• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The invention relates to a hydraulic pipe, line or hose break safety shutoff valve (20) for shutting off a supply channel (22) against a discharge channel (25), the channels (22, 25) open into an axial bore (27) of a valve housing (28). in that a locking piston (41) acted upon by a spring (61) is displaceably mounted. The blocking piston (41) has a valve cone (19) which, in the blocking position of the blocking piston (41), sealingly abuts against a valve seat (30) of a valve seat body (30) projecting radially inwards into a space bounded by the valve cone (43) , It is a in the axial bore (27) extending, expandable stopper body (36) for limiting an opening stroke of the locking piston (41) provided on which this in its open position acted upon by the spring (61). Alternatively or additionally, a safety shut-off valve (46) arranged in front of the blocking piston (41) is provided for shutting off the feed channel (22), which has a shut-off element (54) rotatably mounted in the valve housing (28) about an axis of rotation (53) is selectively transferred from an open position into a safety shut-off, in which an inflow of the hydraulic medium via the supply passage (22) to the locking piston (41) is prevented.
    公开号:AT13195U1
    申请号:TGM212/2012U
    申请日:2012-05-15
    公开日:2013-08-15
    发明作者:
    申请人:Neumeister Hydraulik Gmbh；
    IPC主号:
    专利说明:

    Austrian Patent Office AT13195U1 2013-08-15
    The invention relates to a hydraulic safety shut-off valve, in particular a pipe, line or hose break safety shut-off valve for shutting off a supply channel which can be connected to a pump or connected to a hydraulic consumer, for example a hydraulic cylinder, in particular a hydraulic balancing cylinder. for or from a truck, preferably for or from a heavy transport vehicle, in particular via a high-pressure hose to be secured, connectable or connected discharge channel, wherein the supply channel and the discharge channel open into an axial bore extending in the direction of an axial bore of a valve housing, in the Locking piston is slidably mounted in the axial direction, which is acted upon by the spring force of a spring in the axial direction, whereby the locking piston up to a certain, a value greater than zero amounting Grenz Strömungsgeschwindig speed of a hydraulic medium is held in an open position in which the hydraulic medium can flow from the supply passage in the discharge channel, and vice versa, and wherein the blocking piston due to exceeding the limit flow rate of the hydraulic medium and a resulting pressure difference, against the spring force the spring, is transferred from its open position into a blocking division or is transferred, in which the supply passage is shut off from the discharge channel, wherein the locking piston has a valve cone with a conical surface, in the blocking division of the locking piston on a valve seat of a radially inward in one of the conical surface of the valve cone limited space projecting into valve seat body, preferably the valve housing, sealingly.
    In such safety valves are flow-controlled, single-acting or blocking in a flow direction seat check valves. These are used to prevent a load loss caused by pressure loss and are used in particular where at a burst or damage to a pressurized by a fluid medium hollow body, such as a pressure line or a pressure hose, or in the event of such accidents, danger is in default. Such safety check valves are used, for example, as a ballast in single-acting axle compensation cylinders in heavy transport vehicles. Since such Achsausgleichszylinder are movably installed, serves as the last oil supply line in front of the hydraulic cylinder always a high-pressure hose piece, which is for example 0.5 to 1 meter long. In such Achsausgleichszylindern several cylinders in cylinder groups are often combined hydraulically and connected to each other via a pressure line which can be supplied by a pump with hydraulic medium. The cylinder groups can also be hydraulically combined and connected to one another in a conduit, preferably crosswise. A safety shut-off valve is installed in front of each axle compensation cylinder with high-pressure hose. Because in the event of bursting or damage, especially leading to one of the hydraulic cylinder high-pressure hose, fall - if not such a safety check valve - possibly together with the high-pressure cylinder connected hydraulic cylinder, so that there is a leakage of the oil and consequently to a tilting or crashes of a load can occur, which must be prevented absolutely.
    During a normal driving process with different weights load the same hydraulically interconnected Achsausgleichszylinder unevenness of the infrastructure. Thus, if an axle unit, which can be formed with a pair of wheels on a rocker arm with a hydraulic Achsausgleichszylinder, drives over an obstacle, so for example on road bumps, larger stones, wooden beams, curbs and the like, displaces the Achsausgleichszylinder oil in the corresponding or with this interconnected other axle compensation cylinder elsewhere of the vehicle. During this balancing process, oil flows from a supply passage into a drain passage in the safety valve, and vice versa.
    The safety valve can now be designed so that the flow rate does not exceed a certain size, ie a certain limit or switching flow rate or a certain volume flow in this process. As a result, a correspondingly large pressure loss or a pressure difference, as a result of which the safety valve closes, occurs in the case of such safety valves shut off depending on the flow velocity or on exceeding a certain flow velocity. Now, if the extremely rare accident, such as a hose or pipe or line break, which may be the case, for example, by heavy rockfall or as a result of a passing between the wheels metal part, so breaks between the affected Achsausgleichszylinder and the upstream safety valve system or oil pressure abruptly together. As a result, in the safety valve between the supply channel and the discharge channel, a correspondingly large flow velocity of the oil and consequently a correspondingly large pressure loss or a correspondingly large pressure difference which is greater than the limit or switching flow velocity or which is greater than the limit - Or switching pressure difference, so that the safety shut-off valve closes immediately and thus prevents the oil drain over the other connected to this line or circuit Achsausgleichszylindern. The failed cylinder-axle unit runs free from this moment, as completely relieved, with. The entire load distribution now takes over the remaining axle units. In such an accident, the driver, who can be signaled this accident in a suitable manner automatically, for example, by means of electronic pressure control systems, properly break the journey and repair or repair the damage.
    A flow-dependent switching, damped closing hydraulic pipe break valve with the features of the preamble of claim 1 has become known from DE 2 352 826 A. However, this pipe break valve is constructed comparatively complicated and is therefore relatively complex and expensive. The assembly and disassembly of such a pipe break valve or its valve elements is relatively complex and this pipe break valve requires comparatively much space due to its construction. In addition, in this pipe break valve, the movement of the locking piston from its open position into its blocking division in two stages successively, namely first, in a first closing phase, unthrottled or undamped, ie with a high closing speed, and then, in a second closing phase, shortly before maximum pressure drop is reached, throttled or damped, so a reduced closing speed, which drops to zero, in which case the pipe break valve locks. For this purpose, special space consuming switching and throttle means are required. The applications for this pipe break valve are relatively limited by design.
