EP0119543A2 - Positionneur compact du type électro-hydraulique pour vannes de turbines - Google Patents

Positionneur compact du type électro-hydraulique pour vannes de turbines Download PDF

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Publication number
EP0119543A2
EP0119543A2 EP84102385A EP84102385A EP0119543A2 EP 0119543 A2 EP0119543 A2 EP 0119543A2 EP 84102385 A EP84102385 A EP 84102385A EP 84102385 A EP84102385 A EP 84102385A EP 0119543 A2 EP0119543 A2 EP 0119543A2
Authority
EP
European Patent Office
Prior art keywords
pressure
hydraulic
valve
pump
compact drive
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP84102385A
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German (de)
English (en)
Other versions
EP0119543A3 (fr
Inventor
Wolfgang Dipl.-Ing. Kindermann
Ernst Kloster
Hans-Joachim Leupers
Helmut Schaper
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Siemens AG
Original Assignee
Kraftwerk Union AG
Siemens AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Kraftwerk Union AG, Siemens AG filed Critical Kraftwerk Union AG
Publication of EP0119543A2 publication Critical patent/EP0119543A2/fr
Publication of EP0119543A3 publication Critical patent/EP0119543A3/fr
Withdrawn legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D17/00—Regulating or controlling by varying flow
    • F01D17/20—Devices dealing with sensing elements or final actuators or transmitting means between them, e.g. power-assisted
    • F01D17/22—Devices dealing with sensing elements or final actuators or transmitting means between them, e.g. power-assisted the operation or power assistance being predominantly non-mechanical
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/18—Combined units comprising both motor and pump

Definitions

  • the invention relates to an electrohydraulic compact drive for valves of turbomachinery, in particular steam turbines, such as control, quick-closing or diverter valves, according to the preamble of claim 1.
  • the complex task is mainly solved by the features specified in the characterizing part of claim 1.
  • Advantageous further developments are specified in subclaims 2 to 12.
  • the advantages that can be achieved with the invention are primarily to be seen in the fact that the pressure increase in the hydraulic supply system leads to an average system pressure of, for. b. 140 bar (this value is about 4 times as high as the system pressure in conventional electrohydraulic controls, which is around 36 bar there), high actuating or switching forces of the power piston with a small construction volume of the power piston-cylinder system and with a small construction volume of the rest Components of the hydraulic supply system, such as pumps and pressure accumulators, can be achieved.
  • the pressurized fluid container or oil container (the designation tank is also common) can be made relatively small, but large enough to serve as installation space for the switch-off spring guided on the piston rod.
  • the pressurized fluid container thus forms the central load-bearing housing for the attached partial housing in modular design; In terms of its wall thickness, it is dimensioned accordingly, with the added advantage that the container walls and its cover can serve to accommodate hydraulic channels.
  • FIG. 1 prior art
  • FIG. 2 The actuators, i.e. the switching and actuating drives, are to be explained first.
  • the key feature of the new compact drives is the integrated control fluid supply. This means an increase in the number of modules to be accommodated in the drive. Due to the higher system pressure, the construction volume can still be kept small, using positive displacement pumps will. With an increase in pressure from 36 bar up to an average system pressure of 140 bar, the actuating piston area F K1 - see FIG. 2 - and thus the stroke volume is reduced to approx. 25%, based on the conventional actuator AO (FIG. 1).
  • the pump, accumulator and oil tank are dimensioned accordingly (not shown in FIGS. 1, 2), so that a compact design results when the supply is installed.
  • the actuator piston area of actuator AO is labeled F K0 , where F K0 ⁇ 4 F K1 .
  • the oil tank is also the installation space for the closing spring a7 guided on the piston rod a1, a20.
  • the tank a10 is connected to the supply room a110 via a double valve b4.
