EP0425621A1 - Soupape de limitation de pression comportant un piston a gradins ou un double piston - Google Patents

Soupape de limitation de pression comportant un piston a gradins ou un double piston

Info

Publication number
EP0425621A1
EP0425621A1 EP90906875A EP90906875A EP0425621A1 EP 0425621 A1 EP0425621 A1 EP 0425621A1 EP 90906875 A EP90906875 A EP 90906875A EP 90906875 A EP90906875 A EP 90906875A EP 0425621 A1 EP0425621 A1 EP 0425621A1
Authority
EP
European Patent Office
Prior art keywords
valve
piston
pressure relief
spring
relief 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.)
Withdrawn
Application number
EP90906875A
Other languages
German (de)
English (en)
Inventor
Richard Voss
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.)
Voss Richard Grubenausbau GmbH
Original Assignee
Voss Richard Grubenausbau GmbH
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
Priority claimed from DE3916260A external-priority patent/DE3916260A1/de
Priority claimed from DE19893922894 external-priority patent/DE3922894A1/de
Priority claimed from DE19893929094 external-priority patent/DE3929094A1/de
Application filed by Voss Richard Grubenausbau GmbH filed Critical Voss Richard Grubenausbau GmbH
Publication of EP0425621A1 publication Critical patent/EP0425621A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
    • F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
    • F16K17/0446—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with an obturating member having at least a component of their opening and closing motion not perpendicular to the closing faces
    • F16K17/046—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with an obturating member having at least a component of their opening and closing motion not perpendicular to the closing faces the valve being of the gate valve type or the sliding valve type
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7781—With separate connected fluid reactor surface
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7837—Direct response valves [i.e., check valve type]
    • Y10T137/7904—Reciprocating valves
    • Y10T137/7922—Spring biased
    • Y10T137/7925—Piston-type valves