    From DE 10 2009 043 568 A1, a double-acting or a blocking in opposite flow directions hydraulic pipe, line or hose break safety valve has become known, regardless of the flow direction of the hydraulic medium and regardless of whether the to be secured by the valve, pressurized with the fluid medium under pressure hollow body, in particular the pipe to be secured, the line to be secured or the hose to be secured on the first channel associated valve side or on the second channel associated valve side breaks or fails Depending on the flow rate or of the flow rate of the hydraulic medium, automatically and safely closes or shuts off. Although this safety valve combines a multitude of advantages in itself, it has been shown in practice that overuse of the hydraulic consumer can occur in rare cases. This safety valve has an axially displaceable plunger shaft, which acts as a valve position indicator. To seal the tappet shaft a total of four seals are required. As a result, it can lead to a correspondingly increased friction, with the result of a correspondingly poorer response of the locking piston or its valve cone. This safety valve is by design still comparatively complex and still takes up comparatively much space.
    It is therefore an object of the invention to provide a safety shut-off valve of the type mentioned at the outset which, given advantageous flow and switching conditions and favorable possibilities for a Damped or time-delayed closing and space-saving integrated, additional safety shutdown of the supply channel relative to the discharge channel and for a sensitive, so precise and repeatable response of the locking piston or its valve cone, is particularly easy to assemble or disassemble, particularly space-saving or compact and comparatively is simple and is particularly simple and inexpensive to produce and in which the risk of overuse of the hydraulic load is minimized.
    This object is achieved by a safety shut-off valve according to claim 1, in particular in that a transversely, preferably perpendicular, extending to the axial axis extending into the axial bore stop body for limiting an opening stroke of the locking piston is provided, which acts on the locking piston in its open position is applied by the spring force of the spring, and wherein the stopper body is attached to or in the valve housing such that it for the purpose of disassembly or assembly of the locking piston from a Hubbegrenzungsstellung in which it limits the opening stroke of the locking piston, in an on or In the extended position, in which the locking piston can be removed or installed and / or that, viewed in the inflow of the hydraulic medium from the supply channel in the discharge channel, arranged in front of the locking piston, integrated, safety stopcock, preferably ball valve, for Shut off the supply duct an inflow of the hydraulic medium is provided to the locking piston or to shut off the supply passage relative to the discharge channel having a rotatably mounted in the valve housing, about a rotation axis rotatable, the axial bore transversely, preferably perpendicular to the axial axis passing obturator, optionally from an opening position in which an inflow of the hydraulic medium through the supply channel to the locking piston is possible, can be converted into a safety shut-off, in which an inflow of the hydraulic medium via the supply passage to the locking piston is prevented, and wherein the axis of rotation of the obturator in the area one or in an imaginary plane containing the axial axis of the axial bore, preferably perpendicular to the axial axis, is arranged.
    By such an arrangement and attachment of such a stopper body can be a significant manufacturing simplification at the same time advantageous opportunities for favorable flow and switching conditions and a space-saving integrable safety shutdown of the supply channel relative to the drainage channel and for a particularly simple assembly and disassembly of both the stopper body reach the locking piston.
    By such an arrangement of such a safety shut-off valve and its obturator can achieve a significant manufacturing or processing and installation simplification. In an integration of such a safety shut-off valve designed as a fixed pressure line feed channel can be closed manually or mechanically against the drainage channel even in cases where there is no pipe or hose or hose break, for example, in a repair or maintenance case or at a so-called "lifts", for example, of individual axle units, so that they can be mechanically bolted.
    By a combination of said measures, in addition to the above advantages, a total of particularly compact and space-saving safety check valve can be provided.
    The safety check valve according to the invention may preferably be used as a hose break safety check valve in heavy duty vehicles to hedge Achsausgleichszylindern, which have a hydraulic hose as the last link in front of the mobile working cylinders. Between each cylinder-hose unit and the fixed leads of the groupwise interconnected or connected cylinder, a safety valve according to the invention can be installed, which at hose break, in 3/19 Austrian Patent Office AT 13 195 Ul 2013-08-15
    Direction of the affected cylinder immediately hermetically tight closes.
    The safety shut-off valve according to the invention is a flow-controlled, one-way check valve, which immediately opens again when pressure relief or when flowing through the hydraulic medium in the opposite direction. This means that after a possible closing of the valve, without a hose, pipe or line break is present, which can occur, for example, in the mentioned application, in a fast driving over potholes or obstacles due to the large flow velocities occurring, the safety shut-off valve automatically opens in the opposite direction. After closing the safety check valve, for example, due to the passing of a large pothole, the safety check valve automatically opens after retiring from the pothole again, not only because of the locking piston acting on the restoring forces of the spring, but also additionally supported by a slight pressure increase occurring on the cylinder side.
    In the flow-controlled, single-acting safety check valve according to the invention, the risk of overuse of the hydraulic consumer, for example in the mentioned application, the cylinder or cylinder-piston unit, minimized. The safety shut-off valve thus automatically locks only in case of hose, pipe or pipe breakage, but not in cases where it could lead to the formation of an overpressure in or in the hydraulic consumer, so that this pressure can otherwise degrade.
    According to an advantageous embodiment it can be provided that the stop body is received or stored in its Hubbegrenzungsstellung either at one end of its ends facing away from each other in a transverse bore of the valve housing or received at its ends facing away from each other in each case a transverse bore of the valve housing or stored.
    According to a preferred embodiment it can be provided that the transverse bore or at least one transverse bore or each transverse bore is designed as a through hole which is open on the one hand to a housing side of the valve housing and the other opens into the axial bore, so that with, preferably low , Play in the through hole or in the through holes or in the other transverse bore, recorded or mounted stop body from the affected side of the housing from mountable or dismountable to the affected side of the case. This allows a very simple assembly and disassembly of the stopper body and transfer of the stopper body from its Hubbegrenzungsstellung in an on or extended position, in which the locking piston can be particularly easy on or removed.
    It is particularly advantageous if the stopper body is detachably connected to the valve body again so that it is completely removable, so it is then handled separately. This allows a simple complete replacement or a particularly simple assembly or disassembly.
    When the stopper body is arranged and secured in its Hubbegrenzungsstellung such that a projecting into the axial bore part of the stopper body in the open position of the locking piston of the hydraulic medium, preferably completely, in the axial direction is flowed around or is flowed around, can be at advantageous possibilities for a particularly simple, cost-effective and space-saving design, further improved flow and switching conditions.