  • Changes in pressure as a result of changes in temperature and level in the oil tank a10 are compensated for by an overpressure or underpressure valve b40, b41, the air flowing in under underpressure being filtered (filter b42) and both sub-valves b40, b41 approximately concentrically with one another with their spring-loaded closure pieces and Valve seats are arranged.
  • the control fluid supply is designed to protect the pump b1 and to save energy for intermittent operation, i. H. with the excess of the pump delivery flow compared to the consumer leakage flow, the accumulators b2 are filled with increasing pressure: charging operation.
  • the overflow valve b5 When the overflow valve b5 is closed, the pump current flows through the check valve b6 and filter b3 to the accumulators b2. After reaching the upper charge pressure, the overflow valve b5 opens, the check valve b6 closes, so that the pump b1 feeds back into the container a10, i. H. almost pressure-free circulation during unloading.
  • the leakage current and, if necessary, the stroke volume are taken from the accumulators.
  • FIG. 3 shows with FIG. 3 the pressure-time behavior of the charging cycle.
  • the upper charge pressure p max is approx. 160 bar
  • the lower charge pressure p approx. 140 bar with the first useful storage volume ⁇ V L.
  • the zade time ⁇ t 1 is approx. 20 s
  • the discharge time ⁇ t el approx. 2 min if only the leakage current flows out, see FIG. 8.
  • FIG. 9 shows the valve lift curve over time for the two extreme control processes c1, c2.
  • the pressure range from the lower boost pressure 140 bar to the min.
  • Operating pressure p min of 110 bar with the second useful storage volume ⁇ V R is provided for control processes, see Fig. 10.
  • diaphragm accumulators b2 are used in which the separating element between control liquid a60 or a6 and gas c3 represents a clamped diaphragm b20. This rolls - Fig. 7 - from the wall during the work cycle - no chafing - so that abrasion that enters the filtered liquid is avoided.
  • the accumulators b2 each consist of a pot part b21 with a cover part b22, which parts are sealed together in the area of the parting joints b23 and the edge of the bell-like membrane b20.
  • the pot part b21 has a bottom-side bore b24 for connecting the line 112, 113 for the control liquid a6 (see FIG.
  • the cover part b22 has a filler opening b25 on the cover side, which can be closed, for pressurized gas, for. B. nitrogen.
  • the gas filling c3 fills the entire storage volume, it is under the storage Pre-filling pressure p v (Fig. 8); 7 it is compressed until it holds the respective pressure p min , p m , p max of the control liquid in equilibrium.
  • the latter is used to fill and drain the oil tank a10 with or from control fluid a60. Due to the continuous filtering in the main flow by means of filter b3, the entire hydraulic system is kept at a high level of purity (FIG. 3).
  • the safety valve c6 protects the accumulators b2 against overpressure; it triggers when a permanently adjustable limit pressure is reached; the relief valve c7 serves to relieve the pressure on the accumulators b2 and the pressure busbar 11 during inspection work or the like.
  • actuating cylinder (Fig. 3)
  • the pressurized in the opening direction R ö adjusting piston a5 is relieved on the opposite side F K2.
  • the closing force is exerted by the a7 spring washer.
  • the brake piston a50 is immersed in the damping space a40.
  • the remaining speed can be changed by means of an adjustable throttle (not shown).
  • a check valve b7 opens the damping chamber a40 to the cylinder pressure chamber 51, which is relieved of pressure.
  • Its electric servomotor is labeled b81, its baffle plate system b82 and its spool valve b83.
  • a valve-actuating movement is initiated at a control deviation X R between position command value X should and Stellun g sistwert X is, and when electric current is smaller by the positioner R el power imprinted ( ⁇ 1 Watt) the electro-hydraulic transducers b8.
  • the converter called the electro-hydraulic servo valve, is a high-quality, continuously acting directional control valve with particularly good stationary and dynamic properties and high power amplification (over 10 6 ).
  • the electrical input current becomes a few ms proportional oil flow is assigned to the actuating cylinder as output variable.
