CN202091298U - Bulk flow and high frequency response electrohydraulic vibrating device based on parallel connection of servo valves - Google Patents
Bulk flow and high frequency response electrohydraulic vibrating device based on parallel connection of servo valves Download PDFInfo
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- CN202091298U CN202091298U CN2011201537805U CN201120153780U CN202091298U CN 202091298 U CN202091298 U CN 202091298U CN 2011201537805 U CN2011201537805 U CN 2011201537805U CN 201120153780 U CN201120153780 U CN 201120153780U CN 202091298 U CN202091298 U CN 202091298U
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Abstract
The utility model discloses a bulk flow and high frequency response electrohydraulic vibrating device based on parallel connection of servo valves. The electrohydraulic vibrating device comprises more than two servo valves; an oil inlet opening of each servo valve is connected with an oil source; an oil return opening of each servo valve is connected with an oil return tank; a first working oil port of each servo valve is connected with a first oil port of a double-extending rod symmetrical hydraulic cylinder; a second working oil port of each servo valve is connected with a second oil port of the double-extending rod symmetrical hydraulic cylinder; a displacement sensor is connected with a piston rod of the double-extending rod symmetrical hydraulic cylinder; and the displacement sensor and the servo valves are in electric connection with a controller. The electrohydraulic vibrating device realizes bulk flow and high frequency response and realizes synchronized motions of valve plugs during the parallel connection of the servo valves.
Description
Technical field
The utility model belongs to the Fluid Transmission and Control field, relates to a kind of electrohydraulic servo oscillation device, is applicable to adopt hydraulic jack to drive the occasion that sine or cyclical movement are done in load in the hydraulic system.
Background technique
In hydraulic vibration devices such as hydraulic vibration gen, linear friction welding machine, the position of oil hydraulic cylinder and speed are required to move reciprocatingly by the sinusoidal curve of certain frequency.The general electrohydraulic servo-controlling system realization above-mentioned functions that drives oil hydraulic cylinder by servovalve that adopts.The opening of servovalve is pressed sinusoidal variation according to the command signal of control system, and sinusoidal motion also will be done by same frequency in the speed of oil hydraulic cylinder and position.Direct current biasing and amplitude by the regulating command signal can be controlled zero-bit and the amplitude that oil hydraulic cylinder moves.Along with equipment improves constantly the amplitude of shake unit and the requirement of frequency, the flow of servovalve and the demand of frequency response are risen simultaneously thereupon.In order to satisfy this demand, traditional electric liquid shake unit has following several structural type:
The one, still adopt single servovalve to drive hydraulic jack, and the flow and the frequency response that improve this servovalve, such as the progression that increases pilot stage, or adopt parallel pilot stage, or the new design of employing new technology is to improve the frequency response of electromechanical transducer. as far as possibleBut its defective is that the restriction owing to various conditions makes that the effect that aforesaid way rose is limited on the one hand, an independent servovalve, and along with the increase of rated flow, its frequency response meeting significantly reduces thereupon, is difficult to realize simultaneously big flow and high frequency sound.On the other hand, even there is the servovalve product that satisfies big flow and high frequency sound requirement, its price is generally also high as to be difficult to accept.
The 2nd, adopt a plurality of oil hydraulic cylinders mode that drives load in parallel.Single like this oil cylinder and drive the required flow of its servovalve can be constant or increase not quite, require as long as servovalve satisfies high frequency sound, and can significantly improve its driving force behind the multi-cylinder parallel.But also there are many shortcomings in this method, as oil cylinder and servovalve all need to dispose many covers, a plurality of oil cylinder parallel connection relate to complicated decoupling zero control problem, complex structure, in some occasions because the restriction of installing space does not allow to adopt the structure of multi executors parallel connection.
The model utility content
The purpose of this utility model is the deficiency that overcomes in the existing electric liquid shake unit, provides a kind of large-flow high-frequency based on the servovalve parallel connection simple in structure to ring electric liquid shake unit.