Definitions

  • the invention relates to a pressure relief valve for the protection of hydraulic units, in particular the hydraulic longwall construction in underground mining and tunnel construction against sudden overloading as a result of rock blows or similar effects, with the valve housing arranged in the valve housing and displaceable therein against the force of the valve spring and the inlet bore provided on one side of the valve piston equipped with a blind bore and end-side radial bores and the outlet bores provided on the other side of the valve piston, the valve piston passing over an O-hole which can be passed over by the radial bores. Ring is sealed.
  • pressure relief valves also known as safety valves
  • safety valves are used where there is a risk of damage to the hydraulic system due to overloading, in particular in underground coal mining in the form of hydraulic rams.
  • These hydraulic stamps are used both as individual stamps and integrated in expansion racks, especially shield removal racks. Due to the particular danger, the use of pressure relief valves is prescribed by the supervisory authorities in the case of shield removal frames of this type, but also in the case of hydraulic stamps, in order to prevent permanent damage or even destruction and thus dangers to the miners in the event of overloading.
  • a pressure relief valve is known from DE-OS 28 3o 891, in which overpressures in the hydraulic system are reduced by means of a valve spring which is clamped between the screw plug and the valve piston.
  • a conical or spherical valve 1 closing body is molded onto the valve plate or spring plate, which, when an overload occurs, arises from the Valve seat is raised.
  • a damping cylinder is formed on the piston and limits the throughflow opening.
  • Such valve closing bodies do not, however, provide the necessary closing security for the intended use as pressure limiting valves or rocking valves.
  • a correct design, in particular the spring is very difficult, but this is a prerequisite for a reliable response of such a rocket valve.
  • valve housing 1 the valve spring is arranged in such a way that it presses on the valve plate and thus on the valve piston and thus influences the opening of the valve according to the setting.
  • the valve piston is displaceably guided on a piston bore formed in the guide, the necessary sealing being carried out via an O-ring seated in a groove.
  • the O-ring must always be completely covered by the radial bores of the valve piston in order to ensure problem-free operation or timely response of the valve and, on the other hand, to ensure the longest possible service life for the O-ring.
  • the blind bore formed in the valve piston and connected to the piston bore can be reached via the radial bores, so that when the O-ring is passed over, the pressure medium can flow out of the hydraulic unit to be protected.
  • a disadvantage of these known pressure relief valves is the low flow values of 40 to 60 or a maximum of 100 liters per minute. This is unsatisfactory for the necessary safety and in particular the quick responsiveness of such valves.
  • Another disadvantage is that the valve springs used must have considerable wire thicknesses and helix diameters due to the pressures to be taken into account, which in turn requires corresponding dimensions for the entire valves. The greater the flow rate accordingly, the larger the valve springs and thus the entire valve housing must become. But then, especially in underground coal mining, such pressure relief valves can no longer be used simply because of the excessively large dimensions, quite apart from the fact that the necessary cross sections for removing the pressure medium are not available.
  • the invention is therefore based on the object of creating a pressure-limiting valve with a large flow rate (over 10,000 liters per minute) but small dimensions (valve spring, spring chamber) and acceptable closing values.
  • valve piston is designed as a continuous tubular sleeve with a large outflow area and has an approach serving as a control piston and has a reduced diameter and on both sides of the outlet bore designed as a transverse bore, sealing rings and thereby separated, acted upon with the same pressure Spaces inside and above the Venti 1 kol ben and that the control piston rests on the spring plate loaded by the valve spring.
  • control piston Because of the one-piece construction, it is possible to equip the control piston with such a small diameter that initially there are favorable differential areas and, in addition, due to the assignment of the valve spring to this control piston, a valve spring with extremely favorable values, that is to say low Ab ⁇ measurements can be used. Due to the valve spring with low wire thickness and corresponding spring forces, a small valve housing can be used, in which the valve spring can be easily integrated. In addition, the control piston now simultaneously becomes a pressure-limiting valve which, as such, already allows a flow rate of around 4oo liters per minute.
  • the actual Valve piston can also allow a much larger flow rate of 2ooo liters per minute and more due to its favorable dimensions, that is, its large discharge area, so that a valve is created that surely has more than looo liters per minute flow rate.
  • the clever discharge of the pressure medium also improves the closing values from the area of the control piston.
  • a further improvement in the closing values is achieved by using sealing rings which have low coefficients of friction.
  • the spring chamber is separated via an intermediate wall from the inlet bore, which merges into the transverse bore serving as an outlet bore below the intermediate wall, that the valve piston forms a structural unit with the control piston, which unit with a the inner blind bore and radial bores extending from the blind bore and which moves in a bore formed in the intermediate wall with an O-ring! ch is guided and that the spaces are connected via through-flow bores formed in the cover of the valve 1.
  • a favorable design is achieved by inserting the control piston in the center of the cover and by Flow bores are arranged in a circle around it.
