board feeds back according to force transducer carries out power closed loop control, it is ensured that force transducer defeated
Go out value rule change between the first setting and the second setting；Test period is 30 minutes；
Pressurize is tested: switch board is according to the mode of operation of compressed oil air spring, controlled loading hydraulic cylinder compressed oil
Air spring, makes force transducer output valve reach setting value；Then switch board controls 22 to lead to reversal valve dead electricity,
Keep 10 minutes；Then switch board controls servomotor with perseverance torsion according to the mode of operation of extension oil air spring
Square inverts, and permanent torque value is maintained at 0N m, and ensures that the piston rod of hydro-pneumatic spring freely declines, and measures
And record hydro-pneumatic spring and recover to time of the fully extended state；Repeat pressurize to test 5 times；
Dynamic characteristic test: switch board, will according to compressed oil air spring and the mode of operation of extension oil air spring
The measurement signal of displacement transducer as feedback signal constitute outer shroud control loop, using servomotor rotating speed as
Internal ring controls loop, centered by setting position, controls hydro-pneumatic spring with the frequency set and the displacement of setting
Doing back and forth movement, it is bent with the positional value of displacement transducer that the output valve of force transducer is measured and recorded to switch board
Line, obtains speed characteristics and the indicator card of hydro-pneumatic spring.
The specific embodiment provided according to the application, this application discloses techniques below effect: the application passes through
Use driven by servomotor kinetic energy-hydraulic energy conversion element, kinetic energy-hydraulic energy conversion element drive load hydraulic pressure
The loading to hydro-pneumatic spring implemented by cylinder, solves in the hydraulic cylinder loading method of adoption rate/servo valve control,
The energy loss caused due to ratio/servo valve throttling, it is achieved that the nothing throttling motor control of loading hydraulic cylinder,
Improve the work efficiency of system.And the energy of hydro-pneumatic spring is converted to liquid by loading hydraulic cylinder by the present invention
Pressure energy, then hydraulic energy is converted to kinetic energy by kinetic energy-hydraulic energy conversion element, then by servomotor with
And servo-driver converts kinetic energy into electric energy, then electric energy is returned to system power supply electrical network, it is achieved that to oil
The recovery of air spring energy.Compared with ratio/servo valve control cylinder mode loading method, under declared working condition it is
The efficiency of system can improve more than 80%, has significant energy-saving effect, can be prevented effectively from system oil liquid temperature liter.
Accompanying drawing explanation
In order to be illustrated more clearly that the embodiment of the present application or technical scheme of the prior art, below will be to enforcement
In example, the required accompanying drawing used is briefly described, it should be apparent that, the accompanying drawing in describing below is only
Some embodiments of the application, for those of ordinary skill in the art, are not paying creative work
On the premise of, it is also possible to other accompanying drawing is obtained according to these accompanying drawings.
The embodiment system schematic that Fig. 1 provides for the application；
Wherein, 1 is test-bed, and 2 is hydro-pneumatic spring, and 3 is force transducer, and 4 is loading hydraulic cylinder, 5
For displacement transducer, 6 is the first relief valve, and 7 are 23 leads to reversal valve, and 8 is auxiliary feed-oil hydraulic pump,
9 is boosting loop, and 10 is kinetic energy-hydraulic energy conversion element, and 11 is the 3rd relief valve, and 12 is 22
Logical reversal valve, 13 is servomotor, and 14 is servo-driver, and 15 is pressure transducer, and 16 for controlling
Cabinet.
Detailed description of the invention
Below in conjunction with the accompanying drawing in the embodiment of the present application, the technical scheme in the embodiment of the present application is carried out clearly
Chu, be fully described by, it is clear that described embodiment be only some embodiments of the present application rather than
Whole embodiments.Based on the embodiment in the application, those of ordinary skill in the art are not making creation
Property work premise under the every other embodiment that obtained, broadly fall into the scope of the application protection.
The purpose of the application is to provide a kind of hydro-pneumatic spring performance test system and test method, above-mentioned to solve
The problem that prior art exists, makes system hydro-pneumatic spring 2 can be carried out static state, dynamically and continuously be loaded,
And, in loading procedure, without restriction loss, energy when hydro-pneumatic spring 2 stretches is capable of reclaiming,
It is substantially reduced the restriction loss of system, reduces fluid temperature rise, improve system energy utilization rate, accomplish energy-conservation height
Effect.
