EP0104272B1 - Dispositif servomoteur actionné par fluide sous pression - Google Patents

Dispositif servomoteur actionné par fluide sous pression Download PDF

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Publication number
EP0104272B1
EP0104272B1 EP82109580A EP82109580A EP0104272B1 EP 0104272 B1 EP0104272 B1 EP 0104272B1 EP 82109580 A EP82109580 A EP 82109580A EP 82109580 A EP82109580 A EP 82109580A EP 0104272 B1 EP0104272 B1 EP 0104272B1
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EP
European Patent Office
Prior art keywords
piston
control valve
chamber
pressure
valve
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.)
Expired
Application number
EP82109580A
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German (de)
English (en)
Other versions
EP0104272A1 (fr
Inventor
Steffen Paulo Russak
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.)
Sulzer AG
Original Assignee
Gebrueder Sulzer 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 Gebrueder Sulzer AG filed Critical Gebrueder Sulzer AG
Publication of EP0104272A1 publication Critical patent/EP0104272A1/fr
Application granted granted Critical
Publication of EP0104272B1 publication Critical patent/EP0104272B1/fr
Expired legal-status Critical Current

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Classifications

    • 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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
    • F15B2211/30575—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve in a Wheatstone Bridge arrangement (also half bridges)
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/321—Directional control characterised by the type of actuation mechanically
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional control characterised by the type of actuation actuated by fluid pressure
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/35—Directional control combined with flow control