    According to a particularly preferred embodiment it can be provided that the stopper body is designed as a, preferably cylindrical, in particular circular cylindrical, stop pin or stop bolt. This allows a particularly simple, inexpensive and compact design and allows a particularly simple assembly and disassembly and advantageous flow and switching conditions.
    Conveniently, the stopper body in its Hubbegrenzungsstellung with 4/19 Austrian Patent Office AT 13 195 Ul 2013-08-15
    Help a releasable stopper body securing means, for example by means of a screw plug, in particular a hexagon socket screw to be secured against falling out of the transverse bore or from the transverse bores. At the same time can be achieved with the help of the stopper-securing means a securely sealed closure of the transverse bore or the respective transverse bore.
    If, according to an advantageous embodiment, the obturator viewed in the inflow of the hydraulic medium from the supply passage in the discharge, is arranged in front of the stopper body and / or disposed between the stopper body and a supply port for connecting a supply line, a whole particularly compact design and further simplified assembly or disassembly ratios can be achieved.
    According to one embodiment, it can be provided that the discharge channel is designed with a valve housing in a transverse direction, preferably perpendicular to the axial axis, passing through hole, which is open to facing away from the housing sides of the valve housing and with a first through-bore part a first housing side of said housing side is provided with a first terminal for connecting a first line to be secured and which is provided with a second through-hole portion on a second housing side of said housing sides with a second terminal for connecting a second line to be secured, and wherein a closure means , Preferably a closure screw, is provided, by means of which or by means of which either the first port or the second port against leakage of the hydraulic medium can be closed. This allows a further simplified installation of Sicherheitsabsperrventils or more appropriately ausgestalteter Sicherheitsabsperrventile, a seitenzugeordneter connection of securing hollow bodies, such as pipes, tubes or hoses, is particularly easy. This is particularly advantageous if several safety check valves are needed and if they are each equipped with the safety stopcock arranged according to the invention, because then actuation of the respective obturator is possible from the same side.
    It can be provided that the through hole or its through-hole parts extend in the direction of a transverse axis, which is arranged transversely, preferably perpendicular to the axis of rotation of the obturator of the safety stopcock, preferably wherein the obturator is actuated from a housing side or is, which transversely, preferably perpendicular, away from the transverse axis. As a result, the above advantages can be realized to a particular degree.
    In a further preferred embodiment of the invention can be provided that the locking piston has an opening extending in the axial direction, in particular a blind hole, which is open to one of its valve cone end facing away and the or the radially is delimited on the outside by a cylindrical piston wall, which, viewed in a cross section perpendicular to the axial axis, is annular and has a receiving space for receiving a spring part of the out in the open position of the locking piston protruding therefrom, designed as a compression spring, the one end directly or indirectly supported on an inner wall of a spring support body of the locking piston and the other end is supported directly or indirectly on the valve housing in the clamped state. As a result, not only a favorable guidance and support of the compression spring can be achieved, but also possibilities for an exact guidance of the locking bolt in the axial bore. By these measures, the safety valve according to the invention in a particularly secure storage and management of its locking piston and, in advantageous ways for an exact centering of the locking piston relative to the valve seat, even more compact and space-saving executable or executed.
    It can be provided according to a particularly preferred embodiment, that the piston wall has a cylindrical outer surface and an outer diameter and on its cylindrical outer surface on a cylindrical inner surface of the axial bore, vorzugsvor. 5/19 Austrian Patent Office AT13195U1 2013-08-15 a housing part, supported over a certain guide length, which is always, that is also in the open position of the locking piston, at least half as large as the outer diameter of the piston wall, preferably at least equal to or greater than the outer diameter of the piston wall. As a result, an exact guidance of the locking bolt in the axial bore can be achieved, so that the locking bolt can be displaced with certainty without interference, in particular without tilting, relative to the axial bore in the axial direction.
    Furthermore, it can be provided that the safety shut-off valve is provided with a damping device for damped or time-delayed closing of the locking piston, by means of which over the entire closing of the locking piston a damped or delayed closing of the locking piston is effected or which over the entire closing path the blocking piston causes a damped or time-delayed closing of the locking piston. In this way, the closing speed of the locking piston over the entire closing path, ie its stroke between its maximum open position and its closed position, be kept constant and depending on the selected damping or throttling can set the value of the closing speed. This also makes it possible to intercept any pressure and flow peaks which may occur during normal operation of the safety shut-off valve such that the valve does not strike or close while the valve is in case of malfunction, ie if the hollow body to be secured by means of the safety valve fails or breaks. especially a pipe, a pipe or a hose, sufficiently fast, safe and tight closes.
    It can be provided according to a preferred embodiment, that it is at the damping means at least one, preferably a single, provided in one or in the piston wall of the locking piston, radially from the inside outwardly extending through hole, via which the hydraulic medium located in the receiving space then, when the blocking piston is transferred from its maximum open position or from an open position into its blocking division, flows throttled into the discharge channel. As a result, a particularly simple and inexpensive construction is possible and the safety shut-off valve can work very effectively and safely. The height or the value of the closing speed can be adjusted depending on the selected inner diameter of the through hole.
    According to a further improved embodiment, it can be provided that the locking pin has a ring groove which, considered in a cross section containing the axial axis, V- or U- or trapezoidal may be designed and which may be limited by a conical surface of the poppet, which forms a valve seat associated with the first groove side of the groove and further from an adjoining this conical surface, extending away from the latter in the axial direction groove bottom cylindrical surface of a connecting body and finally from a conical surface of a or the spring support body of the locking piston Supporting the spring, wherein said conical surface forms a second groove side of the groove and adjoining the conical surface of the valve cone, adjoining the groove bottom cylindrical surface, wherein the conical surface of the valve cone and the conical surface of the spring support body with the axial axis one, preferably approximately equal huge, acute angle, preferably each about 45 degrees, include, and wherein the valve cone, the connecting body and the spring support body, preferably the entire locking piston, are made in one piece or is. As a result, particularly favorable flow and switching conditions and a simple and inexpensive construction can be achieved.
    It can be provided that extends the groove bottom cylindrical surface of the connecting body in the axial direction over a groove bottom length which corresponds substantially to a length over which a cylindrical surface of the valve seat body extends in the axial direction, which radially inwardly projecting valve seat body bounded radially inward. As a result, the above advantages can be further improved.
