Device for limiting power of electrohydraulic servo drive

FIELD: hydraulics.

SUBSTANCE: device comprises sleeve with step outer side and axial passage that receives two cylindrical collars of the step slide valve whose third collar is provided with face stop. The outer side of the smaller diameter of the sleeve is provided with the first and second grooves interconnected through the axial passage. The outer surface of greater diameter of the sleeve has two chamferings whose surfaces are connected with the axial passage through openings. The first collar is arranged near the face of the slide valve opposite to the stop to define a control chamber, is provided with two flat chamferings, and is made for permitting cooperation with the ports of the first groove in the sleeve. The second collar is separated from the third collar by a groove and is made for permitting cooperation with radial openings of the sleeve. The first groove is open from its face, and the ports of the second groove are connected with the space defined in the axial passage between the collars of the slide valve.

EFFECT: enhanced efficiency.

6 cl, 10 dwg

 

The invention relates to mechanical engineering and can be used in control systems working bodies of various machines, such as aircraft, limited power consumption.

From the patent literature known two-stage limiter power, containing the primary and secondary spools and two adjustable throttle connected with the regulator pump [1].

The disadvantages of this limiter is the large size and weight, low efficiency, high complexity of manufacturing and maintenance, lack of range bypass frequency control signal that can be worked out with sufficient precision, low dynamic resistance and the low quality of the transition process, due to suboptimal schematic and design parameters.

From the patent literature known limiter power electro-hydraulic actuator containing a sleeve with a stepped outer surface and an axial channel, which has two cylindrical working belt speed of the spool, the outer surface of the smaller diameter sleeve is made of the first and second grooves, United Windows axial channel [2].

The disadvantages of this limiter is a low efficiency caused by the inability to provide the full texts of the control range and reducing the pressure of the volume control to the minimum value, equal to the suction pressure, the lack of functionality due to the fact that the control is performed on the pump pressure and throttle pressure regulation electro-hydraulic actuator, i.e. not provided by the space-throttle control), as well as the related lack of the frequency control signal, which can be practiced with sufficient accuracy, the low quality of the transition process and low dynamic resistance due to suboptimal design decisions spool with two belts and sleeves with three closed grooves.

An object of the invention is the creation of an effective limiter power and expanding Arsenal of power limiters.

The technical result of the invention is to improve efficiency, increase functionality, expanding the range of noise frequencies, the improvement of the dynamic characteristics of a reserve of stability and quality of the transition process in space-throttle regulation drive using the proposed limiter power.

The invention consists in that the limiter power electro-hydraulic actuator includes a sleeve with a stepped outer surface and an axial channel, which has two cylindrical Rabochaya spring-loaded stepped spool, the third belt which is equipped with end stops and with a diameter larger than a diameter of the axial channel of the sleeve, on the outer surface of the smaller diameter of which is made of the first and second grooves, United with the axial channel and the outer surface of the larger diameter sleeve is made with two flat sections, the surfaces of which are connected by radial holes with the axial channel, the first band is located at the end of the spool opposite stop with the formation of camera control, made of a width less the width of the second belt, with two flat sections on the outer surface and interoperable with Windows first groove of the sleeve, having a length greater than the width this band; a second band separated by the groove on the spool from the third band is located at a distance from the latter is smaller than the first, and made interoperable with the radial holes of the sleeve, the first groove which is open from her face, and the second groove are connected with the working cavity formed in the axial channel between the first and second belts of the spool.

Preferably the second band is located at distances from the first and third belts, the ratio of the length of which is 10.

The first groove of the sleeve is connected with the axial channel of the two Windows of rectangular shape with a length, p is ebisawa 2± 0.1 times the width of the first belt.

The second groove of the sleeve is connected with the axial channel four Windows in the form of a circle with a diameter amounting to 0,5±0.05 diameter of the axial channel.

The radial holes of the sleeve is made in the form of interconnected circles and rectangular groove whose width is 0.1÷0.3 diameter of this circle, which is located from the outer surface of the sleeve of smaller diameter.

