EP2007989B1 - Hydraulic device - Google Patents
Hydraulic device Download PDFInfo
- Publication number
- EP2007989B1 EP2007989B1 EP07722248.7A EP07722248A EP2007989B1 EP 2007989 B1 EP2007989 B1 EP 2007989B1 EP 07722248 A EP07722248 A EP 07722248A EP 2007989 B1 EP2007989 B1 EP 2007989B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- hydraulic chamber
- hydraulic
- piston
- flange
- switch
- 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.)
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/021—Valves for interconnecting the fluid chambers of an actuator
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
- F15B15/1423—Component parts; Constructional details
- F15B15/1447—Pistons; Piston to piston rod assemblies
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
- F15B15/149—Fluid interconnections, e.g. fluid connectors, passages
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/18—Combined units comprising both motor and pump
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/20—Other details, e.g. assembly with regulating devices
- F15B15/204—Control means for piston speed or actuating force without external control, e.g. control valve inside the piston
Definitions
- the present invention relates to a hydraulic device with a jacket tube, a longitudinally displaceably sealingly mounted in the jacket piston rod with a piston flange, sealingly between the jacket tube and the piston rod existing hydraulic chambers and a hydraulic control device with at least one valve unit, a pump unit and a tank unit, wherein by means of the hydraulic control device Pressure variation within the corresponding hydraulic chamber, the respective desired position of the piston rod is adjustable, wherein on one side of the piston flange through the inner wall of the jacket tube and the outer wall of the piston rod with piston flange, a first hydraulic chamber is formed, on the other side of the piston flange a switch box stationary sealing at the Piston rod is mounted with piston flange, the space formed by the inner wall of the casing tube and the outer wall of the piston rod with piston flange in a second and third hydraulic chamber divided, wherein the second hydraulic chamber via a first valve unit can be acted upon with pressure, the piston flange has at least one continuous KolbenflanschausEnglishung, the socket has at
- Such hydraulic devices are used, for example, within a superordinate control loop in order to regulate the actual or desired state of a superordinated component.
- An application of such a hydraulic device is, for example, for a steam valve of a turbine in power plant construction.
- By the movement of the piston rod of the hydraulic device is controlled by the steam valve, the amount of steam supplied to a turbine.
- an exact control and a permanently reliable function must be guaranteed.
- the steam valve of a turbine In the event of a disaster, that is, for example, if the power fails due to lightning strike, the steam valve of a turbine must be closed suddenly, as it causes enormous irreparable damage to the Turbine can lead, if the steam valve is open in this case too long. Therefore, such hydraulic devices must be able to respond to sudden changes between the setpoint and actual value.
- a hydraulic drive device for an injection molding machine which has a pilot-operated check valve, which is activated from the outside and integrated in a piston.
- the DE 1 263 432 B is a pressure-medium-actuated valve with a pressurized drive means for slow and steady actuation and for the production of intermediate positions described, which is characterized in that the first pressure medium drive, a second pressure medium drive is superimposed, which causes a quick closure or a quick opening.
- the second pressure medium drive from a piston operable by pressure medium, which makes the first pressure medium drive ineffective by responding to a malfunction signal the first pressure medium drive and controls the rapid closing of the valve and after solving the fault, the first pressure medium drive can be effective again.
- a steam control valve with combined safety shut-off function for controlled steam supply with simultaneous protection against impermissible overpressure is described.
- an axially floating assembly consisting of a Absperrkegel, a spindle and a double piston is used, the stepped portion is sealed on the double piston of a fixedly connected to the actuator, cup-shaped coupling socket, said double piston and coupling socket on the hollow drilled drive spindle relieved chamber lock in.
- the present invention the object or the technical problem of specifying a hydraulic device of the type mentioned, which is structurally simple, has a compact design, ensures a reliable long-term function and a timely response to abruptly occurring Differences between setpoint and actual value possible.
- the hydraulic device according to the invention is characterized by the features of independent Ansprüchs 1.
- Advantageous embodiments and further developments are the subject of the independent claims 1 or indirectly dependent claims.
- the hydraulic device according to the invention is characterized demgzeß by the fact that on one side of the piston flange through the inner wall of the jacket tube and the outer wall of the piston rod with piston flange, a first hydraulic chamber is formed on the other side of the piston flange a switch box is mounted stationary sealingly on the piston rod with piston flange , which divides the space formed by the inner wall of the jacket tube and the outer wall of the piston rod with piston flange in a second and third hydraulic chamber, wherein the second hydraulic chamber via a first valve unit can be acted upon with pressure, the piston flange has at least one continuous KolbenflanschausEnglishung, the socket at least one through SiemensdosenausEnglishung has, within the switch box, that is arranged in the second hydraulic chamber, a sealing longitudinally displaceable switching plate, the switching plate has a continuous Drosselaus brieflyung, whereby a communication connection between the first and second hydraulic chamber, the switching plate in the normal operating condition, the Kolbenflanschaus Principleung and the Heidelbergdosen
- a particularly advantageous embodiment in the second alternative is characterized in that the first valve unit is designed as a servo valve unit.
- a structurally particularly simply designed, a permanently reliable function ensuring variant of both alternatives is characterized by the fact that the switch has a mechanical end stop for the indexing plate in the open position.
- a particularly advantageous embodiment, which aims at a significant reduction of the flow resistance in the open indexing plate is characterized in that the KolbenflanschausEnglishruc grid-shaped along a circular contour are present in the piston flange, wherein the KolbenflanschausEnglishung may preferably be formed as bores.
- the Heidelberg are grid-shaped along a circular contour in the wall of the socket, wherein the Heidelbergtelleraus traditions are preferably formed by a present at the peripheral edge of the box crown structure.