Definitions

  • the invention relates to a pressure medium-actuated servomotor arrangement according to the preamble of claim 1.
  • Such a servomotor arrangement for actuating steam isolation valves has been proposed, in which the two control valves are influenced from the control room via two electrical control lines.
  • This arrangement therefore has the disadvantage that two external lines are required from the control room to the servomotor in order to move the piston of the servomotor arrangement from a first to a second position.
  • the second control valve is actuated due to an action of the first control valve, there is no need for a second external control line, which increases the operational reliability of the servomotor.
  • a relatively expensive and relatively fault-sensitive solenoid valve can be saved.
  • clear safety-related conditions are created. Since the second control valve is cheaper and less prone to failure than a solenoid valve, it is well suited for redundancy switching.
  • the arrangement according to claim 2 has the advantage that when the control valves are closed, the rear seat seal prevents the piston from flowing around and therefore no pressure medium is consumed in one piston position.
  • the arrangement according to claim 3 brings the safety-related advantage that if the first control valve breaks, the servomotor moves from the normal position into the safety position.
  • the arrangement according to claim 4 prevents destruction of the second control valve by external force.
  • the arrangement according to claim 6 relates to a particularly advantageous second control valve which is of very simple construction and at the same time meets high safety requirements.
  • a piston 2 is slidably arranged in a cylinder 1.
  • the piston is drawn in its normal position, that is, in the position it takes up when the system is operating under normal conditions. It divides the interior of the cylinder 1 into two piston chambers 4 and 6 abutting the piston 2.
  • Each of these piston chambers 4 and 6 is, for example, connected via a separate connecting line 8. 9 with a pressure medium source 13 and another, separate connection line 10, for example. 11 connected to a pressure medium sink 14.
  • each of the connecting lines 8 to 11 of each piston chamber there is a first control valve 16 or a second control valve 18 and in each of the other two connecting lines a throttle element 20, 22 is arranged.
  • the first control valve 16 is connected to an external control line 24.
  • the second control valve 18 is actuated by a membrane 30 via a rod 32.
  • the membrane divides a pressure space into a chamber 34 facing the control valve 18 and a chamber 36 facing away from the control valve.
  • a compression spring 38 acts on the membrane 30.
  • the chamber 36 is connected via an internal control line 40 to the piston chamber 4 or 6 to which the first control valve 16 connected to the external control line 24 is connected.
  • the camera 34 which is connected via an internal control line 41 to the piston chamber to which the first control valve 16 is connected.
  • the chamber 34 is connected to the pressure medium source 13 via a connecting line 42.
  • the chamber 36 is connected to the pressure medium sink via a connecting line 43.
  • the piston 2 acts via a piston rod (not shown in FIG. 1) on a movable system part (also not shown).
  • the piston rod can protrude from the cylinder 1 towards the top, towards the bottom or on both sides mentioned.
  • the servomotor arrangement functions as follows: During normal operation of the arrangement, the piston 2 is in its upper stroke end position. A digital plus signal is present at the first control valve 16 via the control line 24, which - like the arrow on the control line - does this symbolized - the first control valve 16 keeps closed. Accordingly, a pressure builds up in the piston chamber 6 by supplying medium via the throttle element 20, which pressure is the same as the pressure in the pressure medium source 13. The same pressure prevails in the chambers 34 and 36 of the second control valve 18, the valve 18 is therefore held in the closed state by the compression spring 38. In the piston chamber 4, due to pressure compensation via the throttle element 22, the pressure is the same as in the pressure medium sink 14. Since the pressure in the pressure medium source 13 is considerably higher than in the pressure medium sink, the piston 2 is pressed into the upper stroke end position with great force.
  • the first control valve 16 opens.
  • the pressure in the piston chamber 6 drops to a value depending on the size of the throttle device 20 and the flow cross section of the connecting line 11 , which is close to the pressure of the pressure medium sink 14.
  • This drop in pressure propagates into the chamber 36 via the internal control line 90 and results in the control valve 18 being opened.
  • the pressure in the piston chamber 4 now rises to a value which is close to the pressure of the pressure medium source.
  • the piston moves quickly into the lower stroke end position. It remains there until a plus signal occurs in the external control line 24, so that the first control valve 16 closes.
  • the arrangement according to FIG. 1 b) functions as follows: in the normal state, the first control valve 16 is closed under the effect of a flow signal in the external control line 24 and the second control valve 18 is also in the closed position. If the signal in the external control line 24 drops, the first control valve 16 opens, the pressure in the piston chamber 4 increases and propagates via the control line 41 into the chamber 34 of the second control valve 18. The resulting pressure difference on the membrane 30 outweighs the force of the compression spring 38, so that the second control valve 18 opens. The pressure in the piston chamber 6 decreases, and the piston 2 thus moves into the lower stroke end position.
  • the first control valve 16 in contrast to the arrangements according to FIGS. 1a) and 1b) - the first control valve 16, as indicated by the arrow on the external control line 24, is open in the normal position and also the control valve 18 If the external control signal drops, the first control valve 16 closes, the pressure in the piston chamber 4 increases and, as a result, the second control valve 18 also closes, so that the pressure in the piston chamber 6 drops and the piston 2 shifts to the lower stroke end position.
  • both control valves are open in the normal state.
  • a higher pressure is present in the piston chamber 6 than in the piston chamber 4.
  • the first control valve 16 is now closed due to the drop in the control signal in the external control line 24, the pressure in the piston chamber 6 and in the chamber 34 drops, as a result of which the second Control valve 18 closes under the action of the compression spring 38. This increases the pressure in the piston chamber 4 and the piston 2 moves to the lower stroke end position.