  • the control piston can be produced, for example, by turning off the valve piston in the upper region.
  • the through-flow bores ensure that the valve piston is in equilibrium under normal pressure conditions, so that the cross bores are effectively closed. Only when the pressure is increased can the small control piston then perform its function by moving the valve plate against the force of the valve spring and at the same time moving the valve piston, so that pressure medium can escape from the area of the valve piston and the control piston at the same time . As a result, the necessary relief of the hydraulic unit is achieved until the excess pressure is released, whereupon the pressure limiting valve closes again immediately.
  • the rapid and precise response is ensured according to the invention in that the control piston has an outer ring groove in the attachment area.
  • the transverse bores extend obliquely outwards from an annular channel. This reduces the deflection of the pressure medium flow to a minimum.
  • valve piston has an outer radius of 25 mm and the control piston has lo mm. It is also provided that the valve piston is equipped with 12 radial bores with a diameter of 5 mm and the control piston with 6 radial bores with a diameter of 2.5 mm, so that the corresponding amounts of pressure medium can also be safely removed.
  • sealing rings possibly also the O-ring
  • Such sealing rings which are no longer flexible, nevertheless lead to an effective seal, have extremely long service lives and allow the above-mentioned favorable closing values to be achieved because the friction between the sealing ring and the valve piston is reduced to a minimum. This is particularly the case if the sealing rings are rectangular in cross section.
  • Such sealing rings lead to a flat seal without the friction occurring substantially reducing the movement of the valve piston.
  • valve pistons in the form of the continuous tubular sleeve with a very large diameter, which in turn contributes to an increase in the permissible and possible flow rate.
  • the sealing rings are arranged in sealing grooves which are open at the top and bottom and are fixed by means of a push-in sleeve or a screw guide, which also represents the intermediate wall .
  • the push-in sleeve is advantageously acted upon by the pressure of the pressure medium and fixed in the connecting piece without the need for a lock or a screw connection.
  • the screw guide on the other hand, is screwed in from the spring chamber and effectively fixes the upper sealing ring without it being able to move out of its position in the assigned ring groove during operation.
  • a further embodiment of the invention provides that the control piston is formed through the intermediate wall of the tubular sleeve-shaped valve piston and is toothed with it in the opening direction of the valve as a stepped piston with a differential area.
  • the differential areas in the transition area between the control piston and the valve piston can be specified, with the toothing of the valve piston and Control piston is ensured that both each perform the same movements or that the control piston takes the valve piston with it and forces it into the respective position.
  • the difference surfaces are specified in particular in that the valve piston merges into a type of tappet, the pressure medium penetrating through the blind bore of the valve piston as usual, then further into the corresponding inner pocket bore of the control piston and from there via the end-side radio holes reaches the spring chamber, so that the same pressure is built up on both sides of the transverse bores.
  • the difference surface that is to say the pressure surface, is then only predetermined by the plunger already mentioned, or rather, the guide shoulder. Uneven movement of the control piston and the valve piston are precluded by the fact that the control piston is mounted in the intermediate wall of the valve piston 1 and is guided in the set screw.
  • valve piston is designed as a tubular sleeve with a closed intermediate wall, that the spaces are designed as ring channels and are connected to one another via housing bores running parallel to the valve axis, and that the tubular sleeve has a diameter reduction in the opening direction on the outside.
  • No pressure medium quantities need to be displaced here, only the quantities present in the ring area, whereby a quick and precise response of the valve is still possible with favorable spring dimensions.
  • the small wire diameter of the valve spring allows favorable dimensions, whereby the special design ensures that the additional channels can be placed so that the dimensions of the valve are not affected.
  • the ring channels and the housing bores connecting them are so cleverly housed that neither the diameter or the width of the pressure limiting valve has to be changed, nor the length of the Valve housing.
  • connection to the plunger in the case of single plunger valves can be accomplished easily and quickly, since the connection piece with the inlet bore has an external connection thread.
  • the seal to the connecting hydraulic part can be easily accomplished by equipping the connecting piece on the free surface with an annular groove and an outer O-ring.
  • the intermediate wall has a throttle bore and that the diameter reduction is formed in the transition area between the intermediate wall and the spring space on the tubular sleeve.
  • the spring chamber and vestibule are connected by a throttle bore, the same pressure is initially established on both sides of the intermediate wall. Therefore, if an overload occurs, the O-ring or sealing ring is quickly passed over through the radial bores and thus a rapid escape of the pressure medium, whereby springs with a spring characteristic with a small pitch can be used, so that with relatively small and tight-fitting springs can be worked.
  • the diameter reduction ensures a correct displacement of the valve piston against the force of the valve spring, which has an extremely favorable spring characteristic. Likewise, due to this design, if the overload is removed, the valve piston is retracted, and thus the hydraulic system used for support measures is activated.