Understandable for enabling the above-mentioned purpose of the application, feature and advantage to become apparent from, below in conjunction with the accompanying drawings and
The application is described in further detail by detailed description of the invention.
This application provides a kind of hydro-pneumatic spring performance test system, comprising: test-bed 1, servo are electric
Machine 13, servo-driver 14, fuel tank, kinetic energy-hydraulic energy conversion element 10,22 lead to reversal valve 12,
Loading hydraulic cylinder 4, force transducer 3, displacement transducer 5 and switch board 16；
Described servo-driver 14 has feeding function, described servo-driver 14 and described servomotor
13 electrical connections；Described servomotor 13 has rotating forward and drags and reversion loading function, described servomotor 13
Output shaft be connected with the drive shaft of described kinetic energy-hydraulic energy conversion element 10；Described kinetic energy-hydraulic energy turns
The inlet port changing element 10 is connected to fuel tank, and the delivery outlet of described kinetic energy-hydraulic energy conversion element 10 passes through
Described 22 lead to reversal valve 12 and are connected with the rodless cavity hydraulic fluid port of described loading hydraulic cylinder 4；Described with carrier fluid
Cylinder pressure 4 is arranged on described test-bed 1；Described 22 lead to reversal valve 12 by described switch board 16
Control commutation；
Described force transducer 3 is arranged on the piston rod of described loading hydraulic cylinder 4；Institute's displacement sensors 5
It is embedded in loading hydraulic cylinder 4 internal, or, institute's displacement sensors 5 is arranged on described test-bed 1；
Signal is fed back to described switch board 16, described switch board 16 by described force transducer 3 and displacement transducer 5
Feedback signal according to described force transducer 3 and displacement transducer 5 is controlled by described servo-driver 14
The turning to of described servomotor 13, rotating speed and moment of torsion.
The application drives kinetic energy-hydraulic energy conversion element 10, kinetic energy-hydraulic energy by using servomotor 13
Conversion element 10 drive load hydraulic cylinder 4 implements the loading to hydro-pneumatic spring 2, solve adoption rate/
In the hydraulic cylinder loading method of servo valve control, the energy loss caused due to ratio/servo valve throttling, real
Show the nothing throttling motor control of loading hydraulic cylinder 4, improve the work efficiency of system.And the present invention passes through
The energy of hydro-pneumatic spring 2 is converted to hydraulic energy by loading hydraulic cylinder 4, more first by kinetic energy-hydraulic energy conversion
Hydraulic energy is converted to kinetic energy by part 10, then is turned by kinetic energy by servomotor 13 and servo-driver 14
It is changed to electric energy, then electric energy is returned to system power supply electrical network, it is achieved that the recovery to the energy of hydro-pneumatic spring 2.
Compared with ratio/servo hydraulic cylinder loading method, under declared working condition, the efficiency of system can improve more than 80%,
There is significant energy-saving effect, system oil liquid temperature liter can be prevented effectively from.
When hydro-pneumatic spring 2 carries out pressurize test, switch board 16 leads to reversal valve 12 by operation 22
Commutation, it is achieved that the rodless cavity of loading hydraulic cylinder 4 is closed, and then meet hydro-pneumatic spring 2 long-time pressurize examination
Test requirement.The power of servomotor 13 can be cut off in this case, to reduce the energy consumption of system further.
Such as: assume that the power of the system of the application and traditional ratio/servo hydraulic cylinder loading method is
500KW, when being circulated test under declared working condition, traditional ratio/servo hydraulic cylinder loading method is in pressure
When contracting hydro-pneumatic spring 2 and extension oil air spring 2, in the unit interval, consume the energy of 500KW h respectively,
Consume the energy of 1000KW h altogether.And the efficiency of the servo-driver 14 of the application is typically not less than 96%,
The efficiency of servomotor 13 is typically not less than 95%, and the efficiency of kinetic energy-hydraulic energy conversion element 10 is general not
Less than 90%, pipeline loss is generally not more than 1%, and the efficiency of loading hydraulic cylinder 4 is typically not less than 96%, meter
Calculating and understand, the total work efficiency of the application is not less than 96% × 95% × 90% × (1-1%) × 96%=78%.