For achieving the above object, the technological means taked of the utility model is: its large-flow high-frequency based on the servovalve parallel connection rings electric liquid shake unit and comprises oil sources, oil sump tank, two above servovalves, two rod symmetrical hydraulic cylinder, controller and displacement transducers; The filler opening of described each servovalve all is connected with oil sources, the return opening of each servovalve all is connected with oil sump tank, first actuator port of each servovalve all is connected with first hydraulic fluid port of two rod symmetrical hydraulic cylinders, and second actuator port of each servovalve all is connected with second hydraulic fluid port of two rod symmetrical hydraulic cylinders; Described displacement transducer is connected with the piston rod of two rod symmetrical hydraulic cylinders; Described displacement transducer and each servovalve all are electrically connected with described controller.
Further, servovalve described in the utility model is two.
Further, the utility model also comprises acceleration transducer, and described acceleration transducer is connected with the piston rod of two rod symmetrical hydraulic cylinders.
Further, the utility model also comprises first pressure transducer and second pressure transducer, described first pressure transducer is connected with first hydraulic fluid port of two rod symmetrical hydraulic cylinders, and described second pressure transducer is connected with second hydraulic fluid port of two rod symmetrical hydraulic cylinders.
Compared with prior art, the utility model has the advantages that:
(1) adopt a plurality of servovalves mode that drives same oil cylinder in parallel, installing required flow is provided simultaneously by a plurality of valve parallel connections, little to the traffic requirement of each servovalve.Can select intermediate flow common on the market, the servovalve of high frequency sound for use, realize easily and the saving cost, satisfy the height of big flow, high frequency sound, high performance price ratio simultaneously and asked.
(2) only adopted a hydraulic jack to drive load, simple in structure, save installing space.
(3) adopt the utility model electricity liquid shake unit, can carry out synchronization control to its servovalve in parallel, realized when valve core movement is crossed zero-bit synchronously, the control accuracy height has solved the flow that the nonsynchronous problem of valve core movement caused between the servovalve in parallel effectively and has reduced and problems such as reversing impact.
(4) the utility model electricity liquid shake unit to the latus rectum of its servovalve and number in parallel without limits can be according to the number and the size of the servovalve of the required parallel connection of traffic demand reasonable disposition of device, and is flexible.
Description of drawings
Fig. 1 is the hydraulic schematic diagram of a kind of mode of execution of the utility model electricity liquid shake unit;
Fig. 2 is at 50Hz, under the input signal of ± 20% full stroke, the utility model electricity liquid shake unit is carried out valve core of servo valve displacement diagram figure in parallel behind the synchronisation control means;
Fig. 3 is the partial enlarged drawing of Fig. 2 when valve core of servo valve displacement in parallel is just being passed through zero-bit;
Fig. 4 is Fig. 2 at the partial enlarged drawing that valve core of servo valve displacement in parallel is negative when passing through zero-bit.
Embodiment
As shown in Figure 1, the utility model rings electric liquid shake unit based on the large-flow high-frequency of servovalve parallel connection and comprises oil sources 1, oil sump tank 2, two above servovalves, two rod symmetrical hydraulic cylinder 5, controller 11 and displacement transducers 7; The filler opening of each servovalve all is connected with oil sources 1, the return opening of each servovalve all is connected with oil sump tank 2, first actuator port of each servovalve all is connected with first hydraulic fluid port of two rod symmetrical hydraulic cylinders 5, and second actuator port of each servovalve all is connected with second hydraulic fluid port of two rod symmetrical hydraulic cylinders 5; Displacement transducer 7 is connected with the piston rod of two rod symmetrical hydraulic cylinders 5; Displacement transducer 7 and each servovalve all are electrically connected with described controller 11.Wherein, controller 11 can use the dsp chip of TIX, and concrete model is TMS320F240.