    It is understood that the above measures and features within the feasibility of the invention are also combined with each other. Other aspects, advantages and features of the invention will become apparent from the claims and from the following description part, in which a preferred embodiment of the invention is described with reference to the drawings.
    1 shows an inventive safety valve in a partially broken Dar position, with illustration of a partial longitudinal section, wherein the locking piston of the safety valve is in its basic and open position. FIG. 2 shows the safety valve according to FIG. 1 in a plan view from above; FIG. Fig. 3 is a schematic representation of a hydraulic circuit diagram of the safety valve, which is fluidly connected via a hydraulic hose with a hydraulic cylinder-piston unit.
    In the safety check valve 20 shown in the figures is a flow-controlled, one-way, seat check valve for shutting off a supply passage 22 with respect to a discharge channel 25. It may preferably be configured or used as a hose break safety check valve. The supply passage 22 may, as shown schematically in FIG. 3, be connected to a hydraulic pump 21. As also shown in FIG. 3, the discharge channel 25 may be connected to at least one hydraulic consumer 24. The consumer 24 may, according to a preferred application of the safety valve 20, be a hydraulic compensating cylinder 24 of a heavy transport vehicle not shown in the figures. It can be provided a plurality of hydraulic cylinders, which in each case with the interposition of a high-pressure hose each an inventive safety valve 20 can be connected upstream. The supply ducts of this plurality of safety valves can be connected via supply lines to a common connection, so that a group of hydraulic cylinders can be supplied together by the pump 21 with a hydraulic medium as a fluid pressure medium, preferably with oil.
    The safety valve 20 comprises, as essential valve parts, a multipart valve housing 28, a blocking piston 41, a stop pin 36, also referred to as a stopper body, and a safety stopcock 46.
    The valve housing 28 consists of a cuboid valve housing part 29 and two housing parts 31 and 32, which are mounted in the region of the ends of the valve housing part 29. The housing parts 31 and 32 are each designed as screw connections. For this purpose, each housing part 31, 32 of these housing parts 31, 32 has an external thread, by means of which the respective housing part 31, 32 is screwed into a corresponding internal thread of the valve housing part 29. For sealing the housing parts 31, 32 in relation to the valve housing part 29, an annular seal 68 or 58, in each case in the form of an O-ring, is provided in each case. Each housing part 29, 31, 32 of the valve housing 28 has a coaxially arranged, circular cylindrical axial bore 27. Their bore longitudinal axes are aligned with each other to form an axial axis 33rd
    The housing part 31 shown on the left in Figures 1 and 2 on the left is designed with a thrust bearing in the form of an axial bore 27 for guided storage of the locking bolt 41. The locking pin 41 is mounted displaceably in the axial bore 27 of the housing part 31 in the axial direction 34 and is installed there coaxially to the axial axis or longitudinal axis 33.
    The housing part 32 shown on the right in each of FIGS. 1 and 2 is designed as a connecting flange for connecting a supply line 23 (FIG. 3). For this purpose, it has a connection external thread on its connection end facing outward in the axial direction 34. At the same time, the housing part 32 serves for the sealed clamping of a shut-off device 54 of a safety shut-off valve 46. This will be discussed in more detail below.
    The locking piston 41 is substantially rotationally symmetrical to its longitudinal axis or designed to the axial axis 33 and is designed as a hollow body. It has an axially extending 34 circular cylindrical bore 47, which is designed as a blind hole and which is open in the direction of the housing part 31. The bore 47 forms a receiving and pressure chamber 51 for receiving the fluid medium and for receiving a portion of the compression spring 61st
    The compression spring 61 is preferably a helical compression spring. It is understood, however, that other compression springs or similar springs can be installed. The compression spring 61 is supported with its one spring end 63 on a front inner wall 52 of a spring support body 80 of the locking piston 41. The compression spring 61 protrudes beyond the end 49 of the locking piston 41 pointing away from the valve plug 43 and, in the clamped state, is supported by its other spring end 64 on an end inner wall 88 of the housing part 31.
    The locking piston 41 is guided over a bore 47 radially outwardly bounding piston wall 50 of a tubular locking piston part on and in the axial bore 27 of the housing part 31 and there 34 slidably mounted in the axial direction. For this purpose, the blocking piston 41 is dimensioned such that it is supported via the circular-cylindrical outer surface 82 of its piston wall 50 over a minimum guide length 85 on the circular-cylindrical inner surface 84 of the axial bore 27 of the housing part 31. This minimum guide length 85 is greater in the illustrated embodiment than the outer diameter 83 of the piston wall 50. This results in a particularly accurate guidance of the locking piston 41 is achieved.
    At its end 48 facing away from the housing part 31, the blocking piston 41 has a valve cone 43 with a conical surface 45. This conical surface 45 extends obliquely from outside to inside, ie in the direction of the axial axis 33, and in the direction of the housing part 31 or in the closing direction 71 and closes with the axial axis 33 an acute angle 92.1. The angle 92.1 is preferably about 45 degrees. The conical surface 45 merges in the direction of the end of the blocking piston 41 pointing away from the housing part 31 or, in the direction of the housing part 32, into a circular-cylindrical outer surface of an abutting body 72 of the blocking piston 41. The abutment body 72 is bounded at its abutting end with a substantially planar abutment surface 72.1. The abutment body 72 has an outer diameter 97 which is slightly larger than the inner diameter of an axial bore 27.1 of a radially inwardly extending valve seat body 30 of the valve housing part 29. The valve seat body 30 is bounded radially inwardly by a cylindrical surface 62 which in one the axial axis 33 viewed cross-section, parallel to the axial axis 33 extends (Fig. 1). The cylindrical surface 62 of the valve seat body limits the valve seat 35, which is designed with an annular edge, radially inwards. In the axial direction 34 of the valve seat body 30 is bounded by two spaced apart at a distance 62.1 circular ring end faces facing away from each other in the opposite direction.