  • the hydraulic connections are labeled 116 (connection to pressure oil rail 11), I T (connection to drain rail 1 2) and I A (control oil outlet).
  • I B is a B connection designed as a blind flange for double-sided application.
  • the feedback of the actuating path to the electrical position controller R el takes place via a displacement transducer b9, which preferably works according to the ultrasound principle, which closes the position control loop, see dashed return line I back .
  • I el symbolizes signal lines for the electrical controlled variables X R of the controller R el to the electric servomotor b81.
  • b841 and b842 are supply and return lines to a fluid filter, not shown.
  • An electro-hydraulic servo valve of basically the same structure, as shown in Fig. 3 and 13, is a standard component and z. B. described in catalog 730 from Moog GmbH. in D-7030 Böblingen with the title "Flow Servo Valves Series 73", published in May 1975 (6 pages), see in particular the three illustrations on page 2.
  • the circuit symbol shown there with a brief functional description has also found its way into the "ISO -Norm 1219 "of the" International Organization for Standardization "with the title” Fluid power systems and components - Graphic symbols ", Ref. ISO 1219 - 1976 (E / F).
  • the switch symbol is shown there on page 10 under No. 7.2.4. In the context of the present application, therefore, an even more detailed explanation of the electro-hydraulic servo valve can be dispensed with.
  • 2-way seat valves c5 controlled by solenoid valves are opened with the shortest actuating time and the piston chamber a51 is connected to the outlet. Due to the short channels from cylinder a4 via directional control valves c4 to oil reservoir a10 and the possible generous dimensioning of directional seated valves c5, short closing times of ⁇ 150 ms and short delay times can be achieved.
  • the 2-way seat valves c5 are standard built-in elements with piston guidance, which are kept closed when the actuating cylinder pressure a6 is present under valve plug c51 with the control pressure formed by the directional solenoid valve c4 above the plug.
  • the energized solenoid c41 is de-energized and the control pressure is reduced, the directional control valve c4 opens.
  • the triggering process is supported by a second magnet c42 on the directional control valve c4, the armature c43 of which causes a breakaway pulse via a spring c420 and thus ensures a reliable response from the rest position even after a long period of operation.
  • the anchor c43 hits the end face of the slide switch c40 as a striking anchor after passing through the distance c430.
  • the pressure line 110 is connected to the pressure side of the pump b1 and opens into the pressure oil or pressure fluid busbar 11 via the check valve b6, the short line section 1101, the filter b3 and the line section I11. These are connected via spur lines closed:
  • the accumulators b2 via lines 112 and 113, the safety valve c6 via line 117 and the relief valve c7 via line 118, the drain line opening into the oil container or tank a10 is designated by 127,
  • the pump suction line 120 is connected to the suction side of the pump b1 and its lower end dips into the hydraulic fluid reservoir of the tank or oil container a10.
  • a filler and emptying nozzle c8, a cylinder drain line 129 and the drain busbar 12 of servo valve b8 and the directional spools c4 and poppet valves c5, whose drain connection lines connected to 12 are designated 1 T or 122 or 123, also open into this reservoir a60 are.
  • Fig. 16 shows the section through an actuator, suitable for a live steam valve.
  • the pot-shaped housing a10 provides a welding con structure and is attached to the valve housing a13 via a column a14.
  • the central interior a100 of the housing a10 which is closed off with a lid d1, also serves as an oil container.
  • the piston rod on which the diaphragm spring column a7 is guided over bushings d2 passes through this.
  • the cylinder block d3 screwed onto the cover d1 contains all control assemblies, such as servo valve b8 or control valve c9 (FIG. 18), poppet valve c5 with pilot control c4, ventilation valve b400, displacement transducer b9 and binary position transmitter (not shown) for reporting the extreme positions "open” and “closed “, e.g. B. for automatic testing. These are protected by a screw-off hood d4, which forms the control room a120.
  • b400 serves to vent the pressure rail during commissioning and is located at the geodetically highest point of the compact drive.