  • the response of the valve piston is particularly safe sets when the diameter reduction is formed to give a pressure surface difference of 0.08 to 0.2 cm 2 .
  • the invention is particularly characterized in that a very small pressure relief valve with high flow rates, that is, with flow rates of looo to 3ooo liters per minute is created, which due to its favorable dimensions can be used practically anywhere in underground mining and also in other areas. This is achieved by means of the measures and features which do not or only slightly influence the manufacturing outlay, the safe and simple setting of the entire pressure limiting valve being provided.
  • the favorable dimensions are achieved, in particular, in that springs with a spring characteristic with a small pitch are used, which ensure a favorable response behavior of the pressure relief valve with an extremely small space requirement.
  • the functioning of the valve is ensured by favorable closing values by using suitable sealing rings.
  • the use of a 1-piston valve with a very large discharge area ensures the flow rate of 10,000, 2,000 and more liters per minute, so that the special conditions in underground coal mining can be taken into particular account.
  • Fig. 1 is a pressure relief valve in longitudinal section with step piston, in the closed and open state
  • Fig. 2 is a pressure relief valve with two parts
  • a pressure relief valve with a valve piston designed as a tubular sleeve and lateral
  • Fig. 1 shows a pressure relief valve (1) in the two possible positions.
  • the open position of such a pressure relief valve (1) is shown on the right side and the closed position on the left side.
  • the valve housing (2) is shown in section so that the individual parts can be seen.
  • the valve housing (2) consists of an upper part (3) with an internal thread (4) and a connector (5) with an external thread (6).
  • the external thread (5) is approximately congruent with the external connection thread (9), via which such a pressure relief valve can be connected, for example, to a hydraulic ram, ie it can be screwed on.
  • the connector (5) has an inner bore, which also represents the inlet bore (13) for the pressure medium.
  • the valve piston (10) which in the present case is designed as a tubular sleeve (20), is inserted into this inlet bore (13).
  • the valve piston (lo) has a blind bore (14) which merges into radial bores (15, 16).
  • the radial bores (15, 16) are separated from the ring channel (18) and the transverse bores (17) via the sealing ring (19) when the valve is closed.
  • the pressure medium coming from the inlet bore (13) penetrates into the pressure-limiting valve (1), and thus cannot exit via the blind bore (14) and the radial bores (15, 16) when the valve is closed.
  • the lower edge (28) of the transverse bore (17), as shown in the left half of FIG. 1, lies above the radial bores (15, 16) which are sealed or separated from the sealing ring (19).
  • the outer wall (29) of the valve 1 piston (lo) or "of the tube sleeve (2o) is continuously smooth, so that normal friction occurs when the sealing ring (19) is passed over.
  • the valve spring (11) is supported on the adjusting screw (12) and on the spring plate (26), on which the control piston (6o) bears.
  • the valve spring (11) arranged in the spring chamber (22) can thus effectively load the control piston (6o) in such a way that it and therefore also the valve piston (lo) can only open when the set spring force is exceeded.
  • the valve spring is adjusted using the adjusting screw (12), which can be adjusted in the head part (38) in the inner bore (39) using the thread (4o). It has an internal hexagon (44) to simplify the setting.
  • valve piston (lo) in the form of the tubular sleeve (2o) takes place once, as already mentioned, via the lower sealing ring (19), which is accommodated in an annular groove (55) and, on the other hand, via the one in the annular groove ( 5o) arranged upper sealing ring (51).
  • These sealing rings consist of the lowest possible friction-generating plastic (Teflon).
  • This cover (79) is provided with throughflow openings (8o, 81) so that the pressure medium in the blind bore is present both in the space (47) and in the space (46) above it, i.e. on both sides of the valve piston (lo).
  • the valve piston (10) thus hovers in the position shown in the left half of FIG. 1, as long as the pressure conditions set via the valve spring (11) are maintained.
  • the pressure medium also flows through the control piston (60), which has an inner pocket bore (62) and radial bores (63, 64) arranged at the end. It is sealed over the O-ring (75), so that only when driving over this O-ring (75) through the radi al bores (63, 64) pressure medium can penetrate into the spring chamber (22). To do this, the force of the valve spring (11) must be overcome. Since the outer wall (65) of the control piston (6o) is smooth, on the other hand the O-ring (75) has a relatively small diameter, the frictional forces are so low here that the closing values of the valve are not affected .
  • a through hole (68) is provided in the adjusting screw (12) through which the pressure medium can escape into the open.
  • this through bore (68) is closed by a dirt valve.
  • This dirt valve 1 is formed by a sealing bolt (95) which has a seat (96), so that, as can be seen from the left half of Fig.
  • the flow of the pressure medium is hampered as little as possible via the plate ring (98) by providing it with recesses (99).
  • the spring (loo) as such is secured via the guide (lo2), so that the valve spring (11) and the spring (loo) cannot get caught or influence each other.
  • an outer annular groove (83) is formed, by means of which the response of the valve during the return stroke is significantly improved.
  • the sealing rings (19, 51) rub out of the outer wall (29) of the valve piston (lo) in order to keep the valve tight.
  • this friction intentionally leads to an impairment but only a slight impairment of the movement sequence because the sealing rings (19, 51) consist of Teflon or a similar plastic.
  • the lower sealing ring (19), which is accommodated in the annular groove (55), can be easily installed despite its low flexibility, since in the inlet bore (13) a push-in sleeve (85) is inserted from the opening direction (61).