- a structurally particularly simple design that easily ensures a permanently reliable closure of Kolbenflanschausappelsch and Heidelbergdosenausnaturalungen is characterized in that the switching plate is formed so that the second hydraulic chamber facing the pressure surface is greater than the pressure chamber facing the first hydraulic chamber. As a result, the same pressure is ensured even in the second alternative, in the normal operating state in the first and second hydraulic chamber, which reliably closes the switch plate.
- the strength properties of the hydraulic device according to the invention are increased according to a preferred embodiment in that the piston flange is integrally connected to the piston rod.
- a constructionally particularly simple to implement embodiment is characterized in that in the wall of the jacket tube, an annular space is present, which is in communication with the second hydraulic chamber via the bore extending within the piston rod and which can be acted upon by the second valve unit or the first valve unit with pressure ,
- the shift plate arranged longitudinally displaceably about the piston rod initially acts as a valve slide in the normal operating state, but is able to connect both sides of the piston flange or the first and third hydraulic chambers with one another.
- a pressure P1 prevails in the first hydraulic chamber due to the external acting force.
- the second hydraulic chamber is acted upon by a pressure P2, which is chosen so large that in the normal operating state of the switching plate, the KolbenflanschausEnglishung and sealing the Wegnausnaturalung sealing.
- the first valve unit controls the first hydraulic chamber and determines the positioning of the piston rod relative to the jacket tube.
- the second valve opens against the tank and the second hydraulic chamber is depressurized.
- the indexing plate opens the KolbenflanschausEnglishung and the WegnausANSung, as in the first hydraulic chamber due to the external force is still pending.
- the piston flange then acts like a sieve and the piston rod with piston flange abruptly moves against an external hard stop, solely due to the effect of the external force.
- the second hydraulic chamber is pressurized via the first valve unit. Due to the throttle recess, the same pressure also occurs in the first hydraulic chamber. The respective positioning of the piston rod is accomplished via the first valve unit with variation of the pressure in the second hydraulic chamber.
- the pressure surfaces of the switching plate relative to the first and second hydraulic chamber are chosen so that always in the normal operating condition resulting in the direction of the first hydraulic chamber pressure force is applied to the switch plate so that it sealingly closes the KolbenflanschausEnglishung and the Wegnausnaturalung.
- the pressure in the second hydraulic chamber drops very sharply or is set equal to zero.
- the indexing plate opens the piston flange recess and the Wenndosenaus supraung, whereby the above-mentioned screening function occurs, that is, the piston no longer works as a hydraulic cylinder and the oil in the first hydraulic chamber in a simple manner is pressed into the third hydraulic chamber.
- the piston either travels to the hard stop in the event of a failure or to a position in which the target pressure of the second hydraulic chamber becomes greater.
- the hydraulic device according to the invention has the great advantage that a transport of the hydraulic fluid around the outer jacket tube around, as in the prior art, can be completely eliminated. As a result, a compact design is made possible by the hydraulic device according to the invention.
- the hydraulic fluid itself does not experience any great acceleration, but is merely "pushed through a sieve". In addition, in the quick-closing state, a higher speed and thus shorter reaction time is possible.
- Fig. 1 and 2 is shown in a schematic longitudinal section, the upper half of a known hydraulic device 10.1.
- the hydraulic device 10.1 has a piston rod 12 with a piston flange 14, which is mounted longitudinally displaceably in a jacket tube 16.
- the piston rod 12 has a connection unit 72, can be connected to the means not shown, which transmits the movement (B) of the piston rod to a component, here a schematically illustrated steam valve 50 of a turbine system.
- the steam valve 50 is operated via a control device 56 shown schematically.
- the piston rod 12 can be up to a in Fig. 1 schematically shown end stop 52 are moved out. Furthermore, the piston rod 12 is permanently under the action of an external force 54, which can be constructively generated for example by a spring element.
- the inner wall of the jacket tube 16 In the area in front of the piston flange 14, that is in Fig. 1 To the left of the piston flange 14, the inner wall of the jacket tube 16, the wall of the piston rod 12 and the wall of the piston flange 14 forms a first hydraulic chamber 20.
- the piston flange 14 is longitudinally displaceable relative to the inner wall of the jacket tube 16 via a second sealing unit 62.
- a switch box 40 On the opposite side of the first hydraulic chamber 20 of the piston flange 14 is a switch box 40 stationary sealingly on the piston rod 12 is present, which divides the first hydraulic chamber 20 opposite region into a second hydraulic chamber 22 and a third hydraulic chamber 24.
- the second hydraulic chamber 22 is in this case to the piston rod 12 and the third hydraulic chamber 24 is disposed towards the jacket tube.
- the switch box 40 is sealed off from the piston rod 12 via a third sealing unit 64.
- a longitudinally displaceable switching plate 42 is present, which is sealed by fourth sealing units 66 relative to the piston rod 12, the inner wall of the switch box 40 and the wall of the piston flange 14.
- the switch box 40 has in its piston flange 14 facing Stirnend Scheme circumferentially arranged WegnausEnglishungen 36 which by the switching plate 42.1 in the in Fig. 1 shown position are sealingly closed.
- the piston flange 14 has through KolbenflanschausEnglishlessness 26, which also from the indexing plate 42.1 in the in Fig.1 be sealed position shown.
- Fig. 1 extends the KolbenflanschausEnglishung 26 parallel to the longitudinal axis of the piston rod 12. It is also conceivable to arrange the recess 26 inclined to the longitudinal axis (dashed line).
- the first hydraulic chamber 20 facing the pressure surface of the switching plate 42.1 is in Fig. 1 denoted by A1.
- the second hydraulic chamber 22 facing the pressure surface is in Fig.1 denoted by A2.
- the jacket tube 16 has a wall recess, which together with the wall of the piston rod 12 forms an annular space 38, which is sealed on both sides of the annular space 38 arranged first sealing units 60.
- the annular space 38 communicates with the second hydraulic chamber 22 via bores 46 extending in the piston rod 12.