    The conical surface 45 of the valve plug 43 forms a first groove side 87.1 of a radially outwardly open annular groove 81 of the locking piston 41. The annular groove 81 is viewed in a cross section containing the axial axis 33, V- or U-shaped design (Figures 1 and 2). The ring groove 81 is on its first groove side 87.1 of the conical surface 45 of the valve cone 43, of a subsequent thereto in the direction of the housing part 31 and in the closing direction 71 groove bottom cylindrical surface 90 of the connecting body 91, and, on a second groove side 87.2, delimited by a to the groove bottom cylindrical surface 30 in the direction of the housing part 31 and in the closing direction 71 subsequent conical surface 37 of the spring support body 80 of the locking piston 41. The conical surface 37 of the spring support body 80 extends obliquely from outside to inside and in the direction of the housing part 32 and closes with the axial axis 33 at an acute angle 92.2. This angle 92.2 is preferably the same size as the angle 92.1 and is accordingly preferably also about 45 degrees. The groove bottom cylindrical surface 90 of the connecting body 91 extends in the axial direction 34 parallel to the cylindrical surface 62 of the valve seat body 30 over a groove bottom length 90.1, which corresponds substantially to the length 62.1, over which the cylindrical surface 62 of the valve seat body 30 extends in the axial direction 34. In the illustrated basic and open position 65 of the locking piston 41 is in the range of 8/19 Austrian Patent Office AT13195U1 2013-08-15
    Ring groove 81 formed due to the there approximately symmetrical to a perpendicular to the axial axis 33 formed, imaginary center plane formed components namely the valve seat body 30 and this in the basic and open position 65 opposite locking piston part of the locking piston 41 an approximately equal flow cross-section.
    Preferably, the entire locking piston 41 is manufactured or formed in one piece. As a result, the locking piston 41 can be made particularly simple and inexpensive and also be handled easily.
    In the open position 65 shown in Figures 1 and 2, the locking piston 41 is located with the abutment surface 72.1 of its abutment body 72, acted upon by the spring force of the spring 61, extending at a perpendicular to the axial axis 33 in the axial bore 27, as Stop pin trained stop body 36 at. The stop pin 36 is fixed in the valve housing part 29 of the valve housing 28 such that it is for the purpose of disassembly or assembly of the locking piston 41 of a mounting shown in Figures 1 and 2 - And stroke limiting position 42, in which it limits the opening stroke of the locking piston 41, in a not shown in the figures on or extended position can be converted, in which the locking piston 41 off or can be installed. The stop pin 36 is received or stored in the region of its ends 59.1, 59.2 pointing away from each other in a respective transverse bore 60.1, 60.2 of the valve housing part 29 of the valve housing 28 with a small clearance. The transverse bores 60.1 and 60.2 are circular-cylindrical and extend in the transverse direction 74 along a transverse axis 79 coaxial with this transverse axis 79. The transverse axis 79 is formed perpendicular to the axial axis 33 and intersects it. The transverse axis 79 and the axial axis 33 are thus arranged in a common imaginary plane. A transverse bore 60.1 of the two coaxial transverse bores 60.1, 60.2 is designed as a through-bore 60.1, while the other transverse bore 60.2 is designed as a blind bore 60.2. The through hole 60.1 is open on the one hand to the axial bore 27, ie opens radially inward into the axial bore 27, and on the other hand to a housing side 66.1 of the valve housing part 29 of the valve housing 28 open. In this manner, the stop bolt 36 received or mounted with play in the transverse bores 60.1 and 60.2 can be disassembled particularly easily relative to said housing side 66.1 or the stop bolt 36, or in a repair case a new, corresponding stop bolt, in the course of assembly of the valve 20, after a previously made introduction and proper positioning of the spring 61 and the locking pin 41 in the or the axial bore 27, are mounted from said housing side 66.1 ago. The stop pin 36 is thus releasably connected to the valve housing 28 such that it is completely removable. In its installed state, ie in the Hubbegrenzungsstellung 42 shown in Figures 1 and 2, the stop pin 36 is arranged and fixed so that it in the illustrated open position 65 of the locking piston 41 and then when the hydraulic medium from the supply passage 22 in the Ableitungskanal 25, or vice versa, flows, at least partially, namely in the present case to those in the axial bore 27 into projecting stud portions 36.1, 36.2 of the axial bore 36, the hydraulic medium is completely flowed around in the axial direction 34 in the transverse direction on both sides of the abutting body 72 of the Locking piston 41 extend. The stop pin 36 is secured in its Hubbegrenzungsstellung 42 using a designated also as a stop-securing means-locking screw 67, against falling out of the transverse bores 60.1,60.2. The closure screw 67 also serves to tightly close the transverse or through-bore 60.1.
    With respect to a direction of inflow of the hydraulic medium from the supply channel 22 in the discharge channel 25 in front of the stopper bolt 36 and between the stopper pin 36 and the supply port 70 for connecting the supply line 23, also referred to as a safety stopcock ball valve 46 is to shut off the Zuleitungskanals 22 opposite the discharge channel 25 and to shut off the supply passage 22 against inflow of the hydraulic medium to the locking piston 41 is arranged. The ball valve 46 has a shut-off ball 54 functioning as a shut-off ball, which is rotatably mounted about a rotation axis 53 in the valve housing part 29 of the valve housing 28. The Absperrkugel 54 passes through the axial bore 27 in the transverse direction 74. The Absperrkugel 54 can optionally from the open position shown in Figure 1 55, in which an inflow of the hydraulic medium via the supply passage 22 to the locking piston 41 and a flow of the hydraulic medium of the Supply passage 22 in the discharge channel 25, and vice versa, is allowed to be transferred to a safety shut-off position, not shown in the figures, in which an inflow of the hydraulic medium via the supply passage 22 is prevented to the locking piston 41 and in which a flow of the hydraulic medium from the supply passage 22 into the discharge channel 25, and vice versa, is prevented.
    The axis of rotation 53 is also perpendicular to the transverse axis 79 of the stop pin 36 and 79 of the stop pin 36 receiving or supporting transverse bores 60.1, 60.2 arranged. The axis of rotation 53 and the axial axis 33 are thus arranged in a common imaginary plane which is perpendicular to the transverse axis 79.