  • This plug-in sleeve (85) is secured at the bottom by the O-ring (86) and the support ring (87) and at the top by the O-ring (88) and the support ring (89).
  • the upper sealing ring (51) can also be easily installed, since it is fixed by the screw guide (9o), which is sealed via the O-ring (91) and the support ring (92).
  • the mounting of the screw guide (9o) is facilitated by the recess (93), which enables screwing into the thread without problems.
  • the opening (78) of the inlet bore (13) is so far widened that the push-in sleeve (85) is inserted just as easily as the screw guide (9o) can be screwed in.
  • valve 1 shows on the right half an open pressure-limiting valve (1), it becoming clear that the pressure medium is now, for example, unobstructed through the inlet bore (13) into the pressure-limiting valve (1) due to the overloading of the associated hydraulic unit ) can occur to pass through the blind bore (14) and the radial al bores (15, 16) in the annular channel (18). From there it closes via the cross bores (17) from the pressure relief valve. Due to the relatively large diameter of the valve piston (lo), which has an outer radius of 25 mm and due to the 12 radial bores (15, 16), each with a diameter of 5 mm, a flow rate of over 2ooo liters per minute is ensured.
  • the pressure medium flows through the control piston (6o) and its inner pocket bore (62) up to the radial bores (63, 64) into the spring chamber (22). From here, after the sealing bolt (95) has been lifted, it reaches the area of the set screw and through the through hole (68) to the outside. If the pressure peak is released, the valve spring (11) presses the control piston (6o) and thus the valve piston (11) more or less freely through the sealing rings (19, 51) and the O-ring (75) Valve piston (lo) in the position shown in the left side of Fig. 1 back. Then the pressure relief valve (1) is closed again and the effectiveness of the associated hydraulic unit is ensured.
  • valve piston (10) and control piston (6o) form a movement unit.
  • the control piston (6o) is toothed in the opening direction (61) with the valve piston (lo) so that both perform the same movements.
  • the control piston (6o) is equipped with an inner blind bore (62) adjoining the blind bore (14) and end-side radial bores (63, 64), so that the pressure medium in the spring chamber (here also serving as the upper space (46)) 22) can penetrate.
  • the valve piston (10) is thus in equilibrium, since the same pressure conditions are present both in the space (46) and in the space (47).
  • the valve spring (11) is housed between the outer wall (65) of the control piston (6o) and the inner wall (37) of the valve piston (lo).
  • the difference surface (66) is achieved in that the control piston (6o) is equipped with a guide projection (67) which forms an inner groove (71) on the inner piston and is inserted into the through bore (68) of the adjusting screw (12) reaches in.
  • a guide is achieved through the locking plate (7o).
  • the O-ring (75) provides the necessary seal.
  • the O-ring (75) is secured by the retaining nut (74), which is screwed into a corresponding thread.
  • the adjusting nut (12) is in turn sealed via the O-ring (76).
  • valve housing (2) consists of the upper part (3) with an internal thread (4) and the connecting piece (5) with an external connection thread (9).
  • the screw connection as such is secured by the O-ring (7), so that the pressure medium cannot escape through this screw connection, while the outer O-ring (8) at the lower end of the connection piece (5) is secure and tight Ensures connection with the hydraulic unit to be protected.
  • Fig. 3 shows an embodiment in which the valve spring
  • (11) receiving spring chamber (22) is separated by an intermediate wall (23) from the so-called antechamber (24), that is, the room (47).
  • the intermediate wall (23) runs at right angles to the valve axis (21).
  • the intermediate wall (23) can also serve as a spring plate (26). However, a separate spring plate is provided here, which rests loosely on the intermediate wall (23).
  • the outer wall (29) of the tubular sleeve (2o) has two diameters.
  • the diameter reduction (3o) in the closed state of the pressure relief valve (1) is approximately in the area of the lower edge (28) of the transverse bore (17).
  • an O-ring seal (31) is provided in addition to the sealing ring (19 and 51).
  • the O-rings (31) lie in the annular groove (32).
  • the annular channel or space (47) is connected to the blind bore (14) or the inlet bore (13) via the radial bores (49).
  • the wall of the radi al bores (49) serves at the same time for connecting the groove (55) in which the sealing ring (19) is located.
  • the inner wall (33) and the outer wall (34) of the valve housing (2) are arranged at such a distance that a sufficiently strong wall is secured for the valve housing.
  • the housing bore (48) is accommodated, which connects the two spaces (46, 47) or the ring channels.
  • valve housing (2) In the area of the connector (5), the valve housing (2) has a section (52) on the outside with the external connection thread (9).
  • the outer O-ring (8) lies in an annular groove (54) in the free surface (53) of the connecting piece (5).
  • the connection of the two spaces (46, 47) or of the spring space (22) and antechamber (24) is achieved by a throttle bore (25) in the partition (23 ) is formed and which via the spring plate (26) with the bore (27) ensures a connection between the spring chamber (22) and the vestibule (24).
  • the same pressure is also established in the spring chamber (22) and the vestibule (24) via this throttle bore (25).
  • the diameter reduction between the lower and upper part is 25 to 24.7 mm. Due to the difference in pressure area of, for example, 0.1 cm 2 , a valve spring (11) with a particularly favorable spring characteristic, namely with a small pitch, can be used. Due to the spring wire dimensions and the overall height, this valve spring (11) with a favorable spring characteristic has such a small space requirement that the entire pressure relief valve has favorable dimensions.
  • the entire pressure relief valve (1) is sealed from the outside by the ring groove (35)