  • the valve 16 responds to a drop in the control signal in the external control line 24 by opening, while it is closed in the normal position.
  • the two control valves 16 and 18 are each in the opposite position, that is, when the control valve 16 is closed, the control valve 18 is open and vice versa. If the control valve 16 is now opened from the normal position, a pressure builds up in the piston chamber 4 as well as in the chamber 36. On both sides of the diaphragm 30, the pressures keep the equilibrium, so that the compression spring 38 closes the second control valve 18. As a result, the pressure medium escapes from the piston chamber 6 via the throttle element 22 and the piston moves into the lower stroke end position.
  • control valves are analogous to Figure 1e), each in the opposite position.
  • the first control valve 16 opens when the signal in the external control line 24 drops.
  • the first control valve 16 is opened, the pressure in the piston chamber 6 and in the chamber 34 drops.
  • the control valve 18 closes, causing the piston chamber 4 comes under pressure and the piston 2 moves to the lower position.
  • the first control valves 16 are in the open position in the normal position; they drop when the external control signal drops. Based on the previous statements, it should be easy to understand that the second control valves 18 open and the pistons move into the lower stroke end position.
  • the servomotor arrangement comprises a valve which is open in the normal position. Its housing 50 with an inlet connection 51 and an outlet connection 52 together with a cover 54 forms the cylinder 1 of the servomotor arrangement, in which the piston 2. is axially displaceable.
  • a piston rod 56 is arranged coaxially therewith, which runs through the piston chamber 6, penetrates the adjoining cylinder base 58 and carries a closure part 60 at its end projecting into a valve chamber 53.
  • a peripheral sealing surface 62 of the closure part 60 interacts with a valve seat 64 in the interior of the valve chamber 53.
  • the piston 2 is provided on its side facing away from the piston rod 56 in the region of its circumference with the rear seat 48 which interacts with a matching counter surface 49 in the cover 54.
  • the cover 54 is fastened in a gas-tight manner to an upper flange surface 66 of the valve housing 50 using screws, not shown.
  • the servomotor arrangement according to FIG. 2 is directly comparable with the embodiment variant according to FIG. 1a) and extends from the piston chamber 6, here through multiple broken bores, connecting line 11 to the outer wall of the housing where it ends openly.
  • the connecting line 11 is drilled radially from the outside, forming a valve seat, and this tapping is surrounded by a threaded blind hole.
  • the connection piece 68 of a solenoid valve 70 which corresponds to the first control valve 16, is screwed into this threaded blind hole.
  • the solenoid valve 70 contains an axially displaceable part 73 within a direct current coil 72, which consists of a valve spindle 74, a collar 75 and an armature 76.
  • a compression spring 78 which acts on the collar 75, is supported on the bottom of the threaded blind hole.
  • the compression spring 78 pushes the displaceable part 73 to the left, so that the blocking of the connecting line 11 is released.
  • the connecting line 9 extends in a U-shape from the upper region of the valve chamber 53 into the lower zone of the piston chamber 6.
  • the valve chamber 53 forms the pressure medium source.
  • the throttle element 20 is formed by a screw 21 which plunges radially into the connecting line 9 and is adjustable by turning the screw. It should be noted here that FIG. 2 is to be understood in part as a diagram. The bores that are shown in the plane of the drawing are in reality partially spatial. Therefore, the screw 21 can be adjusted from the outside.
  • the internal control line 40 connects to the connecting line 9 at the top, which leads to a system of three stepped bore sections 80, 87, 86.
  • the same system of bore sections can be seen on the right side of Figure 3 on an enlarged scale.
  • a piston 82 is slidably arranged in the first bore section 80 and carries a support piston 85 via a conical transition piece 83 and a cylindrical neck 84.
  • the support piston 85 slides in a third bore section 86, which has a considerably smaller diameter than the first bore section 80.
  • An annular chamber 88 located between the first and the third bore section is formed by a second bore section 87, which extends over a short, conical section 89, which serves as a valve seat, is connected to the third bore section 86.
  • the annular chamber 88 corresponds to both the inlet chamber of the control valve 18 and the chamber 34 from FIG. 1a).
  • the connecting line 42 therefore forms part of the connecting line 8. It is connected together with a section of the connecting line 9 to the valve chamber 53.
  • a bore corresponding to the connecting line 8 branches off laterally, which runs through the flange surface 66, continues in the cover 54 and opens into the piston chamber 4
  • a vent hole 90 then leads from the upper, free end of the third bore section 86 to the atmosphere.
  • a threaded blind hole 92 is made in the cover 54, the bottom of which is connected to the piston chamber 4 via a short bore, which corresponds to the connecting line 10, and part of the connecting line 8.
  • the threaded blind hole 92 there is a hollow screw 93 which together with the threaded blind hole forms the throttle element 22.
  • the threaded blind hole is basically conical, and the banjo bolt also ends conically at the bottom.
  • a central hole in the hollow screw bifurcates at its lower end, so that two openings open into the conical part of the banjo bolt.
  • the passage cross-section between the conical parts of the hollow screw 93 and the threaded blind hole 92 can be changed by screwing the hollow screw more or less deeply into the threaded blind hole.
  • the throttle member 22 is thus adjustable.
  • the servomotor arrangement according to FIG. 2 operates as follows: the closure part 60 of the valve is in its normal position; in the present case the valve is open. A pressure medium flows under relatively high pressure through the inlet connector 51 and the outlet connector 52. Accordingly, the valve chamber 53 is also under pressure. A positive signal is present in the external control line 24, so that current flows in the DC coil 72 and the armature 76 is pulled to the right; the valve spindle 74, overcoming the force of the compression spring 78, rests on its seat and thereby blocks the connecting line 11. The pressure in the piston chamber 6 is the same as in the valve chamber 53, since it communicates with the valve chamber 53 via the connecting line 9 and the throttle element 20.