    The shut-off ball 54 of the safety ball valve 46 is sealed by means of at least one ring seal 98. The ring seal 98 is supported on one side on its outer circumference in the axial direction 34 on a ring end face of the housing part 32 shown on the right in FIG. 1 and is supported on an end face of a contact pressure ring 95 on its side facing away from this side in an opposite direction from. The contact pressure ring 95 is supported with an end face pointing away from this end face in the direction of the housing part 31 on a radially inwardly extending annular shoulder 94 of the valve housing part 29 of the valve housing 28. Between the contact pressure ring 95 and the ring seal 98 of the ball valve 46, a ring seal 96 is provided for sealing against the valve housing part 29, which is arranged in a radially outwardly open annular groove. The Absperrkugel 54 of the ball valve 46 is by means of a, preferably with a polygon, here a square, provided actuator 40 from the open position shown 55 in a closing or shut-off position, not shown, can be transferred. For this purpose, the actuator 40, preferably manually, by means of a tool, not shown, for example by means of a fork wrench, about the axis of rotation 53 are rotated. For exact adjustment of the open position 55 and the closed position of the shut-off ball 54 of the safety ball valve 46, the actuator 40 is provided with a switching disc 100. This is non-rotatably connected to an actuating pin 106 of the actuator and is secured by means of a snap ring 105 axially with respect to the axis of rotation 53 on the actuating bolt 106. The indexing disk 100 has two stop lugs 102.1 and 102.2 which are offset by a circumferential angle 104 of 90 degrees from one another and which can be brought into abutment against a stop pin 101 by rotating the actuating member 40 about the axis of rotation 53 with associated abutment surfaces 103.1, 103. In the illustrated open position 55, the stop surface 103. 1 of the stop lug 102. 1 bears against the stop pin 101. Starting from this position, the actuator 40 in the illustration of Figure 2 about the axis of rotation 53 in the clockwise direction, as long, namely in the present case by an angle 104 of 90 degrees, are rotated until the other stop surface 103.2 of the other stop lug 102.1 on the stop pin 101st strikes. Then the shut-off ball 54 of the safety ball valve 46 is in its safety closing or shut-off position, so that the supply channel is shut off from the discharge channel 25.
    The safety valve 20 according to the invention is a damped closing valve. It is equipped with a damping device 73 for the damped or time-delayed closing of the locking piston 41. The damping device 73 is formed with a throttle bore 73 designed as a through-bore. This passes through the piston wall 50 of the locking piston 41 in the radial direction. The throttle bore 73 extends radially outwardly from the receiving or pressure chamber 51 and is accordingly in fluid communication with a pressure chamber 69, which in turn is in fluid communication with the discharge channel 25 or into which the discharge channel 25 opens (FIG. 2). Upon a displacement of the locking piston 41 from its open position 65 in the closing direction 71 into its blocking division, the hydraulic medium in the receiving or pressure chamber 51 is forcibly retracted through the throttle bore 77 into the pressure chamber 69 pressed outside. This results in a correspondingly time-delayed damped closing of the blocking piston 41.
    The safety valve 20 according to the invention is a flow-dependent closing check valve. In other words, closes the safety valve 20 as a result of exceeding a certain limit or switching flow velocity of the hydraulic medium and thereby resulting pressure difference, which also with limit or. Switching pressure difference can be called. Until reaching the limit or switching flow rate, which is essentially dependent on the choice of the compression spring 61, in particular of their spring characteristic, the locking piston 41 is due to the application of the oppositely directed spring forces of the spring 61 in the in the figures 1 and 2 shown basic open position 65 held. In this position 65, therefore, the hydraulic medium can flow from the supply channel 22 into the discharge channel 25, and vice versa. The safety valve 20 may for example be designed such that the limit or. Switching pressure difference is 4 bar.
    Now occurs the rare case of a hose breakage of the high pressure hose 93, so breaks between the cylinder 24 and the upstream safety valve 20 of the system or. Oil pressure abruptly together. In such a case arises from P to S an increased flow velocity and thereby increasing flow resistance between P and S causes an increasing pressure difference from P to S. This conditionally, the valve plug 43 in the closing direction 71, ie in Figures 1 and 2 of moved right to left, against the spring force of the spring 61 until the valve plug 43 abuts with its conical surface 45 on the valve seat 35, after which the valve 20 is closed or shut off. This stops the loss of hydraulic fluid in fractions of a second. Only the cylinder 24 affected by the hose breakage can lose its remaining hydraulic medium and can optionally run empty or depressurized until the damage is noticed or stopped. If necessary, further axle compensation cylinders are provided, the axle units equipped therewith can then take over the load portion of the failed axle compensation cylinder 24. In other words, in the case of hose breakage of the hose 93, the flow rate in the safety valve 20 exceeds the limit flow rate of the hydraulic medium, and accordingly, the resulting pressure difference exceeds a threshold pressure. As a result, the locking piston 41 begins to move against the spring force of the compression spring 61 in a direction 71, where the pressure due to the flow velocity and the resulting pressure difference is lower by the switching or limiting pressure difference, for example by 4 bar. The locking piston 41 then moves further in the closing direction 71 against the spring force of the compression spring 61 until the conical surface 45 of the valve cone 43 of the locking piston 41 abuts the valve seat 35 of the valve seat body 30. Then the locking piston 41 is in its locking division, not shown in the figures. In the course of this closing operation, as already explained above, located in the receiving or pressure chamber 51 hydraulic medium or oil must be displaced, namely radially outwardly through the throttle bore 73 into the pressure chamber 69, whereby it is a damped, So delayed closing of the valve 20 comes. The closing speed of the valve 20 is dependent on the selected bore diameter of the throttle bore 73 and is constant over the entire closing path 86 of the locking piston. It is understood that 20 different locking piston can be used or available for one and the same safety check valve, for example in the form of a set of different locking piston. These can differ from each other due to different bore diameter of their respective throttle bore. By selecting a particular locking piston with a certain bore diameter of its throttle bore, the closing speed can be set to a desired value. 11/19 Austrian Patent Office AT 13 195 Ul 2013-08-15