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Safety Valves (AREA)

Abstract

Une soupape de limitation de pression présentant des coefficients de débit de 3000 litres par minute et plus est caractérisée par un piston à soupape (10) en forme de douille, disposé de manière coulissante dans le sens longitudinal du corps de soupape (2), contre l'effort d'un ressort de soupape (11). La soupape (1) est subidivisée en deux chambres (46, 47). Le piston à soupape (10) constitue avec le piston pilote rapporté (60) une unité de construction, le piston pilote dont le diamètre est inférieur étant chargé par la cuvette de ressort (26) et le ressort de soupape (11). Le ressort de soupape (11) est réglable de sorte que la valeur d'ouverture de la soupape de limitation de pression (1) peut être déterminée d'avance. La configuration particulière du piston à soupape à gradins (10) avec piston pilote (60) permet d'utiliser des cuvettes de ressort (11) ayant des effets de ressort et des dimensions relativement faibles, de façon que la soupape tout entière présente elle aussi des dimensions relativement avantageuses. La réponse de la soupape de limitation de pression est assurée grâce à la conception à gradins du piston à soupape (10)/piston pilote (60) et des bagues d'étanchéité (19, 51) mises en oeuvre qui se trouvent à l'extérieur sur le piston à soupape (10) à diamètre important, sans entraver sensiblement son mouvement par l'effet de la friction. Malgré cela, l'étanchéité est assurée, car les bagues d'étanchéité (19, 51 et également 75) présentent une grande résistance et une faible friction.
EP90906875A 1989-05-19 1990-05-10 Soupape de limitation de pression comportant un piston a gradins ou un double piston Withdrawn EP0425621A1 (fr)

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
DE3916260 1989-05-19
DE3916260A DE3916260A1 (de) 1989-05-19 1989-05-19 Kleinbauendes druckbegrenzungsventil mit grosser durchflussmenge
DE19893922894 DE3922894A1 (de) 1989-05-19 1989-07-12 Kleinstbauendes druckbegrenzungsventil mit grosser durchflussmenge
DE3922894 1989-07-12
DE19893929094 DE3929094A1 (de) 1989-07-12 1989-09-01 Gebirgsschlagventil mit doppelkolben
DE3929094 1989-09-01

Publications (1)

Publication Number Publication Date
EP0425621A1 true EP0425621A1 (fr) 1991-05-08

Family

ID=27199588

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90906875A Withdrawn EP0425621A1 (fr) 1989-05-19 1990-05-10 Soupape de limitation de pression comportant un piston a gradins ou un double piston

Country Status (7)

Country Link
US (1) US5180443A (fr)
EP (1) EP0425621A1 (fr)
AU (1) AU633915B2 (fr)
CA (1) CA2033066A1 (fr)
HU (1) HU208563B (fr)
PL (1) PL285245A1 (fr)
WO (1) WO1990014500A1 (fr)

Families Citing this family (15)

* Cited by examiner, † Cited by third party
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Publication number Publication date
US5180443A (en) 1993-01-19
AU5555690A (en) 1990-12-18
HU904364D0 (en) 1991-08-28
CA2033066A1 (fr) 1990-11-20
HU208563B (en) 1993-11-29
AU633915B2 (en) 1993-02-11
PL285245A1 (en) 1991-01-28
HUT57381A (en) 1991-11-28
WO1990014500A1 (fr) 1990-11-29

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