- a further first sealing unit 60 is present, which seals the jacket tube 16 relative to the piston rod 12 longitudinally displaceable sealing.
- a hydraulic control device 34 which receives signals from the higher-level control device 56.
- the hydraulic control device 34 acts on a first valve unit 32.1, which is designed as a servo valve, and a second valve unit 30, which is designed as a switching valve.
- the second valve unit 30 acts on the annular space 38 with a pressure P2, which then also prevails in the second hydraulic chamber 22.
- the first valve unit 32.1 pressurizes the first hydraulic chamber 20 with a pressure P1 which can be varied as a function of the respective nominal values and by means of which the movement B of the piston rod 12 within the jacket tube 16 can be controlled.
- the second hydraulic chamber 22 facing the pressure surface A2 of the switching plate 42.1 and the first hydraulic chamber 20 facing the pressure surface A1 of the switching plate 42.1 are selected in the exemplary embodiment so that the pressure surface A2 is greater than the pressure surface A1. This geometry is not mandatory in the illustrated embodiment.
- the third hydraulic chamber 24 is connected, for example, open against a tank.
- a second embodiment of a hydraulic device 10.2 is shown, which has the same basic structure as the hydraulic device 10.1 according to the Fig.1 and 2 , The same components bear the same reference numerals and will not be described again.
- the main differences to the hydraulic device 10.1 according to the Fig. 1 and 2 consists in that the switching plate 42.2 has at least one Drosselaus originallyung 70 which establishes a communication connection between the first hydraulic chamber 20 and the second hydraulic chamber 22, and only a first valve unit 32.2 is provided, which is designed as a servo valve and the annular space 38 with pressure P1 acted upon.
- the external force 54 can be generated for example via a spring element.
- the spring element engage externally or internally on the piston rod.
- Fig. 5 It can be seen that the KolbenflanschausEnglishurigen 26 are continuously present in a circular predetermined grid around the piston rod 12 in the piston flange 14. At the same time it can be seen that the Wegnaus traditions 36 are formed on the socket 40 to the front open, that is, the socket 40 has a crown-like structure in the front end.
- Fig. 6 is an external perspective view of the hydraulic device 10.1 according to the invention shown, it can be seen that the device 10.1 can be made very compact.
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Description
Die vorliegende Erfindung betrifft eine Hydraulikvorrichtung mit einem Mantelrohr, einer in dem Mantelrohr längsverschieblich dichtend gelagerten Kolbenstange mit einem Kolbenflansch, zwischen dem Mantelrohr und der Kolbenstange dichtend vorhandenen Hydraulikkammern und einer Hydraulikregeleinrichtung mit zumindest einer Ventileinheit, einer Pumpeinheit und einer Tankeinheit, wobei mittels der Hydraulikregeleinrichtung durch Druckvariation innerhalb der entsprechenden Hydraulikkammer die jeweils gewünschte Position der Kolbenstange einstellbar ist, wobei auf einer Seite des Kolbenflansches durch die Innenwandung des Mantelrohrs und die Außenwandung der Kolbenstange mit Kolbenflansch eine erste Hydraulikkammer gebildet wird, auf der anderen Seite des Kolbenflansches eine Schaltdose ortsfest dichtend an der Kolbenstange mit Kolbenflansch gelagert ist, die den durch die Innenwandung des Mantelrohrs und der Außenwandung der Kolbenstange mit Kolbenflansch gebildeten Raum in eine zweite und dritte Hydraulikkammer unterteilt, wobei die zweite Hydraulikkammer über eine erste Ventileinheit mit Druck beaufschlagbar ist, der Kolbenflansch zumindest eine durchgehende Kolbenflanschausnehmung aufweist, die Schaltdose zumindest eine durchgehende Schaltdosenausnehmung aufweist, innerhalb der Schaltdose, das heißt in der zweiten Hydraulikkammer, ein dichtend längsverschieblicher Schaltteller angeordnet ist.The present invention relates to a hydraulic device with a jacket tube, a longitudinally displaceably sealingly mounted in the jacket piston rod with a piston flange, sealingly between the jacket tube and the piston rod existing hydraulic chambers and a hydraulic control device with at least one valve unit, a pump unit and a tank unit, wherein by means of the hydraulic control device Pressure variation within the corresponding hydraulic chamber, the respective desired position of the piston rod is adjustable, wherein on one side of the piston flange through the inner wall of the jacket tube and the outer wall of the piston rod with piston flange, a first hydraulic chamber is formed, on the other side of the piston flange a switch box stationary sealing at the Piston rod is mounted with piston flange, the space formed by the inner wall of the casing tube and the outer wall of the piston rod with piston flange in a second and third hydraulic chamber divided, wherein the second hydraulic chamber via a first valve unit can be acted upon with pressure, the piston flange has at least one continuous Kolbenflanschausnehmung, the socket has at least one continuous Schaltdosenausnehmung within the switch box, that is arranged in the second hydraulic chamber, a sealingly longitudinally displaceable switching plate is.