    REFERENCE LIST 20 Safety 57 (Outer) O-ring / O-ring Shut-off valve / Safety valve 58 Gasket / O-ring 21 Pump 59.1 End of 36 22 Inlet duct 59.2 End of 36 23 Inlet 60.1 Cross bore / throughbore 24 Consumers / (compensating) cylinders 60.2 Transverse bore / blind bore 25 Drainage channel 61 (compression) spring 26 Drainage 62 Cylindrical surface of 30 27 Axial bore 62.1 Length 27.1 Axial bore 63 Spring end 28 Valve housing 64 Spring end 29 Valve housing part 65 Basic / open position 30 Valve seat body 66.1 (first) Housing side of 28 31 (first ) Housing part / screw connection 66.2 (second) housing side of 28 32 (second) housing part / 66.3 (third) housing side of 28 Screw connection 66.4 (fourth) Housing side of 28 33 Axial axis / longitudinal axis of 27 67 Body locking device stop / 34 Axial direction Screw plug 35 Valve seat 68 Seal / O-ring 36 Stop body / stop pin 69 Pressure chamber 36.1 Part of 36 70 Supply connection 36.2 Part of 36 71 Closing direction 37 Cone surface of 80 72 Impact body 38 Vent channel 72.1 Abutment surface 39 Bleed screw 73 Damping device / 40 Actuator of 54 DrosseL / continuity 41 Blocking piston opening / bore 42 Stroke limit position 74 Transverse direction 43 Valve plug 75 Through hole 44 Inflow direction 75.1 (first) Through hole part 45 Conical surface of 43 75.2 (second) through-bore part 46 Safety stopcock / 76.1 (first) connection ball valve 76.2 (second) connection 47 opening / bore / blind hole 77.1 (first) line 48 end of 41 77.2 (second) line 49 end of 41 78 closing means / 50 Piston wall Plug screw 51 Housing space / pressure chamber 79 Transverse axis / axis of 52 (front) inner wall of 41 36; 60.1,60.2 53 Rotary axis 80 Spring support body 54 Barrier / blocking cone 81 Ring groove 55 Opening position of 46, 54 82 Outer surface of 50 56 Level 83 Outer diameter of 50 12/19 AT 13 195 UI 2013-08-15 Austrian
    Patent Office 84 Inner surface of 27 97 Outer diameter of 72 85 (minimum) guide length 98 Ring seal 86 (total / maximum) 99 Seal / O-ring Locking path of 41 100 Shift disc 87.1 (first) Groove side 101 Stroke (bolt) 87.2 (second) Slot side 102.1 Stop lug 88 (front) inner wall of 31 102.2 stop lug 90 groove bottom cylinder surface 103.1 stop surface of 102.1 90.1 groove base length 103.2 stop surface of 102.2 91 connecting body 104 angle 92.1 angle 105 snap ring 92.2 angle 106 actuating pin 93 (high pressure) / (hydraulic) ) Hose E Venting option 94 Ring-shoulder P Pump connection 95 Pressure ring S First hose connection 96 Seal / O-ring S 'Second hose connection 13/19
    权利要求:
    Claims (16)
    [1]
    Austrian Patent Office AT13195U1 2013-08-15 Claims 1. Hydraulic pipe, line or hose break safety shut-off valve (20) for shutting off a feed duct (22) connectable to a pump (21) to one having a hydraulic consumer (24), for example one Hydraulic cylinder (24), in particular a hydraulic balancing cylinder (24), for a truck, preferably for a heavy transport vehicle, in particular via a high pressure hose (93), connectable discharge channel (25), wherein the supply channel (22) and the discharge channel (25) in an axial bore (27) of a valve housing (28) extending in the direction of an axial axis (33), in which a locking piston (41) is displaceably mounted in the axial direction (34), which is displaced by the spring force of a spring (61) in the axial direction (34 ), whereby the blocking piston (41) up to a certain, a value greater than zero amounting border flow velocity a hydraulic medium is maintained in an open position (65) in which the hydraulic medium from the supply passage (22) in the discharge channel (25) can flow, and vice versa, and wherein the locking piston (41) due to exceeding the limit flow rate the hydraulic medium and a resulting pressure difference against the spring force of the spring (61) from its open position (65) is transferred or transferred into a blocking division, in which the supply channel (22) opposite the discharge channel (25) is shut off the blocking piston (41) has a valve cone (43) with a conical surface (45) in the blocking pitch of the blocking piston (41) on a valve seat (35) of a radially inwardly into one of the conical surface (45) of the valve cone (43) limited space (37) projecting into valve seat body (30), preferably of the valve housing (28), sealingly abuts, characterized in that a transverse to d he axial axis (33) in the axial bore (27) extending stop body (36) for limiting an opening stroke of the locking piston (41) is provided, on which the locking piston (41) in its open position (65) acted upon by the spring force of the spring (61) is applied, and wherein the stopper body (36) is attached to and / or in the valve housing (28) such that it for the purpose of disassembly and assembly of the locking piston (41) from a Hubbegrenzungsstellung (42), in which he the opening stroke of the locking piston (41) limited, can be converted into an installed or disassembled position, in which the locking piston (41) can be removed and / or that, in the inflow direction (44) of the hydraulic medium of the supply channel (22) in considered the discharge channel (25), in front of the locking piston (41) arranged safety shut-off valve (46) for shutting off the supply duct (22) against inflow of the hydraulic medium to the locking piston (41) and to shut off the Zuleitu ngskanals (22) opposite the discharge channel (25) is provided, which in the valve housing (28) rotatably mounted, about a rotation axis (53) rotatable, the axial bore (27) passing through the obturator (54) which selectively from an open position ( 55), in which an inflow of the hydraulic medium via the supply channel (22) to the blocking piston (41) is made possible, into a safety shut-off position can be transferred, in which an inflow of the hydraulic medium via the supply channel (22) to the locking piston ( 41) is prevented, and wherein the axis of rotation (53) of the obturator (54) in the region of one or in the axial axis (33) of the axial bore (27) containing plane (56) is arranged.
    [2]
    2. Safety stop valve according to claim 1, characterized in that the stop body (36) in the Hubbegrenzungsstellung (42) either in the region of one end of its ends facing away from each other in a transverse bore of the valve housing and stored or in the region of its ends facing away from each other ( 59.1, 59.2) in each case a transverse bore (60.1, 60.2) of the valve housing (28) is received and stored.
    [3]
    3. Safety shut-off valve according to claim 2, characterized in that the transverse bore (60.1) or each transverse bore (60.1, 60.2) is designed as a through-bore, the one-side to a housing side (66.1) the valve housing (28) is open and the other side in the axial bore (27) opens, so that with preferably a small clearance in the through hole (60.1), possibly also in the other transverse bore (60.2), received and mounted stop body (36) can be mounted from said housing side (66.1) and dismantled from said housing side (66.1).
    [4]
    4. Safety check valve according to one of claims 1 to 3, characterized in that the stop body (36) with the valve housing (28) is releasably connected such that it is completely removable.
    [5]
    5. Safety check valve according to one of claims 1 to 4, characterized in that the stop body (36) in its Hubbegrenzungsstellung (42) is arranged and secured such that in the axial bore (27) projecting into the part (36.1,36.2) of the stopper body (36) in the open position (65) of the locking piston (41) of the hydraulic medium, preferably completely, in the axial direction (34) is flowed around and / or flows around.
    [6]
    6. Safety check valve according to one of claims 1 to 5, characterized in that the stop body (36) is designed as a, preferably cylindrical, in particular circular cylindrical, stop pin or stop pin.