  • the casing part of the housing a10 represents the supply space a110.
  • All the control fluid supply assemblies are arranged here: pumps b1, accumulator b2, filter b3, overflow valve b5 (not visible), check valves b6, pressure transducer b500, etc
  • the electric motors b10 are flanged, which penetrate the end wall bore a104 with shaft 110 and coupling 120 and drive the pumps b1 arranged in the supply space.
  • the housing a10 transfers the valve forces to the actuating cylinder a4 and is therefore, as can be seen, dimensioned with correspondingly large wall thicknesses. That also means something for him unpressurized oil chamber a100 oversizing the tank wall and thus maximum security against damage from the outside.
  • the piston rod a2 which is led from the oil chamber a100 through the seals d9 to the outside on the left and is made with a high surface quality, is protected against contamination with a hood el so that the surface condition is preserved and the seal d9 remains intact.
  • the combined gasket set d9 consists of 1 scraper ring, 2 guide rings and 2 sealing rings (not specifically identified).
  • the control liquid a60 is mainly cooled by natural heat exchange of the oil content via the tank wall a101. Depending on the permissible warm-up temperature of the pressure fluid and the load, it may be possible to do without a special coolant or without a heat exchanger. Natural cooling results from the large cooling surface of the housing wall with a102 cooling fins and from a small number of cycles.
  • Ventilation openings d7 in the cover d5 of the supply room a110 provided with air filters ensure ventilation of this room, which communicates with control room 120 via connecting channels e4 (indicated by dashed lines), which means that depending on the position of use L1, L2 or L3 (see section 3.2.4) any leak oil to the leakage oil collection point in control room a120 (in supply room a110) from supply room a110 (or from control room a120).
  • the cooling air emerging from the fan cowl e3 partly flows through the flange bores e5 along the housing a10 and provides additional oil cooling.
  • e7 in FIG. 19 means a filling and emptying nozzle for pressurized fluid, e71 the associated line, which ends with a mouthpiece e72 at the lowest point of the container, e73 are likewise pump suction lines that open into the fluid space a100 in an arrangement for the lying position L1 of the drive shown .
  • e8 in FIG. 16 means a pressure fluid return line which, coming from the overflow valve b5 (cf. FIGS. 3 and 15), opens into the fluid space a100.
  • E6 denotes the connector box attached to the container or housing a10, which will be explained further below (FIGS. 18 and 19).
  • SBF flame-resistant liquid, eg. B. phosphate ester, as a pressurized fluid connection of a regeneration loop, which has bleaching earth and mechanical filters as filters (not shown).
  • the casing of the container a10 has a tunnel-like cross section with an arch part a105, which has the cooling fins a102, and a reinforced, flat base a106, which forms a flat mounting surface for hydraulic elements of the supply space a110.
  • Line e73 in FIG. 8 corresponds to 120 in FIGS. 3 and 15, e8 corresponds to 128.
  • a series was developed for all live steam, interception and diverter valves, graded according to the nominal valve widths and steam pressure ranges.
  • the picture shows the size comparison of the drives for live steam and interception valves FV and AV, which are also used as variants for UV bypass valves.
  • Compact drives according to the invention are also suitable for driving rotary flaps as adjusting and quick-closing flaps for heating removal and as intercepting quick-closing and adjusting flaps. These are mounted in trunnions and transmit the actuating force via a crank mechanism as torque to the flap (not shown).
  • valves of the shaft seal steam control shall, where fast response times are necessary, vorzu g s-actuated also electro-hydraulic actuators, also with electrical actuation and internal oil supply.
  • a 36 bar actuator A01 (Fig. 29, 30) is compared with a compact actuator All (Fig. 31, 32) of the same output, suitable for a live steam control valve of nominal size 200.
  • the compact drive A11 has a slightly longer overall length.
  • Servo valve b8 and poppet valve c5 have no positive overlap of their control edges, so that the hydraulics respond smoothly and smoothly.