Derartige Hydraulikvorrichtungen werden beispielsweise innerhalb eines übergeordneten Regelkreises eingesetzt, um den Ist- beziehungsweise Sollzustand eines übergeordneten Bauteils zu regeln. Ein Einsatzfall einer derartigen Hydraulikvorrichtung ist beispielsweise für ein Dampfventil einer Turbine im Kraftwerksbau. Durch die Bewegung der Kolbenstange der Hydraulikvorrichtung wird über das Dampfventil die einer Turbine zugeführten Dampfmenge geregelt. Dabei muss einerseits eine exakte Regelung und eine dauerhaft zuverlässige Funktion gewährleistet sein. Im Katastrophenfall, das heißt wenn beispielsweise infolge Blitzeinschlag der Strom ausfällt, muss das Dampfventil einer Turbine schlagartig geschlossen werden, da es zu enormen irreparablen Schäden an der Turbine führen kann, wenn das Dampfventil in diesem Fall noch zu lange geöffnet ist. Daher müssen derartige Hydraulikvorrichtungen geeignet sein auf schlagartige Änderungen zwischen Soll- und Istwert zu reagieren.Such hydraulic devices are used, for example, within a superordinate control loop in order to regulate the actual or desired state of a superordinated component. An application of such a hydraulic device is, for example, for a steam valve of a turbine in power plant construction. By the movement of the piston rod of the hydraulic device is controlled by the steam valve, the amount of steam supplied to a turbine. On the one hand, an exact control and a permanently reliable function must be guaranteed. In the event of a disaster, that is, for example, if the power fails due to lightning strike, the steam valve of a turbine must be closed suddenly, as it causes enormous irreparable damage to the Turbine can lead, if the steam valve is open in this case too long. Therefore, such hydraulic devices must be able to respond to sudden changes between the setpoint and actual value.
Es ist eine Hydraulikvorrichtung der eingangs genannten Art bekannt, bei der im Schnellschlussfall die in der Hydraulikkammer befindliche, unter Druck stehende Hydraulikflüssigkeit über ein relativ aufwendiges Kanalsystem nach außen geführt wird. Dabei sind erhebliche Strömungswiderstände zu überwinden. Darüber hinaus baut eine derartige Hydraulikvorrichtung relativ großvolumig.It is a hydraulic device of the aforementioned type is known in which in the case of rapid closure, located in the hydraulic chamber, pressurized hydraulic fluid is passed through a relatively complex channel system to the outside. In this case, considerable flow resistance must be overcome. In addition, such a hydraulic device is relatively bulky.
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Ausgehend von dem genannten Stand der Technik liegt der vorliegenden Erfindung die Aufgabe beziehungsweise das technische Problem zugrunde, eine Hydraulikvorrichtung der eingangs genannten Art anzugeben, die konstruktiv einfach aufgebaut ist, einen kompakten Aufbau aufweist, eine dauerhaft zuverlässige Funktion gewährleistet und eine zeitnahe Reaktion bei schlagartig auftretenden Differenzen zwischen Soll- und Istwert ermöglicht.Based on the cited prior art, the present invention, the object or the technical problem of specifying a hydraulic device of the type mentioned, which is structurally simple, has a compact design, ensures a reliable long-term function and a timely response to abruptly occurring Differences between setpoint and actual value possible.
Die erfindungsgemäße Hydraulikvorrichtung ist durch die Merkmale des unabhängigen Ansprüchs 1. Vorteilhafte Ausgestaltungen und Weiterbildungen sind Gegenstand der von dem unabhängigen Ansprüch 1 direkt oder indirekt abhängigen Ansprüche.The hydraulic device according to the invention is characterized by the features of independent Ansprüchs 1. Advantageous embodiments and further developments are the subject of the independent claims 1 or indirectly dependent claims.
Die erfindungsgemäße Hydraulikvorrichtung zeichnet sich demgmäß dadurch aus, dass auf einer Seite des Kolbenflansches durch die Innenwandung des Mantelrohrs und die Außenwandung der Kolbenstange mit Kolbenflansch eine erste Hydraulikkammer gebildet wird, auf der anderen Seite des Kolbenflansches eine Schaltdose ortsfest dichtend an der Kolbenstange mit Kolbenflansch gelagert ist, die den durch die Innenwandung des Mantelrohrs und der Außenwandung der Kolbenstange mit Kolbenflansch gebildeten Raum in eine zweite und dritte Hydraulikkammer unterteilt, wobei die zweite Hydraulikkammer über eine erste Ventileinheit mit Druck beaufschlagbar ist, der Kolbenflansch zumindest eine durchgehende Kolbenflanschausnehmung aufweist, die Schaltdose zumindest eine durchgehende Schaltdosenausnehmung aufweist, innerhalb der Schaltdose, das heißt in der zweiten Hydraulikkammer, ein dichtend längsverschieblicher Schaltteller angeordnet ist, der Schaltteller eine durchgehende Drosselausnehmung aufweist, wodurch eine Kommunikationsverbindung zwischen der ersten und zweiten Hydraulikkammer besteht, der Schaltteller in normalem Betriebszustand die Kolbenflanschausnehmung und die Schaltdosenausnehmung dichtend verschließt, da er von seiner Dichtgeometrie so ausgebildet ist, dass die auf ihn wirkende Druckkraft aufgrund des in der zweiten Kammer über die erste Ventileinheit eingestellten Drucks größer ist als die auf ihn in entgegengesetzter Richtung wirkende Druckkraft aufgrund des Drucks in der ersten Kammer , und der Schaltteller im Schnellschlusszustand oder ab überschreiten einer vorgegebenen Druckdifferenz zwischen erster und zweiter Hydraulikkammer die Kolbenflanschausnehmung und die Schaltdosenausnehmung freigibt, da in diesem Zustand der über die zweite Ventileinheit eingestellte Druck in der zweiten Hydraulikkammer auf Null gesetzt wird oder sehr stark vermindert ist, wodurch eine Kommunikationsverbindung zwischen der ersten Hydraulikkammer und der dritten Hydraulikkammer entsteht, so dass die Hydraulikflüssigkeit aufgrund des in der ersten Hydraulikkammer herrschenden Druckes von der ersten Hydraulikkammer in die dritte Hydraulikkammer strömt, bis die Kolbenstange einen Endanschlag erreicht oder die vorgegebene Druckdifferenz wieder unterschritten wird und daraufhin der Schaltteller die Kolbenflanschausnehmung und die Schaltdosenausnehmung wieder verschließt.The hydraulic device according to the invention is characterized demgmäß by the fact that on one side of the piston flange through the inner wall of the jacket tube and the outer wall of the piston rod with piston flange, a first hydraulic chamber is formed on the other side of the piston flange a switch box is mounted stationary sealingly on the piston rod with piston flange , which divides the space formed by the inner wall of the jacket tube and the outer wall of the piston rod with piston flange in a second and third hydraulic chamber, wherein the second hydraulic chamber via a first valve unit can be acted upon with pressure, the piston flange has at least one continuous Kolbenflanschausnehmung, the socket at least one through Schaltdosenausnehmung has, within the switch box, that is arranged in the second hydraulic chamber, a sealing longitudinally displaceable switching plate, the switching plate has a continuous Drosselausnehmung, whereby a communication connection between the first and second hydraulic chamber, the switching plate in the normal operating condition, the Kolbenflanschausnehmung and the Schaltdosenausnehmung sealing closes because it is formed by its sealing geometry so that the compressive force acting on it due to the pressure set in the second chamber via the first valve unit is greater than the force acting on it in the opposite direction pressure force due to the pressure in the first chamber, and Switch plate in the quick-closing state or from exceeding a predetermined pressure difference between the first and second hydraulic chamber, the Kolbenflanschausnehmung and the Schaltdosenausnehmung releases, as in this state of the two Valve unit set pressure in the second hydraulic chamber is set to zero or is greatly reduced, whereby a communication connection between the first hydraulic chamber and the third hydraulic chamber is formed, so that the hydraulic fluid due to the prevailing pressure in the first hydraulic chamber from the first hydraulic chamber to the third Hydraulic chamber flows until the piston rod reaches an end stop or falls below the predetermined pressure difference again and then the switch plate closes the Kolbenflanschausnehmung and the Schaltdosenausnehmung again.