  • the pressure in the valve chamber 53 is further present in the space of the first bore section 80 formed beneath the little cup 82 and in the annular chamber 88 on the little boy 82.
  • the pressure effect on the small piston 82 is balanced over a fictitious ring surface with the diameters of the third bore section 86 and the first bore section 80.
  • On a fictitious circular surface with the diameter of the third bore section 86 there is an upward pressure difference, since on the free, upper side of the support piston 85 atmospheric pressure and on the free end face of the piston 82 the pressure in the piston chamber 6, the pressure in the valve chamber 53 is the same.
  • the conical transition piece 83 is therefore seated on the valve seat 89, where it blocks the connecting line 8. Atmospheric pressure therefore prevails in the piston chamber 4 since it communicates with the atmosphere via the throttle element 22.
  • the pressure difference on the piston 2 pushes it upward, the rear seat 48 sealingly resting on the counter surface 49.
  • the power supply to the solenoid valve 70 is interrupted, for example arbitrarily from a control room or automatically by a safety signal, its valve spindle 74 lifts from its seat under the action of the compression spring 78 and pressure medium flows out of the piston chamber 6 via line 11 into the atmosphere out. Since not enough pressure medium can flow in via the throttle element 20, the pressure drops in the piston chamber 6 and also in the space below the piston 82. However, since the full pressure of the pressure medium flowing through the valve is still present in the annular chamber 88, the piston 82 moves downward, thereby releasing the valve cross section at the valve seat 89, pressure medium flowing through the connecting line 8 into the piston chamber 4, and there in the Valve chamber 53 builds up prevailing pressure. As a result of the pressure difference now developing on the piston 2, the latter undergoes an acceleration downward and the closure part 60 sits on the valve seat 64. The valve is closed.
  • the pressure medium sink is then advantageously equipped with a filter.
  • control valve 18 has the same function as the second control valves 18 in examples a), c), e) and g) in FIG. 1, but is simplified compared to those since no rod 32 with the Atmosphere comes into contact with what Sliding seals, such as stuffing boxes, would require.
  • control valves 18 A further, important modification of the control valves 18 is shown using the example of a control valve 18 'adjacent to the pressure medium source on the left-hand side of FIG. 3.
  • a neck 84 and a support bulb 85 are omitted from the bulb 82 ', on the other hand it has an axial blind bore 95 with a spring 96 which is supported at the base of the first bore portion 80'.
  • This embodiment of the second control valve 18 has the advantages of the simpler construction, the elimination of a ventilation bore 90 and the elimination of the support piston 85 and a third leading bore section.
  • the support piston and the latter bore section would require increased machining accuracy, since they must run coaxially with the piston 82 and the first bore section 80, respectively.
  • the second control valve 18, doubled can be arranged in two parallel connecting lines 8.
  • the first control valve 16 will also be doubled in many cases, the two control valves 16 also being arranged in parallel in the cases mentioned.
  • FIG. 3 shows a redundancy circuit of two control valves 18, 18 'that is suitable, for example, according to FIG. 2.
  • the two parallel branches unite to form the connecting line 8 in the bore section designated with an outlet tip 100.
  • the internal control line 40 bifurcates at point 101 and leads from there to the lower ends of the first bore sections 80 and 80.
  • control valve 18 If the control valve 18 is open in the normal position of the piston 2, as shown in cases c), d), g) and h) of FIG. 1, two control valves 18 will be connected in series and not in parallel to form a redundancy . Analogous considerations also apply to the first control valve 16.
  • the arrangement according to FIG. 2 has the particular advantage that, in the event of external influences on the servomotor arrangement - be it that the external control line 24 or the solenoid valve 70 is destroyed or that the valve spindle 74 is torn away even in connection with the destruction of the solenoid valve 70 - move the servomotor and thus also the valve to the safety position.
  • pressure medium source and possibly also more than one pressure medium sink, selection circuits being able to be selected such that the pressure medium source with the highest pressure and the pressure medium sink with the lowest pressure are used. It is conceivable, as an alternative, to provide a point below the valve seat and / or an auxiliary pressure source, for example an auxiliary steam generator, as a pressure medium source in the case of valves controlled by the own medium.
  • auxiliary pressure source for example an auxiliary steam generator
  • FIG. 4 shows a structurally particularly elegant solution for attaching the second control valve, where the control valve 18 'is intelligently arranged in the piston 2 or in the piston rod 56. This solution prevents the connecting line 8 from penetrating the flange surface 66.
  • the control valve 18 'according to FIG. 4 can be combined with a control valve 18 according to FIG. 2 for redundancy purposes.
  • a tapered closure part is attached to the lower end face of a cylindrical cologne via a short neck, the thinner end of which is turned towards the cologne. It is supported by a compression spring basically an outlet chamber which is connected to the piston chamber 6.
  • the outlet chamber ends with a seat on the conical surface of the closure part. On the other side of the seat there is an annular chamber which is connected to the pressure medium sink.
  • a guide bore for the cologne pushes against the pressure chamber, which is closed at the top and is connected to the piston chamber 4 via the control line 40.
  • the servomotor arrangement according to the invention is suitable for bringing the piston into an upper or a lower end position and holding it there.
  • a position transmitter is arranged on the piston, the position signal of which is subtracted from a setpoint signal given by the control room.
  • the control deviation formed in this way is then applied to the first control valve 16, preferably via an I-element.
  • the piston 2 oscillates more or less quickly around the desired intermediate position.
  • control valves 16, 18 can be designed as valves instead of open / close valves, which also assume certain intermediate positions depending on the input signal.
  • adjustable throttle bodies 20, 22 fixed constrictions can also be provided.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Servomotors (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Actuator (AREA)
  • Electrically Driven Valve-Operating Means (AREA)