If the piston rod of two rod symmetrical hydraulic cylinders 5 also is connected with acceleration transducer 8, then can measure the acceleration signal of piston rod movement, also can be regarded as out the speed of piston rod movement by integration, controller 11 in the electricity liquid shake unit can be gathered these signals, constitute acceleration and speed feedback, realize the tri-consult volume closed loop vibration control of piston rod with the feedback signal of displacement transducer 7.
In addition, if first hydraulic fluid port of two rod symmetrical hydraulic cylinders 5 is connected with first pressure transducer 9, second hydraulic fluid port of two rod symmetrical hydraulic cylinders 5 is connected with second pressure transducer 10, then can monitor the pressure of two 5 two actuator ports of rod symmetrical hydraulic cylinder in real time, if pressure surpasses safety range, controller 11 can give the alarm, and takes some corresponding safety measures.
Therefore in the utility model, each servovalve is taked parallel-connection structure, works simultaneously in electric liquid shake unit vibration processes.The actual performance of the visual electric liquid shake unit of the latus rectum of servovalve and quantity requires to change and increase and decrease.
During the work of the utility model electricity liquid shake unit, by the parameters such as charge oil pressure of operator's target setting vibration frequency, amplitude, load quality and oil sources 1, controller 11 calculates the frequency and the initial magnitude of the valve core movement of each servovalve thus.In vibration processes, controller 11 can continue the signal of detecting position displacement sensor 7, obtains the actual amplitude of two rod symmetrical hydraulic cylinders 5, and compares with the target amplitude of setting, if both deviations surpass allowed band, just to previous calculations to initial magnitude revise.According to frequency that calculates and initial magnitude, controller 11 output instruction signals drive each servovalve.By the synchronization control of controller 11 inside, adjust the amplitude and the phase place of the command signal of exporting to each servovalve, thereby finally reach being synchronized with the movement between each servovalve in parallel then.At this moment, it is maximum that the vibration amplitude that two rod symmetrical hydraulic cylinders 5 produce under the driving of each servovalve reaches, and promptly shake unit has produced the vibration of enough frequencies and amplitude.
In the working procedure, the oil sources of being made up of oil hydraulic pump and accumulator 1 is responsible for providing to device the hydraulic oil of steady pressure, enough flows, and oil sump tank 2 provides the oil return path of unimpeded low back pressure.Each servovalve is under the command signal control of controller 11, and valve core opening is done periodically to-and-fro motion.Hydraulic oil flows to two actuator ports of two rod symmetrical hydraulic cylinders 5 off and on by the opening of each servovalve under setpoint frequency, the piston rod that drives two rod symmetrical hydraulic cylinders 5 is done periodically to-and-fro motion, and piston rod drives load and produces vibration.Displacement transducer 7 and acceleration transducer 8 are measured the displacement and the acceleration of piston rod, and first pressure transducer 8 and second pressure transducer 9 are measured the pressure of two actuator ports of two rod symmetrical hydraulic cylinders 5.The valve element position feedback signal that controller 11 is gathered each servovalve, to realize the synchronization control to each servovalve, controller 11 is also gathered above-mentioned displacement, acceleration and pressure signal respectively, constitutes the closed loop control of shake unit.
In the utility model electro-hydraulic device, the common common servovalve of selecting frequency response to meet the demands, a plurality of same hydraulic jacks that drive in parallel reach needed big flow with this.Because selected servovalve does not have too high requirement to flow, is product common on the market, price is comparatively reasonable, and therefore a plurality of parallel connections can be satisfied the requirement of big flow, high frequency sound, high performance-price ratio simultaneously.
Doing the sinusoidal curve vibration with two servovalve parallel connections, electric liquid shake unit below is example, describes the method for the servovalve in parallel of the utility model electricity liquid shake unit being carried out synchronization control in detail:
(1) calculates the frequency and the initial magnitude of the command signal of first servovalve 3 and second servovalve 4 respectively according to target vibration frequency, amplitude, load and the charge oil pressure etc. of shake unit.