Eine besonders vorteilhafte Ausgestaltung bei der zweiten Alternative zeichnet sich dadurch aus, dass die erste Ventileinheit als Servoventileinheit ausgebildet ist.A particularly advantageous embodiment in the second alternative is characterized in that the first valve unit is designed as a servo valve unit.
Eine konstruktiv besonders einfach gestaltete, eine dauerhaft zuverlässige Funktion gewährleistende Ausführungsvariante beider Alternativen zeichnet sich dadurch aus, dass die Schaltdose einen mechanischen Endanschlag für den Schaltteller in geöffneter Position aufweist.A structurally particularly simply designed, a permanently reliable function ensuring variant of both alternatives is characterized by the fact that the switch has a mechanical end stop for the indexing plate in the open position.
Eine besonders vorteilhafte Ausgestaltung, die auf eine deutliche Reduzierung des Strömungswiderstandes bei geöffnetem Schaltteller abzielt zeichnet sich dadurch aus, dass die Kolbenflanschausnehmungen rasterförmig entlang einer Kreiskontur in dem Kolbenflansch vorhanden sind, wobei die Kolbenflanschausnehmung bevorzugt als Bohrungen ausgebildet sein können.A particularly advantageous embodiment, which aims at a significant reduction of the flow resistance in the open indexing plate is characterized in that the Kolbenflanschausnehmungen grid-shaped along a circular contour are present in the piston flange, wherein the Kolbenflanschausnehmung may preferably be formed as bores.
In dieselbe Richtung geht eine vorteilhafte Ausgestaltung, die sich dadurch auszeichnet, dass die Schaltdosenausnehmungen rasterförmig entlang einer Kreiskontur in der Wandung der Schaltdose vorhanden sind, wobei die Schalttellerausnehmungen bevorzugt durch eine am Umfangsrand der Schaltdose vorhandene Kronenstruktur gebildet werden.In the same direction is an advantageous embodiment, which is characterized in that the Schaltdosenausnehmungen are grid-shaped along a circular contour in the wall of the socket, wherein the Schalttellerausnehmungen are preferably formed by a present at the peripheral edge of the box crown structure.
Eine konstruktiv besonders einfache Ausgestaltung, die eine dauerhaft zuverlässige Verschließung der Kolbenflanschausnehmungen und der Schaltdosenausnehmungen problemlos gewährleistet, zeichnet sich dadurch aus, dass der Schaltteller so ausgebildet ist, dass die der zweiten Hydraulikkammer zugewandte Druckfläche größer ist als die der ersten Hydraulikkammer zugewandten Druckfläche. Dadurch ist auch bei der zweiten Alternative, bei der im normalen Betriebszustand in der ersten und zweiten Hydraulikkammer derselbe Druck gewährleistet, das der Schaltteller zuverlässig schließt.A structurally particularly simple design that easily ensures a permanently reliable closure of Kolbenflanschausnehmungen and Schaltdosenausnehmungen is characterized in that the switching plate is formed so that the second hydraulic chamber facing the pressure surface is greater than the pressure chamber facing the first hydraulic chamber. As a result, the same pressure is ensured even in the second alternative, in the normal operating state in the first and second hydraulic chamber, which reliably closes the switch plate.
Die Festigkeitseigenschaften der erfindungsgemäßen Hydraulikvorrichtung werden gemäß einer bevorzugten Ausgestaltung dadurch erhöht, dass der Kolbenflansch einstückig mit der Kolbenstange verbunden ist.The strength properties of the hydraulic device according to the invention are increased according to a preferred embodiment in that the piston flange is integrally connected to the piston rod.
Eine konstruktiv besonders einfach umzusetzende Ausführungsvariante zeichnet sich dadurch aus, dass in der Wandung des Mantelrohrs ein Ringraum vorhanden ist, der über innerhalb der Kolbenstange verlaufende Bohrungen mit der zweiten Hydraulikkammer in Kommunikationsverbindung steht und der über die zweite Ventileinheit beziehungsweise die erste Ventileinheit mit Druck beaufschlagbar ist.A constructionally particularly simple to implement embodiment is characterized in that in the wall of the jacket tube, an annular space is present, which is in communication with the second hydraulic chamber via the bore extending within the piston rod and which can be acted upon by the second valve unit or the first valve unit with pressure ,
Der um die Kolbenstange längsverschieblich angeordnete Schaltteller wirkt zunächst im normalen Betriebszustand als Ventilschieber, der jedoch in Lage ist, beide Seiten des Kolbenflansches beziehungsweise die erste und die dritte Hydraulikkammer miteinander zu verbinden.The shift plate arranged longitudinally displaceably about the piston rod initially acts as a valve slide in the normal operating state, but is able to connect both sides of the piston flange or the first and third hydraulic chambers with one another.