Claims (6)

1. Groupe servomoteur à commande par fluide sous pression, présentant un piston (2) coulissant dans un cylindre (1) et par l'intermédiaire duquel deux chambres à piston (4, 6) attenantes à ce piston sont formées dans le cylindre, chacune des chambres à piston (4, 6) étant reliée par l'intermédiaire de son propre conduit de jonction (8, 9) à une source (13) de fluide sous pression, et étant raccordée, par l'intermédiaire d'un autre conduit de jonction propre (10, 11), à une source (14) de dépression du fluide; une valve de commande (16; 18) étant incorporée dans l'un des deux conduits de jonction (8, 10; 9, 11) de chaque chambre à piston et l'autre conduit de jonction (10, 8; 11, 9) de chaque chambre à piston renfermant un organe d'étranglement (20, 22); et une première (16) des deux valves de commande étant par ailleurs raccordée à un conducteur externe de commande (24), caractérisé par le fait que la seconde valve de commande (18) est réalisée de telle sorte qu'elle puisse être actionnée par un fluide sous pression et puisse être reliée, par l'intermédiaire d'un conduit interne de commande (40,41), à la chambre à piston à laquelle est raccordée la première valve de commande (16) reliée au conducteur externe de commande (24); et par le fait que, dans une position de branchement de la première valve de commande (16) et dans la position de branchement associée de la seconde valve de commande (18), l'une (6) des chambres à piston est soumise à une pression et la pression est détendue dans l'autre chambre à piston (4), tandis qu'en revanche, lors d'une commutation de la première valve de commande (16) et d'une commutation de la seconde valve de commande (18), provoquée par l'intermédiaire du conduit interne de commande (40, 41), la pression est détendue dans l'une (6) des chambres à piston et l'autre chambre à piston (4) est soumise à une pression.
2. Groupe servomoteur selon la revendication 1, caractérisé par le fait que le piston (2) présente une étanchéité de siège postérieur (48), au moins du côté par lequel il vient en butée dans la position normale.
3. Groupe servomoteur selon la revendication 2, caractérisé par le fait que la valve de commande (16) reliée au conducteur externe de commande (24) est fermée dans la position normale du servomoteur.
4. Groupe servomoteur selon l'une des revendications 1 à 3, caractérisé par le fait qu'au moins la seconde valve de commande (18) est intégrée à l'intérieur des limites du servomoteur.
5. Groupe servomoteur selon l'une des revendications 1 à 4, dans lequel le cylindre (1) est relié à un carter de valve (50) et le piston (2) est relié, par l'intermédiaire d'une tige (56), à une pièce obturatrice (60) située dans ledit carter de valve, caractérisé par le fait que le conduit d'admission (51) dans le carter de valve (50) sert de source de fluide sous pression.
6. Groupe servomoteur selon l'une des revendications 1 à 5, caractérisé par le fait que la seconde valve de commande (18') présente une partie d'obturation (82') agissant contre une surface de siège (89') et reliée à un piston muni d'une surface de pression, qui agit dans la direction de fermeture de la partie d'obturation et est reliée à la chambre à piston (6) à laquelle la première valve de commande (16) est raccordée; par le fait que la surface de pression du piston située du côté de la partie d'obturation est raccordée à la source de fluide sous pression; par le fait qu'une zone de raccordement, située au-delà de la surface de siège (89') observée à partir du piston, est reliée à l'autre chambre à piston (4); et par le fait qu'il est prévu un moyen (96) qui charge dans la direction de la fermeture la partie d'obturation (82') de la seconde valve de commande (18').
EP82109580A 1982-09-17 1982-10-16 Dispositif servomoteur actionné par fluide sous pression Expired EP0104272B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH5510/82A CH657675A5 (de) 1982-09-17 1982-09-17 Druckmediumbetaetigte stellmotoranordnung.
CH5510/82 1982-09-17