Because electric liquid shake unit produces vibration by two rod symmetrical hydraulic cylinders 5, and two rod symmetrical hydraulic cylinders 5 are driven by first servovalve 3 and second servovalve 4, therefore, both vibration frequencies equate that promptly the frequency of the command signal of first servovalve 3 and second servovalve 4 all equates with the target vibration frequency.Cylinder diameter, bar footpath, mark vibration frequency and amplitude according to two rod symmetrical hydraulic cylinders 5, can directly calculate the required peak rate of flow of device, again according to the rated flow of first servovalve 3 and second servovalve 4, the charge oil pressure of oil sources 1 and the initial magnitude that load stool and urine can calculate the command signal of first servovalve 3 and second servovalve 4.In vibration processes, controller 11 can continue the signal of detecting position displacement sensor 7, obtains the actual amplitude of two rod symmetrical hydraulic cylinders 5, and compares with the target amplitude of setting, if both deviations surpass allowed band, just can revise the initial magnitude that calculates.
(2) according to the frequency and the initial magnitude of the command signal of first servovalve 3 and second servovalve 4, utilize formula (I) to obtain the initial order signal of first servovalve 3 and second servovalve 4 respectively,
In the formula (I), y
10(t) the initial order signal of expression first servovalve 3, y
20(t) the initial order signal of expression second servovalve 4, A
10The initial magnitude of representing the command signal of first servovalve 3, A
20The initial magnitude of representing the command signal of second servovalve 4, ω
0The frequency of representing the command signal of first servovalve 3 and second servovalve 4, the t express time.
(3) drive first servovalve 3 and drive second servovalve 4 by the present instruction signal of first servovalve 3 by the present instruction signal of second servovalve 4.The present instruction signal is exactly the initial order signal in the step (2) during the execution in step first time (3).Controller 11 is gathered the valve element position feedback signal of first servovalve 3 and second servovalve 4 respectively, and the back obtains the mistake zero-bit phase difference of the spool of first servovalve 3 and second servovalve 4 according to the valve element position feedback signal of first servovalve 3 and second servovalve 4
Wherein, the number of times that the k representative detects, and k=1,2 ...,
The spool of representing second servovalve 4 when detecting for the k time when just passing through zero-bit with respect to the phase difference of the spool of first servovalve 3,
The spool of representing second servovalve 4 when detecting for the k time is at negative phase difference with respect to the spool of first servovalve 3 when passing through zero-bit.
Consider that the spool travel signal may occur repeatedly at the zero-bit place of passing through or shakes, in the data processing of phase difference detection, the one, the time lag between passing through is a little judged, if interval too small (as being significantly less than the signal period half), judge that then this passes through a little for disturbing and rejecting, the 2nd, the periodic samples number of increase testing signal is asked for phase difference mean value.
(4) the mistake zero-bit phase difference of the spool of judgement first servovalve 3 and second servovalve 4
Whether satisfy relation (II), if satisfy, execution in step (5) then, otherwise execution in step (6),
In the formula (II), θ
eThe spool of representing first servovalve 3 and second servovalve 4 is just passing through zero-bit and negative phase difference of allowing when passing through zero-bit;
If (II) satisfy, all there is bigger phase difference positive and negative in the opening that two servovalves be describeds when passing through zero-bit, should mainly take the command signal of second servovalve 4 is carried out at this moment the mode of phase shift, progressively reduces phase difference, enters step (5).If (II) do not satisfy, illustrate that after the method for phase shift the positive and negative phase difference that passes through significantly reduces, tackle phase difference this moment and further judge, enter step (6).
(5) utilize formula (III) and (IV) obtain the present instruction signal of first servovalve 3 and second servovalve 4, after return execution in step (3),
In formula (III), the formula (IV),
The present instruction signal of representing first servovalve 3,
The present instruction signal of representing second servovalve 4,
The phase shift angle of representing second servovalve, 4 present instruction signals,
The phase shift angle of representing second servovalve, 4 last command signals, and
(6) judge
Or
Whether set up, if set up, execution in step (7) then, otherwise finish first servovalve 3 of the utility model electricity liquid shake unit and the synchronization control of second servovalve 4.