Bei der ersten Ausführungsvariante herrscht in der ersten Hydraulikkammer aufgrund der äußeren einwirkenden Kraft ein Druck P1. Über das zweite Ventil wird die zweite Hydraulikkammer mit einem Druck P2 beaufschlagt, der so groß gewählt ist, dass im normalen Betriebszustand der Schaltteller die Kolbenflanschausnehmung und die Schaltdosenausnehmung dichtend verschließt. Die erste Ventileinheit steuert die erste Hydraulikkammer an und bestimmt die Positionierung der Kolbenstange relativ zum Mantelrohr.In the first embodiment variant, a pressure P1 prevails in the first hydraulic chamber due to the external acting force. Via the second valve, the second hydraulic chamber is acted upon by a pressure P2, which is chosen so large that in the normal operating state of the switching plate, the Kolbenflanschausnehmung and sealing the Schaltdosenausnehmung sealing. The first valve unit controls the first hydraulic chamber and determines the positioning of the piston rod relative to the jacket tube.
Sobald eine Schnellschlusssituation auftritt öffnet das zweite Ventil gegen den Tank und die zweite Hydraulikkammer wird drucklos. Dadurch öffnet der Schaltteller die Kolbenflanschausnehmung und die Schaltdosenausnehmung, da in der ersten Hydraulikkammer aufgrund der äußeren Kraft immer noch Druck ansteht. In diesem Zustand besteht eine Kommunikationsverbindung zwischen der ersten und der dritten Hydraulikkammer. Der Kolbenflansch wirkt dann wie ein Sieb und die Kolbenstange mit Kolbenflansch fährt schlagartig gegen einen äußeren Festanschlag, allein aufgrund der Wirkung der äußeren Kraft.As soon as a quick-closing situation occurs, the second valve opens against the tank and the second hydraulic chamber is depressurized. As a result, the indexing plate opens the Kolbenflanschausnehmung and the Schaltdosenausnehmung, as in the first hydraulic chamber due to the external force is still pending. In this state, there is a communication connection between the first and third hydraulic chambers. The piston flange then acts like a sieve and the piston rod with piston flange abruptly moves against an external hard stop, solely due to the effect of the external force.
Bei der zweiten Ausführungsvariante, bei dem der Schaltteller eine durchgehende Drosselausnehmung aufweist, die einen definierten Strömungswiderstand besitzt, wird über die erste Ventileinheit die zweite Hydraulikkammer mit Druck beaufschlagt. Aufgrund der Drosselausnehmung stellt sich auch in der ersten Hydraulikkammer derselbe Druck ein. Die jeweilige Positionierung der Kolbenstange wird über die erste Ventileinheit unter Variation des Drucks in der zweiten Hydraulikkammer bewerkstelligt. Die Druckflächen des Schalttellers gegenüber der ersten beziehungsweise zweiten Hydraulikkammer sind dabei so gewählt, dass stets im normalen Betriebszustand eine in Richtung der ersten Hydraulikkammer resultierende Druckkraft an dem Schaltteller ansteht, so dass er die Kolbenflanschausnehmung und die Schaltdosenausnehmung dichtend verschließt. Tritt nun die Situation ein, dass der Sollwert deutlich größer ist als der Istwert, mithin ein großer Schleppabstand vorliegt, oder es tritt die Situation ein, dass ein Schnellschluss vorliegt, fällt der Druck in der zweiten Hydraulikkammer sehr stark ab beziehungsweise wird gleich Null gesetzt. Dadurch kann, aufgrund des in der ersten Hydraulikkammer anstehenden Druckes der Schaltteller die Kolbenflanschausnehmung und die Schaltdosenausnehmung öffnen, wodurch die bereits oben angesprochene Siebfunktion eintritt, das heißt der Kolben nicht mehr als Hydraulikzylinder arbeitet und das in der ersten Hydraulikkammer befindliche Öl in einfacher Art und Weise in die dritte Hydraulikkammer gedrückt wird. Der Kolben fährt entweder bis zum Festanschlag bei einem Ausfall oder bis in eine Position, bei der der Solldruck der zweiten Hydraulikkammer größer wird.In the second embodiment, in which the indexing plate has a continuous throttle recess, which has a defined flow resistance, the second hydraulic chamber is pressurized via the first valve unit. Due to the throttle recess, the same pressure also occurs in the first hydraulic chamber. The respective positioning of the piston rod is accomplished via the first valve unit with variation of the pressure in the second hydraulic chamber. The pressure surfaces of the switching plate relative to the first and second hydraulic chamber are chosen so that always in the normal operating condition resulting in the direction of the first hydraulic chamber pressure force is applied to the switch plate so that it sealingly closes the Kolbenflanschausnehmung and the Schaltdosenausnehmung. Now enters the situation that the setpoint is significantly greater than the actual value, thus there is a large following error, or there is a situation that there is a quick closing, the pressure in the second hydraulic chamber drops very sharply or is set equal to zero. As a result, due to the pressure prevailing in the first hydraulic chamber, the indexing plate opens the piston flange recess and the Schaltdosenausnehmung, whereby the above-mentioned screening function occurs, that is, the piston no longer works as a hydraulic cylinder and the oil in the first hydraulic chamber in a simple manner is pressed into the third hydraulic chamber. The piston either travels to the hard stop in the event of a failure or to a position in which the target pressure of the second hydraulic chamber becomes greater.