Publications (2)

Publication Number Publication Date
EP0104272A1 EP0104272A1 (fr) 1984-04-04
EP0104272B1 true EP0104272B1 (fr) 1986-07-23

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Application Number Title Priority Date Filing Date
EP82109580A Expired EP0104272B1 (fr) 1982-09-17 1982-10-16 Dispositif servomoteur actionné par fluide sous pression

Country Status (7)

Country Link
US (1) US4513943A (fr)
EP (1) EP0104272B1 (fr)
JP (1) JPS5973606A (fr)
CA (1) CA1225291A (fr)
CH (1) CH657675A5 (fr)
DE (1) DE3272175D1 (fr)
ES (1) ES524393A0 (fr)

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Publication number Priority date Publication date Assignee Title
CH659111A5 (de) * 1982-12-15 1986-12-31 Sulzer Ag Druckmittelbetaetigte stellmotoranordnung mit arretierglied.
US4862788A (en) * 1988-03-28 1989-09-05 Hans Bauman Valve positioning device
US5139663A (en) * 1991-03-14 1992-08-18 Microlift Systems Limited Partnership Discharge valve for dissolved air flotation
US6749173B2 (en) * 2002-09-27 2004-06-15 The Hartfiel Company Valve arrangement and method of directing fluid flow
US20220196181A1 (en) * 2020-12-23 2022-06-23 Goodrich Corporation Inflatable systems with electro-pneumatic valve modules

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US2769912A (en) * 1954-04-12 1956-11-06 Phillips Petroleum Co Shut-off valve
FR1104921A (fr) * 1954-05-18 1955-11-25 Pyper Maroc Dispositif de commande de l'ouverture et de la fermeture des vannes équipées d'un pot de presse
US2928606A (en) * 1957-08-30 1960-03-15 Willin C Lee Solar thermostat control unit
US3277791A (en) * 1965-03-30 1966-10-11 Gen Electric Motion responsive devices
GB1270797A (en) * 1968-09-30 1972-04-12 Lucas Industries Ltd Fluid operated servomechanism
SE364112B (fr) * 1972-06-19 1974-02-11 Alfa Laval Ab
CH652814A5 (de) * 1980-12-19 1985-11-29 Sulzer Ag Mediumgesteuerte absperrventilanordnung.
FI68458C (fi) * 1980-12-23 1985-09-10 Sulzer Ag Tvaongsstyrdaonggeneratoranlaeggning

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US4513943A (en) 1985-04-30
JPS5973606A (ja) 1984-04-25
DE3272175D1 (en) 1986-08-28
EP0104272A1 (fr) 1984-04-04
ES8406108A1 (es) 1984-07-16
CH657675A5 (de) 1986-09-15
CA1225291A (fr) 1987-08-11
ES524393A0 (es) 1984-07-16

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