Calculating and understand, the application will be no less than 500KW h × 78%=390KW h's when compressed oil air spring 2
Energy transmission gives hydro-pneumatic spring 2 as potential energy storage, and will be no less than when upholding hydro-pneumatic spring 2
The energy of 390KW h × 78%=304KW h is converted to electric energy and returns to system power supply electrical network, working unit
Time total energy consumption is 500KW h-304KW h=196KW h.The application is relative to traditional ratio/servo
Hydraulic cylinder loading method decreases at least the energy of (1000KW h-196KW h)/1000KW h=80.4%
Consume.So, compared with ratio/servo hydraulic cylinder loading method, the application is system under declared working condition
Efficiency can improve more than 80%.
As a preferred version, described hydro-pneumatic spring performance test system also includes: low discharge auxiliary feed-oil
Loop, described low discharge auxiliary feed-oil loop includes: auxiliary feed-oil hydraulic pump 8,23 lead to reversal valve 7,
First relief valve 6 and pressure transducer 15；The inlet port of described auxiliary feed-oil hydraulic pump 8 is connected to described
Fuel tank, the delivery outlet of described auxiliary feed-oil hydraulic pump 8 leads to reversal valve 7 and described loading through described 23
The rod chamber hydraulic fluid port of hydraulic cylinder 4 connects；Described pressure transducer 15 is arranged on described loading hydraulic cylinder 4
Rod chamber oil port, signal is fed back to described switch board 16 by described pressure transducer 15；Described first peace
Full valve 6 is arranged on described 23 pipes led between reversal valve 7 and described loading hydraulic cylinder 4 rod chamber hydraulic fluid port
Lu Shang, the drain tap of described first relief valve 6 is connected with described fuel tank, the safety of described first relief valve 6
The signal that value is fed back according to described pressure transducer 15 by described switch board 16 is set；Described 23
Logical reversal valve 7 is controlled commutation by described switch board 16.Described low discharge auxiliary feed-oil loop is mainly used in:
When loading hydraulic cylinder 4 cannot be retracted voluntarily, the retraction operation of secondary load hydraulic cylinder 4；Carrying out oil gas
During spring 2 Dynamic performance examination, compensate hydro-pneumatic spring 2 undercapacity, to improve the dynamic response speed of system
Degree.
As a preferred version, described hydro-pneumatic spring performance test system also includes loop 9 of boosting, described
The inlet port of kinetic energy-hydraulic energy conversion element 10 is connected to described fuel tank by described boosting loop 9；Described
Boosting loop 9 includes: the second relief valve, check valve and boosting hydraulic pump；The oil suction of described boosting hydraulic pump
Mouth is connected to described fuel tank, and the delivery outlet of described boosting hydraulic pump is through described check valve and described kinetic energy-liquid
The inlet port of pressure energy conversion element 10 connects；It is dynamic with described that described second relief valve is arranged on described check valve
On pipeline between energy-hydraulic energy conversion element 10, the drain tap of described relief valve is connected with described fuel tank.
For improving the kinetic energy-hydraulic energy conversion element 10 oil suction state when pump condition, in case kinetic energy-hydraulic energy
Conversion element 10 is emptied.
As a preferred version, described hydro-pneumatic spring performance test system also includes the 3rd relief valve 11,
Described 3rd relief valve 11 be arranged on the delivery outlet of described kinetic energy-hydraulic energy conversion element 10 and 22 lead to
On pipeline between reversal valve 12, the drain tap of described 3rd relief valve 11 is connected with described fuel tank；Described
The safety value of the 3rd relief valve 11 by described switch board 16 according to described force transducer 3 and displacement transducer 5
Feedback signal set.Described 3rd relief valve 11 is used for protecting kinetic energy-hydraulic energy conversion element 10 to work
In the range of safe pressure.
Further, described kinetic energy-hydraulic energy conversion element 10 is hydraulic pump, hydraulic motor or hydraulic pressure secondary
Any one of element.
Further, described loading hydraulic cylinder 4 is single rod asymmetrical cylinder.
Further, described servomotor 13 is AC servo motor, alternating-current variable frequency motor or DC servo
Any one of motor, described servo-driver 14 and described servomotor 13 type matching.