  • FIG. 35 shows the position spread PSB of the 50% actual position value over a time of approx. 15 minutes in a magnifying representation.
  • PA means the position deviation due to driving force.
  • F 21 restoring force F a7 and driving force F 1 applies F 1 - F 2 + F a7 (v g l. F i g . 34).
  • the tensile force (F 2 ) was gradually increased from 13,700 dN to approx. 37,700 dN.
  • the constant setpoint S const was 50%.
  • the largest positional deviation was 0.5 o / oo (approx. 0.1 mm).
  • the comparative value of today's drives is around 0.8%.
  • the table shows the performance data for various operating requirements.
  • pump b1 and motor b10 The design performance of pump b1 and motor b10 is relatively small compared to the high power output during control and quick-closing movements.
  • the power continuously output by the compact drive as the product of the delivery flow of the pump x circulating pressure and the leakage oil flow x system pressure is max. 20% of the design performance.
  • the compact drives are delivered from the factory as a "finished system”.
  • the operating medium After leaving the test field, the operating medium remains in the compact drive.
  • the stroke is already preset.
  • the hydraulic system is permanently set to the required pressure level so that time-consuming adjustment work is no longer necessary on the construction site.
  • the assembly is limited to flanging the valve and connecting the coupling halves.
  • the supply of electrical energy and the signal transmission takes place via a movable cable harness with a plug connection.
  • the overflow valve b5 which is connected to the pump pressure side (line 110) with the line section 1102, serves as an accumulator charging valve. It consists of a two-way seat valve b51 and a pilot valve b52, which are housed in a common housing, ie they can be structurally combined.
  • the two-way seat valve b51 is also referred to as a cartridge valve.
  • the overflow valve b5 with its two sub-valves b51, b52 is fundamentally controlled by the storage, pump and discharge pressure which prevails in the line sections 119, 1102, 128, so that its two-way seat valve b51 connects the pressure side of the pump b1 with the Connects the drain or the fluid reservoir of the fluid container a10 when the upper boost pressure p max of the pressure accumulator b2 is reached in the charging operation.
  • a check valve b6 connected downstream of the overflow valve b5 on the pressure side closes.
  • the overflow valve b5 thus generally speaking comprises a two-way seat valve b51 with an open, close and pressure valve function with an upstream pressure-dependent pilot stage b52, which in the exemplary embodiments according to FIGS. 3 to 5 and 15 as a pilot valve, and although also as a resilient spring-loaded seat valve, but of a special design, azs - is formed.
  • the pilot valve b52 represents a pressure-dependent hydraulic individual resistor with a holding function in the pressure interval between p max and p (normal case), which switches over when p ⁇ p m , i.e. also when the accumulator boost pressure falls below p m down to P min in the case extreme control processes.
  • the outer bush 521a is sealingly inserted into the bore 520 by means of 0-rings on its outer circumference
  • the inner bushing 521b is in turn sealingly inserted in this outer bushing by means of 0-rings on its outer circumference or the like
  • the latter with the mouth of its inner bore 522 serves as a valve seat for the spring-loaded ball 523, which is pressed against the valve seat by an approximately mushroom-shaped pressure piece 523a, on which one end of the spring 523b engages.
  • the other end of the helical compression spring 523b is seated on the spring abutment in the form of a plug 523d which is displaceably sealed in the spring bore 523c in the spring pressure direction.
  • the pressure piece 523a and the mouth of the bore 522 form approximately hemispherical seating surfaces for the ball 523.
  • the tension of the helical compression spring 523b can be adjusted by means of the adjusting bolt 523e can be set, which is screw-mounted and adjustable in the screw cap 523f and engages with its inner end in a recess of the spring abutment stopper 523d, not specified.
  • the screw cap 523f is secured against rotation (screw 523g).
  • a holding piston 524d is inserted into the bore or inner surfaces 524c of the bushing 524a, which is referred to below as the guide bushing and penetrates the inner bushing 521b in its bore 522 with a shaft or needle 525 and bears against the spherical body 523.