The first groove and the axial channel of the sleeve from the first belt spool connected with hydroline throttle control actuator, the second groove with hydroline volume control actuator and the outer surface of the sleeve with two flat sections - with the sink.

The stopper is preferably made with the possibility of an adjustable connection hydroline throttle control hydroline volume regulation, alienating them when the pressure in the hydroline throttle control with simultaneous connection through the slices on a surface of the first belt spool and connecting the hydroline volume regulation with the sink at the further increase of pressure.

1 shows a structural diagram of a limiter power figure 2 - sleeve limiter power figure 3 - cross section of a liner limiter power, 4 - Popper is a great cross-section of the radial holes, figure 5 - valve limiter power, 6 - section of the first belt limiter power figure 7 - schematic diagram of the electrohydraulic servo drive space-throttle control, Fig - logarithmic amplitude-frequency characteristics of the open drive at rated load, figure 9, 10 - transient response of the actuator and its links in idle mode and at rated load, respectively.

The limiter power electro-hydraulic actuator includes a sleeve 1 with a stepped outer surface and an axial channel 2, which has two cylindrical working band 3, 4-step spring-loaded slide valve 5, the third belt 6 which is provided with a conical or hemispherical end fence 7 and is made with a diameter larger than a diameter of the axial channel 2. On the outer surface of the smaller diameter sleeve 1 has first and second grooves 8, 9, United Windows axial channel 2. The outer surface of the larger diameter of the sleeve 1 is made with two flat sections (not labeled), the surfaces of which are connected by radial holes 10, 11 with the axial channel 2. The first belt 3 is located at the end of the spool 5, the opposite extreme position 7 with education at its free end camera control 39. The belt 3 is made with a width of 1.5 mm, less than the width of 2.5 mm of the second belt 4, with two flat sections on the outer surface and interoperable with Windows first grooves 8 of the liner 1 having a length of 3 mm larger than the width of the belt 3. The second belt 4 is located at a distance of 1.5 mm from the third belt 6, which is smaller than the distance of 16 mm from the first belt 3, and is arranged to interact with the radial holes of the sleeve 1, and the second grooves 9 of the latter is connected with the working cavity 12 formed in the axial channel 2 between the first and second belts 3, 4 spool 5.

When the valve 5 is made with a third belt 6 is separated from the second belt 4 by the groove on the spool 5. The second belt 4 is located at distances from the first and third belts 3, 6, constituting 16 mm and 1.5 mm, i.e. the ratio of the distances (lengths) is in the range of 10-12. The first groove 8 of the liner 1 is connected with the axial channel 2 two Windows 13, 14 of rectangular shape with a length of 3 mm, greater than 2±0.1 times the width of 1.5 mm of the first belt 3.

The second groove 9 of the sleeve 1 is connected with the axial channel 2 four Windows 15 in the form of a circle with a diameter of 2 mm, amounting to 0,5±0.05 4 mm diameter axial channel 2.

Radial holes 10, 11 of the sleeve 1 is made in the form of interconnected circle and a rectangular groove, the width "h" is equal to 0.2 mm and is within (is) 0,1÷0.3 diameter d=1 mm this okrugin the STI, located from the outer surface of the sleeve 1 of smaller diameter.

The first groove 8 and the axial channel 2 of the sleeve 1 from the side of her face and the first belt 3 valve 5 are connected by hydroline 40 with hydroline 33 throttle control electro-hydraulic actuator, the second groove 9 with hydroline 42 volume regulation of the pump 17 of the actuator, and the outer surface with two flat sections connected by hydroline 44 from discharge - suction.

The power limiter is made with the possibility of an adjustable connection hose 40 (33) throttle control hydroline 42 volume regulation, alienating them when the pressure in the hydroline 33 (40) with simultaneous connection through the orifice 41, which carry out the slices on a surface of the first belt 3 spool 5, and the connection of hydroline 42 volume regulation through hydroline 44 from discharge - suction with further increase of pressure in an electrohydraulic servo drive.