Use a kind of hydro-pneumatic spring method for testing performance of above-mentioned hydro-pneumatic spring performance test system, including as follows
Step:
Pilot system starts: switch board 16 powers on, and 22 lead to reversal valve 12 and are in power failure state, starts
Servo-driver 14, sets the rotating speed of servomotor 13 as 0 rev/min；
Compressed oil air spring: switch board 16 controls 22 to lead to reversal valve 12 and obtains electric, and switch board 16 passes through
Servo-driver 14 controls servomotor 13 and rotates forward, and servomotor 13 drives kinetic energy-hydraulic energy conversion element
10 rotate forward, and kinetic energy-hydraulic energy conversion element 10 drives fluid to lead to reversal valve 12 to carrier fluid through 22
Cylinder pressure 4 rodless cavity, loading hydraulic cylinder 4 drives piston rod to rise, and piston rod makes hydro-pneumatic spring 2 be compressed to set
Location is put, and system converts electrical energy into the potential energy of hydro-pneumatic spring 2, force transducer 3 and position in this course
Measurement signal is fed back to switch board 16 by displacement sensor 5；
Extension oil air spring: switch board 16 controls 22 to lead to reversal valve 12 and obtains electric, loading hydraulic cylinder 4
Piston rod declines under the pressure effect of hydro-pneumatic spring 2, and fluid leads to reversal valve 12 through 22 and drives dynamic
Energy-hydraulic energy conversion element 10 inverts, and kinetic energy-hydraulic energy conversion element 10 drives servomotor 13 to invert
Generating, meanwhile, according to the rate of stretch requirement of hydro-pneumatic spring 2, switch board 16 passes through servo-drive
Device 14 controls the rotating speed of servomotor 13, and the potential energy of hydro-pneumatic spring 2 is electricity by system in the process
And can feed back to electrical network, when hydro-pneumatic spring 2 is stretched over setting position, servomotor 13 stops operating, power
Measurement signal is fed back to switch board 16 by sensor 3 and displacement transducer 5, for the position of hydro-pneumatic spring 2
Put the control with pressure；
Circulating pressure test: switch board 16 according to compressed oil air spring and the mode of operation of extension oil air spring,
Repeated Compression and extension oil air spring 2；Switch board 16 is with the FREQUENCY CONTROL hydro-pneumatic spring 2 of 3-4 beat/min
Doing back and forth movement, switch board 16 carries out power closed loop control according to the measurement signal that force transducer 3 feeds back, and protects
The rule change between the first setting and the second setting of the output valve of card force transducer 3；Test period is
30 minutes；
Pressurize is tested: switch board 16 is according to the mode of operation of compressed oil air spring, controlled loading hydraulic cylinder 4
Compressed oil air spring 2, makes force transducer 3 output valve reach setting value；Then switch board 16 controls 22
Logical reversal valve 12 dead electricity, makes the output valve of force transducer 3 be maintained at setting value 10 minutes；Then switch board
16 control servomotor 13 according to the mode of operation of extension oil air spring uses up with permanent torque reversal, permanent torque value
Amount is maintained at 0N m and freely declines be as the criterion with the piston rod ensureing hydro-pneumatic spring 2, measures and records oil gas
Spring 2 recovers the time to the fully extended state；Repeat pressurize to test at least 5 times；
Dynamic characteristic test: switch board 16 according to compressed oil air spring and the mode of operation of extension oil air spring,
The measurement signal of displacement transducer 5 is constituted outer shroud as feedback signal and controls loop, by servomotor 13
Rotating speed controls loop as internal ring, centered by setting position, controls the hydro-pneumatic spring 2 frequency with regulation,
Generally between 0.1-2Hz, and regulation shift length does back and forth movement, and switch board 16 is measured and records power
The output valve of sensor 3 and the shift value curve of displacement transducer 16；The speed obtaining hydro-pneumatic spring 2 is special
Property and indicator card.
In this specification, each embodiment uses the mode gone forward one by one to describe, and what each embodiment stressed is
With the difference of other embodiments, between each embodiment, identical similar portion sees mutually.For
For system disclosed in embodiment, owing to it corresponds to the method disclosed in Example, so the comparison described
Simply, relevant part sees method part and illustrates.
Principle and the embodiment of the application are set forth by specific case used herein, above enforcement
The explanation of example is only intended to help and understands the present processes and core concept thereof；Simultaneously for this area
Those skilled in the art, according to the thought of the application, the most all can change
Part.In sum, this specification content should not be construed as the restriction to the application.