    [7]
    7. Safety stop valve according to one of claims 1 to 6, characterized in that the stop body (36) in its Hubbegrenzungsstellung (42) by means of a releasable stopper body securing means (67), preferably by means of a locking screw (67), against a Falling out of the transverse bore (60.1) or from the transverse bores (60.1,60.2) is secured.
    [8]
    8. Safety shut-off valve according to one of claims 1 to 7, characterized in that the obturator (54), viewed in the inflow direction (44) of the hydraulic medium through the supply channel (22), is arranged in front of the stop body (36) and / or between the Stop body (36) and a supply terminal (70) for connection of a supply line (23) is arranged.
    [9]
    9. Safety check valve according to one of claims 1 to 8, characterized in that the discharge channel (25) with a valve housing (28) in a transverse direction (74), preferably perpendicular to the axial axis (33) passing through through hole (75) is designed which is open towards housing sides facing away from one another (66.1, 66.2) of the valve housing (28) and which is provided with a first through-bore part (75.1) on a first housing side (66.1) of said housing sides (66.1, 66.2) with a first connection (76.1 ) for connecting a first line (77.1) and having a second through-bore part (75.2) on a second housing side (66.2) of said housing sides (66.1, 66.2) with a second connection (76.2) for connecting a second line (77.2) is provided, and wherein a closure means (78), preferably a closure screw (78) is provided, by means of which or by means of which either the first terminal (76. 1) or the second port (76.2) is closed against leakage of the hydraulic medium.
    [10]
    10. Safety check valve according to claim 9, characterized in that the through-bore (75) and the through-bore parts (75.1, 75.2) extend in the direction of a transverse axis (79) which is transversely, preferably perpendicular, to the axis of rotation (53) of the obturator (54 ) of the safety shut-off valve (46) is arranged and that the obturator (54) is operable from a housing side (66.3) which is transverse in a direction, preferably perpendicular, to the transverse axis (79) of the transverse axis (79) points away.
    [11]
    11. Safety stop valve according to one of claims 1 to 10, characterized in that the locking piston (41) in an axial direction (34) extending opening (47), in particular a blind hole (47), which or to one of his Valve cone (43) end facing away (49) is open and which is bounded radially outwardly by a cylindrical piston wall (50), which, in a cross section perpendicular to the axial axis of AT 13 195 Ul 2013- 08-15 (33), is annular and has a receiving space (51) for receiving a spring part in the open position (65) of the locking piston (41) protruding therefrom, designed as a compression spring spring (61) extending itself with a spring end (63) directly or indirectly on an inner wall (52) of a spring support body (80) of the locking piston (41) is supported and with another spring end (64) directly or indirectly on the valve housing (28) is supported.
    [12]
    12. Safety check valve according to claim 11, characterized in that the piston wall (50) has a cylindrical outer surface (82) and an outer diameter (83) and on its cylindrical outer surface (82) on a cylindrical inner surface (84) of the axial bore (27). , preferably a housing part (21), via a guide length (85) is supported, which, preferably always, as well as in the open position (65) of the locking piston (41) is at least half as large as the outer diameter (83) of the piston wall (50 ), preferably at least equal to or greater than the outer diameter (83) of the piston wall (50).
    [13]
    13. Safety check valve according to one of claims 1 to 12, characterized in that it is provided with a damping device (73) for damped and / or time-delayed closing of the locking piston (41), which during a movement of the locking piston (41) from its open position ( 65) in its blocking division via a, by the open position (65) on the one hand and the blocking division on the other specific, entire closing path (86) of the locking piston (41) causes a damped and / or delayed closure of the locking piston (41).
    [14]
    14. Safety check valve according to claim 13, characterized in that it is at the damping means (73) at least one, preferably a single, in a piston wall (50) of the locking piston (41) or in the piston wall (50) of the locking piston (41 ) provided, radially from the inside outwardly extending through hole (73), via which the in the receiving space (51) located hydraulic medium, when the locking piston (41) is transferred from its open position (65) in its locking division, throttled in the discharge channel (25) flows.
    [15]
    15. Safety stop valve according to one of claims 1 to 14, characterized in that the locking pin (41) has a ring groove (81) which, in a cross-section containing the axial axis (33), V- or U- or is designed trapezoidal and on its the valve seat (36) associated first groove side (87.1) of a conical surface (45) of the valve cone (43), and of a subsequent groove bottom cylindrical surface (90) of a connecting body (91), and on a second groove side (87.2) is delimited by a conical surface (37) of a spring support body of the blocking piston (41) or of the spring support body (80) of the blocking piston (41) adjoining the groove base cylinder surface (90) for supporting the spring (61), wherein the conical surface (45) of the valve cone (44) and the conical surface (37) of the spring support body (80) with the axial axis (33) each have a, preferably approximately equal, acute angle (92.1, 92.2), preferably each about 4 5 degrees, and wherein the poppet (43), the connecting body (91) and the spring support body (80), preferably the entire locking piston (41) are made in one piece or is.
    [16]
    16. Safety check valve according to claim 15, characterized in that the groove-base cylindrical surface (90) of the connecting body (91) in the axial direction (34) over a groove-basic length (90.1) extending substantially a length (62.1 ), over which extends a cylindrical surface (62) of the valve seat body (30) in the axial direction (34) which defines the radially inwardly projecting valve seat body (30) radially inwardly. 3 sheets of drawings 16/19
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    同族专利:
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    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
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    US4131235A|1976-11-01|1978-12-26|Irrigation Specialties Company|Dual-function valve|
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    DE102009043568A1|2009-09-30|2011-04-07|Neumeister Hydraulik Gmbh|Hydraulic pipe, pipeline or hose rupture safety valve for lorry, has locking pistons kept in positions when medium flows with given flow rate, where medium flows from supply channel into drainage channel and vice versa in positions|
    CH544901A|1972-11-09|1973-11-30|Beringer Hydraulik Gmbh|Hydraulic pipe rupture valve with damped closing|DE202011109211U1|2011-07-26|2012-01-27|Horst Thiele Maschinenbau-Hydraulische Geräte GmbH|Pipe break valve device|
    DE102019131355A1|2019-11-20|2021-05-20|Buchholz Hydraulik Gmbh|Hydraulic valve|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    DE201120050667|DE202011050667U1|2011-07-08|2011-07-08|Safety shut-off valve|
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