Electrohydraulic servo drive space-throttle control in which the power limit of the claimed limiter, contains Executive hydraulic motor 16, a pump 17 with two-way hydraulic regulation and with the spring 18 acting on the regulatory authority (swash) pump 7 in the direction of establishing a maximum flow rate of the pump 17, pressure reducing valve 19 with a tuning inductor 20, two stage hydraulic throttle control with adjustable orifice 21 of the first cascade and automatic pyatilineyny distributor 22 of the second cascade, the inventive three-way restrictor 23 power compensation piston-podavlyayushee (accumulating) device 24, a piston chamber which is connected to the suction pump 17, the valves 25, 26 and the sensor 27 of the displacement of the hydraulic motor 16. The actuator 16 has a cavity and reversing the movable body, the rod or shaft (not labeled). The sensor 27 is connected to the hydraulic motor 16 and the gear-rack and pinion (not labeled). The pump 17 is connected with a drive motor (not illustrated). On the ends of the plunger rotation of the swash plate (not shown) of the pump 17 are camera 43, 45. The sensor 27 is connected to one input of the comparing device 28, the output of which through the amplifier 29 is connected to an Electromechanical transducer 30 of the control orifice 21 of the first stage of steering, rigidly connected to the valve 22 of the second cascade. The distributor 22 is accomplished with two hose 31, 32 connected to the cavities of the hydraulic motor 16, with one hydroline 33, is connected through hydroline 40 to the claimed three-way limiter 23 power, with two hose 34, 35 connected to the discharge and suction pump 16, and with two chambers 36, 37 control. The chamber 37 with a larger control is connected to the input of an adjustable inductor 21 of the first stage and the camera 36 with a smaller area to the output of the pressure reducing valve 19, which is connected with the rod cavity compensation-podavlyayushego device 24 and through the first orifice 38 of constant cross-section - with the input of the adjustable inductor 21 of the first cascade. The entrance pressure reducing valve 19 is connected to the discharge pump 17, hydroline 33 pyatilineyny distributor connected to three-way limiter 23 power, connected to the chamber 39 of the control of the latter, with its hydroline 40 and through the second orifice 41 of constant cross-section with hydroline 42, connected to the chamber 43 of the pump control 17 acting in the direction of increasing consumption, the third hydroline 44 is connected with three-way limiter 23 power and is connected to the suction pump 17, the other chamber 45 of the control that is exerted in the direction of reducing consumption, connected with its discharge.

The valve 25 is connected to hydroline 33 pyatilineyny dispenser 22 and hydroline 40 three-way limiter 23 power, and the second valve 26 via the additionally installed valve 46 recharge with a suction pump 17.

On Fig amplitude-frequency logarithmic characteristic convoy is Acena IW(jw)I, phase logarithmic characteristic denoted by Arg W(jw). Figure 9, 10 of the marked characteristics of the transition process: "a" - input rectangular signal on the positive input of the comparing device, "b" - stroke hydraulic, c - the speed of the hydraulic motor, d - move slide valve 5, "e" - run regulatory body pump, T is the discharge pressure of the pump.

Electrohydraulic servo drive space-throttle control with the declared power limiter operates as follows. The claimed power limiter is not used outside of the drive, this operation is described in the drive.

When the off state of the actuator, the discharge pressure is absent, the spring 18 regulatory authority (bevel washer etc.) pump 17 is set to the maximum stroke of the plungers (or pistons), i.e. in the position of maximum fluid flow. The pressure in the chambers 43, 45 and in the chambers 36, 37 are the same. Start the pump motor 17 causes a discharge pressure acting in chamber 45, resulting regulatory body pump 17 is placed into the position of minimum flow rate of the working fluid required for the readiness of the drive and steering to the failover control signal. Thus, in the absence of a control signal on the positive input of the comparing ustroystva energy consumption is minimal. Pressure reducing valve 19 sets and further provides a stable pressure at the inlet of the throttle 38, into the chamber 36 of the hydraulic system, as well as in the rod end compensation-podavlyayushego device 24 that supports the required level of pressure at the inlet valve 46 and, hence, the suction pump 17. Throttle position 21 provides the balance of the spool valve 22 of the steering neutral position.