If following formula is set up, the spool travel that two servovalves are described meets the demands at one of them phase difference that just passes through and bear when passing through zero-bit, but another phase difference is still bigger, and should enter step (7) this moment, and the mode of taking to change the command signal amplitude further reduces phase difference.
If following formula is false, the spool travel that two servovalves are described all meets the demands at the phase difference that just passes through and bear when passing through zero-bit, and this moment, synchronization control was finished.
(7) utilize formula (V) and (VI) obtain the present instruction signal of first servovalve 3 and second servovalve 4, after return execution in step (3),
Among formula (V), (VI),
The amplitude gain of representing the present instruction signal of first servovalve 3,
The amplitude gain of representing the present instruction signal of second servovalve 4,
The amplitude gain of representing the last command signal of first servovalve 3, and
The amplitude gain of representing the last command signal of second servovalve 4, and
λ
1The amplitude gain coefficient of representing the command signal of first servovalve 3, λ
2The amplitude gain coefficient of representing the command signal of second servovalve 4, Q
N1The rated flow of representing first servovalve 3, Q
N2The rated flow of representing second servovalve 4.
Formula (VI) is for the change that the overcomes servovalve command signal amplitude influence to flow rate of hydraulic system, promptly in the signal amplitude that dwindles (amplification) second servovalve 4, amplify the signal amplitude of (dwindling) first servovalve 3, and satisfy because the command signal amplitude changes caused flow increase and decrease is cancelled out each other.
Above for being the example that two servovalve parallel connections, shake units are done the sinusoidal curve vibration.At two and two above servovalves, when shake unit was done sinusoidal curve or other periodicity curvilinear motion, still applicable above method was carried out synchronization control to the servovalve of the parallel connection of the utility model electricity liquid shake unit.
To shown in Figure 4, at 50Hz, under the input signal of ± 20% full stroke, after the utility model electricity liquid shake unit was carried out synchronization control, the phase difference of the spool travel of two servovalves in parallel when passing through zero-bit was decreased to about 1 ° as Fig. 2.Under the input signal of other frequency and other amplitude, show good synchronization control effect equally, as space is limited, fail to list one by one.This shows that the utility model electricity liquid shake unit can satisfy big flow, the high frequency sound requirement of electric liquid shake unit, and the spool when realizing that servovalve is in parallel is synchronized with the movement.
Claims (4)
1. the large-flow high-frequency based on the servovalve parallel connection rings electric liquid shake unit, it is characterized in that: comprise oil sources (1), oil sump tank (2), two above servovalves, two rod symmetrical hydraulic cylinder (5), controller (11) and displacement transducers (7); The filler opening of described each servovalve all is connected with oil sources (1), the return opening of each servovalve all is connected with oil sump tank (2), first actuator port of each servovalve all is connected with first hydraulic fluid port of two rod symmetrical hydraulic cylinders (5), and second actuator port of each servovalve all is connected with second hydraulic fluid port of two rod symmetrical hydraulic cylinders (5); Described displacement transducer (7) is connected with the piston rod of two rod symmetrical hydraulic cylinders (5); Described displacement transducer (7) and each servovalve all are electrically connected with described controller (11).
2. the large-flow high-frequency based on the servovalve parallel connection according to claim 1 rings electric liquid shake unit, and it is characterized in that: described servovalve is two.
3. the large-flow high-frequency based on the servovalve parallel connection according to claim 1 rings electric liquid shake unit, it is characterized in that: also comprise acceleration transducer (8), described acceleration transducer (8) is connected with the piston rod of two rod symmetrical hydraulic cylinders (5).