  • the accumulator pressure of the pressure rail 11 (see FIG. 3, FIG. 15) is supplied to the lower side of the holding piston 524d via the control line 119 and corresponding control bores 119.1.
  • the counterpressure on the other side of the holding piston 524d generates the spherical body 523 together with the compression spring, including the counterpressure prevailing in the annular space 526 which surrounds the spherical body 523, which is defined by the discharge pressure, because the annular space 526 via the bores or channels 1190 communicates with the interior a60 of the tank a10, as symbolized by the arrow T.
  • the line 1191 is branched from the pump pressure side of the two-way seat valve b51, as shown, via a suitable housing channel;
  • the arrow P and the reference number 1102 of a dashed line section indicate that the line 1191 is connected to the pump pressure line 110.
  • the construction of the two-way seat valve b51 is somewhat simpler than that of the pilot valve b52 described: it has a spring-loaded piston 510 within the piston receiving bore 511 of the housing part 502, a return spring for the piston 510 being designated 512.
  • the piston 510 seals the pump pressure line 1102 from the drain line 128 leading to the tank with its newspaper parts 128.1 arranged in the housing b502 (see arrow T).
  • a free space 511a of the bore b511 is left in the switch position shown, in which the piston 510 can be immersed in its open position.
  • the restricted pressure on the pump pressure side is brought to this free space via housing channel 1103.1 and the line branch 1103.
  • FIG. 5 shows the associated circuit diagram in the detail of the circuit according to FIG. 3 or FIG. 15, but in more detail.
  • the same parts as in FIG. 4 are provided with the same reference symbols.
  • the usual symbol representation in accordance with ISO1219 shows the pilot valve b52 with 2 line connections 1191 and 1191 ', line piece 1191' symbolizing the control pressure function and line 1191 together with the bent arrow and the opposite discharge line 1190 symbolizing the switching or shut-off function.
  • overflow valve b5 (FIG. 4) and its circuit (FIG. 5) results as follows: First, assume operating state I (charging operation), in which the two-way seat valve b51 is closed. Its piston 510 is acted upon by the same pump pressure on the two piston sides; it is therefore pressed by its helical compression spring 512 onto the seat surfaces 513 of the channel mouth. The pilot valve b52 is also closed because the pump pressure, which extends through line 1191 and the throttle point b53 into the interior 522 of the inner bush 521b, is not yet large enough to lift the ball 523 from its seat.
  • the upper boost pressure P max is reached, ie if the accumulators b2 are charged, then the ball 523 is lifted off its seat and the pressure prevailing in the space 522 and in the line 1191 behind the throttle b53 is increased by the Annulus 526 and channels 1190 in the tank, see arrow T, removed. Because of this momentary pressure drop, the holding piston 524c can now be shifted upward from the storage pressure p max via line 119 and channels 119.1 in the illustration shown, so that it holds the ball 523 in the open position with its pin 525.
  • the low pressure level on the outlet side propagates within the line 1191 to the throttle point b53 and is also communicated via the line branch 1103 and the inner channels 1103.1 to the inner side of the piston 510 of the two-way seat valve b51, which, because on its outside via line 1102 the pressure of the pump pressure side in the discharge operation of z. B. 2 bar is present, is shifted to the open position, that is, it lifts off its seat surfaces 513, so that the pump now conveys through channels 128.1 and line 28 into the outlet a60 of the tank a10.
  • This operating state can be referred to as unloading operation or circulating operation (II). It serves to relieve the pump and to save energy.
  • the working capacity of the accumulators b2 in the charged state down to the lower charge pressure p m is sufficient to master all control processes.
  • a discharge of the memory b2 also takes place without control processes due to the inevitable leakage losses of the hydraulic consumers connected to the pressure rail 11, eg. B. the electro hydraulic servo valve b8 or the directional spool valve c4 or the seat valve c5 instead.