When the input signal "and" control on the positive input of the comparing device 28 this signal is converted by the amplifier 29 is applied to the Electromechanical transducer 30 that changes the resistance of the inductor 21 of the first stage booster. Thus, the pressure in the chamber 36 is determined by the setting of the pressure reducing valve 19 and into the chamber 37 - the resulting total resistance of the inductors 21 and 38. The result is a working differential pressure in the chambers 36, 37, defined by the ratio of the effective areas and pressures in these chambers acting on the distributor 22, which moves in the direction of the resultant force. Movement of valve 22 changes the resistance of adjustable chokes connected to the hose 31, 32, 33, and hydroline 33 is connected to the hose 31, 32, in which the pressure is more.

At the same time move is aspideretes 22 restores its equilibrium and the initial resistance of the inductor 6. The valve 22 is installed in the position defined by the signal value of the Electromechanical transducer 30.

The result is a pressure drop in the hose 31, 32 and in the cavities of the hydraulic motor 16. At the same time, the hose 33, 40, 42 and through the groove 8 of the stopper 23, the open belt 3 of the valve 5, the pressure enters the chamber 43, resulting regulatory body pump 17 is transferred to the feeding position of the set value of the flow rate of the working fluid to the hydraulic motor 16. In one of the cavities of the hydraulic motor 16 and hydroline 33 receives the working fluid under pressure determined by the load, and the other cavity stesnjaetsja on the suction of the pump 17. The value of the flow rate of the working fluid pump 17 determines the speed of the hydraulic motor 16. The overshoot on the move "b" of the hydraulic motor 16 is missing, its speed changes smoothly, especially under load. The duration of the transition process from the initial filing of the control signal to establish a steady-state displacement of the hydraulic motor 16 is minimal, as it does not exceed the duration of the displacement regulating parts (valve 5 and the regulatory body pump 17), i.e. less than analogues (Fig.9, 10). The displacement of the hydraulic motor 16 to the load is monitored by the sensor 27, which movement is transmitted through backlash-free gear-ray is Noah transmission. The sensor 27 generates a signal of negative feedback on position, which device 28 algebraically summed with the control signal. The output device 28 and amplifier 29 is reduced to zero and the Electromechanical transducer 30 is returned to its original state, which leads back to the initial state of the throttle 21 and valve 22. The pressure in the hose 31, 32 and in the cavities of the hydraulic motor 16 is aligned. The pressure in hydroline 33 is received and decreases the pressure in the chamber 43 of the pump 17, the regulatory body which returns to the position of the minimum performance.

The contour of the actuator element as claimed limiter has a reserve power And the phase of 60 degrees at the cutoff frequency of 16 Hz (Fig)that guarantees the occurrence of flutter. At rated load, for which the characteristics are constructed figures 9, 10, the gain can be increased before reaching the cut-off frequency of 80 Hz (at zero stock in phase). The corresponding decrease of the load on the hydraulic motor 16, the gain can be increased, and the cutoff frequency can be increased to 150 Hz.