4. the large-flow high-frequency based on the servovalve parallel connection according to claim 1 rings electric liquid shake unit, it is characterized in that: also comprise first pressure transducer (9) and second pressure transducer (10), described first pressure transducer (9) is connected with first hydraulic fluid port of two rod symmetrical hydraulic cylinders (5), and described second pressure transducer (10) is connected with second hydraulic fluid port of two rod symmetrical hydraulic cylinders (5).
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| CN2011201537805U CN202091298U (en) | 2011-05-15 | 2011-05-15 | Bulk flow and high frequency response electrohydraulic vibrating device based on parallel connection of servo valves |
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Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102182729A (en) * | 2011-05-15 | 2011-09-14 | 浙江大学 | Large-flow high-frequency response electrohydraulic vibration device based on parallel servo valves and control method |
| CN108533816A (en) * | 2018-03-30 | 2018-09-14 | 同济大学 | A kind of electrohydraulic servo valve inhibiting function with acceleration bias drift |
| CN108591137A (en) * | 2018-07-12 | 2018-09-28 | 西南交通大学 | A kind of novel robot hydraulic knuckle drive system |
| CN109616001A (en) * | 2018-12-11 | 2019-04-12 | 上海应用技术大学 | Electro-hydraulic position servo system experimental bench |
| CN110594233A (en) * | 2019-09-03 | 2019-12-20 | 浙江大学 | Hydraulic cylinder structure of hydraulic system with higher frequency response requirement and limited installation space |
| CN114811117A (en) * | 2022-02-24 | 2022-07-29 | 浙江工业大学 | High-frequency one-way sinusoidal flow control valve |
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2011
- 2011-05-15 CN CN2011201537805U patent/CN202091298U/en not_active Expired - Fee Related
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102182729A (en) * | 2011-05-15 | 2011-09-14 | 浙江大学 | Large-flow high-frequency response electrohydraulic vibration device based on parallel servo valves and control method |
| CN102182729B (en) * | 2011-05-15 | 2013-05-01 | 浙江大学 | Large-flow high-frequency response electrohydraulic vibration device based on parallel servo valves and control method |
| CN108533816A (en) * | 2018-03-30 | 2018-09-14 | 同济大学 | A kind of electrohydraulic servo valve inhibiting function with acceleration bias drift |
| CN108533816B (en) * | 2018-03-30 | 2019-08-02 | 同济大学 | A kind of electrohydraulic servo valve inhibiting function with acceleration bias drift |
| CN108591137A (en) * | 2018-07-12 | 2018-09-28 | 西南交通大学 | A kind of novel robot hydraulic knuckle drive system |
| CN109616001A (en) * | 2018-12-11 | 2019-04-12 | 上海应用技术大学 | Electro-hydraulic position servo system experimental bench |
| CN110594233A (en) * | 2019-09-03 | 2019-12-20 | 浙江大学 | Hydraulic cylinder structure of hydraulic system with higher frequency response requirement and limited installation space |
| CN110594233B (en) * | 2019-09-03 | 2021-06-29 | 浙江大学 | Hydraulic cylinder structure of hydraulic system with higher frequency response requirement and limited installation space |
| CN114811117A (en) * | 2022-02-24 | 2022-07-29 | 浙江工业大学 | High-frequency one-way sinusoidal flow control valve |
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| Date | Code | Title | Description |
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| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C53 | Correction of patent for invention or patent application | ||
| CB03 | Change of inventor or designer information |
Inventor after: Wei Jianhua Inventor after: Fang Jinhui Inventor after: Kong Xiaowu Inventor after: Hu Shisong Inventor after: Lin Hai Inventor before: Wei Jianhua Inventor before: Fang Jinhui Inventor before: Kong Xiaowu |
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| COR | Change of bibliographic data |
Free format text: CORRECT: INVENTOR; FROM: WEI JIANHUA FANG JINHUI KONG XIAOWU TO: WEI JIANHUA FANG JINHUI KONG XIAOWU HU SHISONG LIN HAI |
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| C17 | Cessation of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20111228 Termination date: 20130515 |