Die erfindungsgemäße Hydraulikvorrichtung hat den großen Vorteil, dass ein Transport der Hydraulikflüssigkeit um das äußere Mantelrohrs herum, wie im Stand der Technik, vollständig entfallen kann. Dadurch wird durch die erfindungsgemäße Hydraulikvorrichtung eine kompakte Bauweise ermöglicht. Die Hydraulikflüssigkeit selbst erfährt keine große Beschleunigung, sondern wird lediglich "durch ein Sieb gedrückt". Außerdem ist im Schnellschlusszustand eine höhere Geschwindigkeit und somit kürzere Reaktionszeit möglich.The hydraulic device according to the invention has the great advantage that a transport of the hydraulic fluid around the outer jacket tube around, as in the prior art, can be completely eliminated. As a result, a compact design is made possible by the hydraulic device according to the invention. The hydraulic fluid itself does not experience any great acceleration, but is merely "pushed through a sieve". In addition, in the quick-closing state, a higher speed and thus shorter reaction time is possible.
Weitere Ausführungsformen und Vorteile der Erfindung ergeben sich durch die in den Ansprüchen ferner aufgeführten Merkmale sowie durch die nachstehend angegebenen Ausführungsbeispiele. Die Merkmale der Ansprüche können in beliebiger Weise miteinander kombiniert werden, insoweit sie sich nicht offensichtlich gegenseitig ausschließen.Further embodiments and advantages of the invention will become apparent from the features further listed in the claims as well as by the embodiments given below. The features of the claims may be combined in any manner as far as they are not obviously mutually exclusive.
Die Erfindung sowie vorteilhafte Ausführungsformen und Weiterbildungen derselben werden im Folgenden anhand der in der Zeichnung dargestellten Beispiele näher beschrieben und erläutert. Die der Beschreibung und der Zeichnung zu entnehmenden Merkmale können einzeln für sich oder zu mehreren in beliebiger Kombination erfindungsgemäß angewandt werden. Es zeigen:
- Fig. 1
- schematischer Längsschnitt durch eine obere Hälft einer im Wesentlichen rotationssymmetrisch ausgebildeten, bekannten Hydraulikvorrichtung mit einer Kolbenstange und einem Mantelrohr mit einer ersten, zweiten und dritten Hydraulikkammer, wobei ein längsverschieblicher Schieber vorhanden ist, mittels dessen eine Kommunikationsverbindung mit der ersten und dritten Hydraulikkammer herstellbar ist, im normalen Betriebszustand,
- Fig. 2
- schematischer Längsschnitt durch eine Hydraulikvorrichtung gemäß
Fig.1 , im Schnellschlusszustand, - Fig. 3
- schematischer Längsschnitt durch eine obere Hälfte einer im Wesentlichen rotationssymmetrisch ausgebildeten Hydraulikvorrichtung mit einer Kolbenstange und einem Mantelrohr mit einer ersten, zweiten und dritten Hydraulikkammer, wobei ein längsverschieblicher Schieber vorhanden ist, mit einer Drosselverbindung zwischen erster und zweiter Hydraulikkammer, mittels dessen eine Kommunikationsverbindung mit der ersten und dritten Hydraulikkammer herstellbar ist, im normalen Betriebszustand,
- Fig. 4
- schematischer Längsschnitt durch eine obere Hälfte einer im Wesentlichen rotationssymmetrisch ausgebildeten Hydraulikvorrichtung mit einer Kolbenstange und einem Mantelrohr mit einer ersten, zweiten und dritten Hydraulikkammer, wobei ein längsverschieblicher Schieber vorhanden ist, mit einer Drosselverbindung zwischen erster und zweiter Hydraulikkammer, mittels dessen eine Kommunikationsverbindung mit der ersten und dritten Hydraulikkammer herstellbar ist, im Schnellschlusszustand beziehungsweise Schleppzustand,
- Fig. 5
- schematische Detailexplosionsperspektive der Kolbenstange einer Schaltdose und eines längsverschieblichen Schalttellers der Hydraulikvorrichtung gemäß
Fig. 1 und - Fig. 6
- schematische Perspektivdarstellung einer Hydraulikvorrichtung gemäß
Fig. 1 von außen gesehen.
- Fig. 1
- a schematic longitudinal section through an upper half of a substantially rotationally symmetrical, known hydraulic device with a piston rod and a jacket tube having a first, second and third hydraulic chamber, wherein a longitudinally displaceable slider is present, by means of which a communication connection with the first and third hydraulic chamber can be produced in the normal operating condition,
- Fig. 2
- schematic longitudinal section through a hydraulic device according to
Fig.1 , in the fast-closing state, - Fig. 3
- schematic longitudinal section through an upper half of a substantially rotationally symmetrical hydraulic device with a piston rod and a jacket tube with a first, second and third hydraulic chamber, wherein a longitudinally movable slide is present, with a throttle connection between the first and second hydraulic chamber, by means of which a communication link with the first and third hydraulic chamber can be produced, in the normal operating state,
- Fig. 4
- schematic longitudinal section through an upper half of a substantially rotationally symmetrical hydraulic device with a piston rod and a jacket tube with a first, second and third hydraulic chamber, wherein a longitudinally movable slide is present, with a throttle connection between the first and second hydraulic chamber, by means of which a communication link with the first and third hydraulic chamber can be produced, in the quick-closing state or towing state,
- Fig. 5
- schematic detail exploded perspective of the piston rod of a socket and a longitudinally displaceable switching plate of the hydraulic device according to
Fig. 1 and - Fig. 6
- schematic perspective view of a hydraulic device according to
Fig. 1 seen from the outside.