Claims (8)
1. a hydro-pneumatic spring performance test system, it is characterised in that: including: test-bed, servo electricity
Machine, servo-driver, fuel tank, kinetic energy-hydraulic energy conversion element, lead to reversal valve, add load hydraulic for 22
Cylinder, force transducer, displacement transducer and switch board；
Described servo-driver has feeding function, and described servo-driver electrically connects with described servomotor；
Described servomotor has rotating forward and drags and reversion loading function, and the output shaft of described servomotor is dynamic with described
The drive shaft of energy-hydraulic energy conversion element connects；The inlet port of described kinetic energy-hydraulic energy conversion element is connected to
Fuel tank, the delivery outlet of described kinetic energy-hydraulic energy conversion element leads to reversal valve through described 22 and adds with described
The rodless cavity hydraulic fluid port of carrier fluid cylinder pressure connects；Described loading hydraulic cylinder is arranged on described test-bed；Described 2
Position 2 leads to reversal valve and is controlled commutation by described switch board；
Described force transducer is arranged on the piston rod of described loading hydraulic cylinder；Institute's displacement sensors is embedded in
Inside loading hydraulic cylinder, or, institute's displacement sensors is arranged on described test-bed；Described force transducer
With displacement transducer, signal being fed back to described switch board, described switch board is according to described force transducer and displacement
The feedback signal of sensor controls the turning to of described servomotor, rotating speed and torsion by described servo-driver
Square.
Hydro-pneumatic spring performance test system the most according to claim 1, it is characterised in that: also include:
Low discharge auxiliary feed-oil loop, described low discharge auxiliary feed-oil loop includes: auxiliary feed-oil hydraulic pump, 2
3 lead to reversal valve, the first relief valve and pressure transducer；The inlet port of described auxiliary feed-oil hydraulic pump is connected to
Described fuel tank, the delivery outlet of described auxiliary feed-oil hydraulic pump leads to reversal valve and described loading through described 23
The rod chamber hydraulic fluid port of hydraulic cylinder connects；Described pressure transducer is arranged on the rod chamber oil of described loading hydraulic cylinder
At Kou, signal is fed back to described switch board by described pressure transducer；Described first relief valve is arranged on described
Lead to for 23 on the pipeline between reversal valve and described loading hydraulic cylinder rod chamber hydraulic fluid port, described first relief valve
Drain tap be connected with described fuel tank, the safety value of described first relief valve by described switch board according to described pressure
The signal of force transducer feedback is set；Described 23 lead to reversal valve by the control commutation of described switch board.
Hydro-pneumatic spring performance test system the most according to claim 1, it is characterised in that: also include
Boosting loop, the inlet port of described kinetic energy-hydraulic energy conversion element is connected to described by described boosting loop
Fuel tank；Described boosting loop includes: the second relief valve, check valve and boosting hydraulic pump；Described boosting hydraulic pressure
The inlet port of pump is connected to described fuel tank, the delivery outlet of described boosting hydraulic pump through described check valve with described
The inlet port of kinetic energy-hydraulic energy conversion element connects；Described second relief valve is arranged on described check valve and institute
Stating on the pipeline between kinetic energy-hydraulic energy conversion element, the drain tap of described relief valve is connected with described fuel tank.
Hydro-pneumatic spring performance test system the most according to claim 1, it is characterised in that: also include
3rd relief valve, described 3rd relief valve is arranged on the delivery outlet and 2 of described kinetic energy-hydraulic energy conversion element
Position 2 leads on the pipeline between reversal valve, and the drain tap of described 3rd relief valve is connected with described fuel tank, described
The safety value of the 3rd relief valve by described switch board according to described force transducer and the feedback letter of displacement transducer
Number set.
Hydro-pneumatic spring performance test system the most according to claim 1, it is characterised in that: described dynamic
Energy-hydraulic energy conversion element is any one of hydraulic pump, hydraulic motor or hydraulic secondary component.
Hydro-pneumatic spring performance test system the most according to claim 1, it is characterised in that add described in:
Carrier fluid cylinder pressure is single rod asymmetrical cylinder.
Hydro-pneumatic spring performance test system the most according to claim 1, it is characterised in that watch described in:
Taking motor is AC servo motor, alternating-current variable frequency motor or DC servo motor, described servo-driver and institute
State servomotor type matching.