Given the load on the hydraulic motor 16 determines the allowable pressure of the pump 17 and, consequently, the magnitude of the permissible power consumption of the drive and proportional is optional to the product of the values of pressure drop and flow rate of the pump 17. In the event of unauthorized increase the load on the hydraulic motor 16 and the discharge pressure of the pump 17 at the same time increasing pressure in the hose 33, 40 and into the chamber 39 of the stopper 23. The latter performs power control on the pressure in the chamber 39, and the valve 5 is moved in the direction of the overlapping belt 3 groove 8 and, consequently, reduce bore, connecting hydroline 40 with hydroline 42, and reduce pressure in the chamber 43 of the pump 17, the flow which also decreases. Smooth flow changes, largely driven by the implementation of the grooves 8 of the open side end face of the spool 5. In case of further growth of the pressure discharge valve 5 limiter 23 belt 3 divides the hydroline 40, 42, simultaneously, the chamber 43 is connected with hydroline 33 only through the orifice 41, which carry out the slices on a surface of the first belt 3 of the valve 5 and the flow rate of the pump 17 is reduced to values close to the minimum. If the increase in the discharge pressure does not stop, the valve 5 is moved further and band 4 provides access from the groove 9 through the working cavity 12 to the radial holes 10, 11, opening the last groove with a width of "h". As a result, the stopper 23 connects hydroline 42 through radial holes 10, 11, i.e. only through the channels of the cartridge case 1 (without external connections, the cat is which could increase the hydraulic losses in this area and to narrow the range of regulation of the pump), with hydroline 44, i.e. directly with the suction. Thus the performance of the valve 5 with the third belt 6 is separated from the second belt 4 groove, reduces the hydrodynamic forces acting on the spool 5 in the switching period of the hose, and thereby prevents the delay and the emergence of self-oscillations. The pressure in the chamber 43 becomes as low as possible, the regulatory body of the pump 17 is returned to the position of the minimum flow and flow (flow rate) of the pump 17 is reduced to the minimum possible with the engine running.

Thus, while ensuring volumetric regulation of the pump using the proposed power limiter provides increased efficiency, drive, extension of the range of noise frequencies, improving dynamic characteristics - stock sustainability and quality of the transition process.

Sources of information

1. SU # 661138, 1979.

2. RU # 2031256, 1995 (prototype).

1. The limiter power electro-hydraulic actuator containing a sleeve with a stepped outer surface and an axial channel, which has two cylindrical working belt spring-loaded manual valve, a third belt which is equipped with end stops and with a diameter larger than a diameter of the axial channel of the sleeve, on the outer poverhnostnogo diameter which is made of the first and second grooves, United with the axial channel and the outer surface of the larger diameter sleeve is made with two flat sections, the surfaces of which are connected by radial holes with the axial channel, the first band is located at the end of the spool opposite stop with the formation of the camera control is performed with a width less the width of the second belt, with two flat sections on the outer surface, and interoperable with Windows first groove of the sleeve, having a length larger than the width of the belt, the second belt is separated by the groove on the spool from the third band is located at a distance from the latter is smaller than the first, and made interoperable with said radial holes of the sleeve, the first groove which is open from her face, and the second groove are connected with the working cavity formed in the axial channel between the first and second belts of the spool.

2. Limiter according to claim 1, characterized in that the second band is located at distances from the first and third belts, the ratio of the lengths of 10-12.

3. Limiter according to any one of claims 1 and 2, characterized in that the first groove of the sleeve is connected with the axial channel of the two Windows of rectangular shape with a length in excess of 2+0.1 times the width of the first belt.

4. Limiter according to any one of claims 1 and 2, characterized t is m, the second groove of the sleeve is connected with the axial channel four Windows in the form of a circle with a diameter amounting to 0,5+0,05 diameter of the axial channel.

5. Limiter according to any one of claims 1 and 2, characterized in that the radial holes of the sleeve is made in the form of interconnected circle and a rectangular groove, the width of which is 0.1 to 0.3 of the diameter of this circle, which is located from the outer surface of the sleeve of smaller diameter.

6. Limiter according to any one of claims 1 and 2, characterized in that the first groove and the axial channel of the sleeve from the first belt spool connected with hydroline throttle control actuator, the second groove with hydroline volume control actuator and the outer surface of the sleeve with two flat sections - with the sink.

7. Limiter according to claim 6, characterized in that it is made with the possibility of an adjustable connection hydroline throttle control hydroline volume regulation, alienating them when the pressure in the hydroline throttle control with simultaneous connection through the slices on a surface of the first belt spool, and a connection hydroline volume regulation with the sink at the further increase of pressure.



 

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