  • an electro-hydraulic pilot control can also be used for the two-way seat valve b51 by the pressure transducer shown in FIG. 16, which measures the pressure in the pressure rail 11 and converts it into an analog electrical quantity. controls a solenoid valve, not shown, which in turn connects line 1191 to the outlet when p max is reached and is reversed by the pressure sensor b500 when the storage pressure drops to p m so that it with its slide switch interrupts the connection from line 1191 to the drain.
  • the hood e3 has a hood extension e31, shown in dashed lines, which surrounds the housing or the container a10 with an annular gap e32 up to approximately the axis-normal plane of the coupling a1.
  • the cooling air is forcibly guided past the cooling fins a102 of the container a10. It then emerges at the mouth e330 of the annular space e33, as is shown by the arrows e30.
  • the cooling with the extended hood e3, e31 provides a better heat supply compared to that with the short hood e3 according to FIG. 9A.
  • the hood extension e31 preferably surrounds the container a10 in the peripheral region of the cooling fins a102, at least approximately in a semicircular shape.
  • a stop body 514 is provided on the bottom of the piston receiving bore 511, which has a plate-shaped foot part 514a and carries a spring plate 514c on a shaft part 514b, which rests in the unspecified spring receiving bore of the piston 510 can immerse.
  • the stop body 514 is provided with slots (not visible) for the passage of the pressure medium from the channel 1103.1 to the free space 511a.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fluid-Pressure Circuits (AREA)
EP84102385A 1983-03-16 1984-03-05 Positionneur compact du type électro-hydraulique pour vannes de turbines Withdrawn EP0119543A3 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE3309421 1983-03-16
DE3309421 1983-03-16
DE3400488 1984-01-09
DE19843400488 DE3400488A1 (de) 1983-03-16 1984-01-09 Elektrohydraulischer kompaktantrieb fuer ventile von turbomaschinen, insbesondere turbinen

Publications (2)

Publication Number Publication Date
EP0119543A2 true EP0119543A2 (fr) 1984-09-26
EP0119543A3 EP0119543A3 (fr) 1985-12-18

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Application Number Title Priority Date Filing Date
EP84102385A Withdrawn EP0119543A3 (fr) 1983-03-16 1984-03-05 Positionneur compact du type électro-hydraulique pour vannes de turbines

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US (1) US4627235A (fr)
EP (1) EP0119543A3 (fr)
DE (1) DE3400488A1 (fr)
ES (1) ES530746A0 (fr)
IN (1) IN162683B (fr)

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US6962944B2 (en) 2001-07-31 2005-11-08 Arqule, Inc. Pharmaceutical compositions containing beta-lapachone, or derivatives or analogs thereof, and methods of using same
US7074824B2 (en) 2001-07-31 2006-07-11 Arqule, Inc. Pharmaceutical compositions containing beta-lapachone, or derivatives or analogs thereof, and methods of using same

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US5490765A (en) * 1993-05-17 1996-02-13 Cybor Corporation Dual stage pump system with pre-stressed diaphragms and reservoir
DE19719080C1 (de) * 1997-04-30 1998-09-10 Mannesmann Ag Elektrohydraulisches Betätigungsgerät für Bremsen für Industrieanlagen
JP3890229B2 (ja) * 2001-12-27 2007-03-07 株式会社コガネイ 薬液供給装置および薬液供給装置の脱気方法
JP3947398B2 (ja) * 2001-12-28 2007-07-18 株式会社コガネイ 薬液供給装置および薬液供給方法
CN1815041A (zh) * 2005-02-06 2006-08-09 何扬东 一种混凝土泵液压系统辅助蓄能增流装置
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US4627235A (en) 1986-12-09
ES8501051A1 (es) 1984-11-01
IN162683B (fr) 1988-07-02
DE3400488A1 (de) 1984-09-20
ES530746A0 (es) 1984-11-01

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