8. using a kind of hydro-pneumatic spring method for testing performance of system as claimed in claim 1, its feature exists
In: comprise the steps:
Pilot system starts: switch board powers on, and 22 lead to reversal valve and are in power failure state, start servo and drive
Dynamic device, sets the rotating speed of servomotor as 0 rev/min；
Compressed oil air spring: switch board controls 22 to lead to reversal valve and obtains electric, and switch board passes through servo-driver
Controlling servomotor to rotate forward, driven by servomotor kinetic energy-hydraulic energy conversion element rotates forward, and kinetic energy-hydraulic energy turns
Change element drives fluid and lead to reversal valve to loading hydraulic cylinder rodless cavity, loading hydraulic cylinder driving work through 22
Stopper rod rises, and piston rod makes hydro-pneumatic spring be compressed to setting position, and system converts electrical energy in this course
For the potential energy of hydro-pneumatic spring, force transducer and displacement transducer, measurement signal is fed back to switch board, for oil
Air spring position and the control of pressure；
Extension oil air spring: switch board controls 22 to lead to reversal valve and obtains electric, and loading hydraulic cylinder piston rod is at oil
Declining under the pressure effect of air spring, fluid leads to reversal valve through 22 and drives kinetic energy-hydraulic energy conversion first
Part inverts, and kinetic energy-hydraulic energy conversion element drives servomotor reversion generating, meanwhile, according to oil gas
The rate of stretch requirement of spring, switch board controls the rotating speed of servomotor by servo-driver, in this process
The potential energy of hydro-pneumatic spring is electric energy and feeds back to electrical network by middle system, when hydro-pneumatic spring is stretched over setting position
When putting, servomotor stops operating, and measurement signal is fed back to switch board by force transducer and displacement transducer, uses
In hydro-pneumatic spring position and the control of pressure；
Circulating pressure is tested: switch board is according to compressed oil air spring and the mode of operation of extension oil air spring, instead
Compound compression and extension oil air spring；Switch board does with the FREQUENCY CONTROL hydro-pneumatic spring of 3-4 beat/min and comes and goes fortune
Dynamic, and carry out power closed loop control according to the measurement signal of force transducer feedback, it is ensured that the output valve of force transducer
Rule change between the first setting and the second setting；Test period is 30 minutes；
Pressurize is tested: switch board is according to the mode of operation of compressed oil air spring, controlled loading hydraulic cylinder compressed oil
Air spring, makes force transducer output valve reach setting value；Then switch board controls 22 to lead to reversal valve dead electricity,
Keep 10 minutes；Then switch board controls servomotor with perseverance torsion according to the mode of operation of extension oil air spring
Square inverts, and permanent torque value is maintained at 0N m, and ensures that the piston rod of hydro-pneumatic spring freely declines, and measures
And record hydro-pneumatic spring and recover to time of the fully extended state；Repeat pressurize to test 5 times；
Dynamic characteristic test: switch board, will according to compressed oil air spring and the mode of operation of extension oil air spring
The measurement signal of displacement transducer as feedback signal constitute outer shroud control loop, using servomotor rotating speed as
Internal ring controls loop, centered by setting position, controls hydro-pneumatic spring with the frequency set and the displacement of setting
Doing back and forth movement, it is bent with the positional value of displacement transducer that the output valve of force transducer is measured and recorded to switch board
Line, obtains speed characteristics and the indicator card of hydro-pneumatic spring.
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| CN107907319A (en) * | 2017-11-29 | 2018-04-13 | 山东省产品质量检验研究院 | A kind of fire-fighting opens performance automatic test equipment with door opener |
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Cited By (4)
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| CN106949117A (en) * | 2017-04-25 | 2017-07-14 | 哈尔滨工程大学 | A kind of test device of spring Valve Vibration Frequency Response |
| CN107356442A (en) * | 2017-07-17 | 2017-11-17 | 集美大学 | A kind of experimental rig of hydro-pneumatic suspension system |
| CN107907319A (en) * | 2017-11-29 | 2018-04-13 | 山东省产品质量检验研究院 | A kind of fire-fighting opens performance automatic test equipment with door opener |
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| CN105738100B (en) | 2018-07-24 |
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