In den
Die Kolbenstange 12 kann bis zu einem in
Im Bereich vor dem Kolbenflansch 14, das heißt in
Auf der der ersten Hydraulikkammer 20 gegenüberliegenden Seiten des Kolbenflansches 14 ist eine Schaltdose 40 ortsfest dichtend an der Kolbenstange 12 vorhanden, die den der ersten Hydraulikkammer 20 gegenüberliegenden Bereich in eine zweite Hydraulikkammer 22 und eine dritte Hydraulikkammer 24 unterteilt. Die zweite Hydraulikkammer 22 ist hierbei zur Kolbenstange 12 hin und die dritte Hydraulikkammer 24 ist zum Mantelrohr hin angeordnet. Die Schaltdose 40 ist über eine dritte Dichteinheit 64 gegenüber der Kolbenstange 12 abgedichtet.On the opposite side of the first
Innerhalb der Schaltdose 40, das heißt innerhalb der zweiten Hydraulikkammer 22 ist ein längsverschieblicher Schaltteller 42 vorhanden, der über vierte Dichteinheiten 66 gegenüber der Kolbenstange 12, der Innenwandung der Schaltdose 40 und der Wandung des Kolbenflansches 14 abgedichtet ist.Within the
Die Schaltdose 40 weist in ihrem dem Kolbenflansch 14 zugewandten Stirnendbereich umlaufend angeordnete Schaltdosenausnehmungen 36 auf, die durch den Schaltteller 42.1 in der in
Der Kolbenflansch 14 besitzt durchgehende Kolbenflanschausnehmungen 26, die ebenfalls von dem Schaltteller 42.1 in der in
Die der ersten Hydraulikkammer 20 zugewandte Druckfläche des Schalttellers 42.1 ist in
Im vorderen Endbereich weist das Mantelrohr 16 eine Wandausnehmung auf, die zusammen mit der Wandung der Kolbenstange 12 einen Ringraum 38 bildet, der über beidseitig des Ringraums 38 angeordnete erste Dichteinheiten 60 abgedichtet ist. Der Ringraum 38 steht über in der Kolbenstange 12 verlaufende Bohrungen 46 mit der zweiten Hydraulikkammer 22 in Kommunikationsverbindung.In the front end region, the
Im rechten Endbereich des Mantelrohrs 16 ist eine weitere erste Dichteinheit 60 vorhanden, die das Mantelrohr 16 gegenüber der Kolbenstange 12 längsverschieblich dichtend abdichtet.In the right end region of the
In
Die zweite Ventileinheit 30 beaufschlagt den Ringraum 38 mit einem Druck P2, der dann auch in der zweiten Hydraulikkammer 22 herrscht. Die ersten Ventileinheit 32.1 beaufschlagt die erste Hydraulikkammer 20 mit einem Druck P1, der in Abhängigkeit von den jeweiligen Sollwerten variiert werden kann und mittels dem die Bewegung B der Kolbenstange 12 innerhalb des Mantelrohrs 16 gesteuert werden kann. Die der zweiten Hydraulikkammer 22 zugewandte Druckfläche A2 des Schalttellers 42.1 und die der ersten Hydraulikkammer 20 zugewandte Druckfläche A1 des Schalttellers 42.1 sind im Ausführungsbeispiel so gewählt, dass die Druckfläche A2 größer ist als die Druckfläche A1. Diese Geometrie ist bei dem dargestellen Ausführungsbeispiel nicht zwingend. Zwingend ist, dass der in der zweiten Hydraulikkammer 22 über die zweite Ventileinheit 30 eingestellte Druck P2 so groß ist, dass eine Druckkraft über die Fläche A2 erzeugt wird, die in jedem Fall größer ist als auf die Druckfläche A1 wirkende Druckkraft infolge Drucks P1 in der ersten Hydraulikkammer 20.The
Dadurch wird gewährleistet, dass der Schaltteller 42.1 im normalen Betriebszustand immer die in
Die dritte Hydraulikkammer 24 ist beispielsweise gegen einen Tank offen geschaltet.The third
In dem Schnellschlussfall, das heißt in dem Fall, in dem die Kolbenstange 12 schlagartig bis zu dem Endanschlag 52 herausgefahren werden muss, öffnet die zweite Ventileinheit 30 gegen den Tank, was zur Folge hat, dass die zweite Hydraulikkammer 22 drucklos wird. Aufgrund der Einwirkung der äußeren Kraft 54 herrscht in der ersten Hydraulikkammer 20 immer ein Mindestdruck P1. Aufgrund dieses anstehenden Druckes, der über die Kolbenflanschausnehmung 26 auf den Schaltteller 42.1 einwirkt, öffnet der Schaltteller 42.1 die Kolbenflanschausnehmung 26 und verfährt bis zu einem innerhalb der Schaltdose 40 vorhandenen mechanischen Anschlag 44. In dieser Position des Schalttellers 42.1 sind auch die Schaltdosenausnehmungen 36 geöffnet, so dass eine Kommunikationsverbindung zwischen der ersten Hydraulikkammer 20 und der dritten Hydraulikkammer 24 entsteht. Dadurch kann die in der ersten Hydraulikkammer 20 befindliche Hydraulikflüssigkeit problemlos ohne große Strömungswiderstände in die dritte Hydraulikkammer 24 abfließen (Pfeil F in
In den
Die wesentlichen Unterschiede zu der Hydraulikvorrichtung 10.1 gemäß den
Im normalen Betriebszustand (
Da die der zweiten Hydraulikkammer 22 zugewandte Druckfläche A2 des Schalttellers 42.2 größer ist als die der ersten Hydraulikkammer 20 zugewandte Druckfläche A1 wird im normalen Zustand der Schaltteller 42.2 immer gegen den Kolbenflansch 14 gedrückt, wodurch die Kolbenflanschausnehmung 26 und die Schaltdosenausnehmung 36 dichtend geschlossen sind.Since the second
In einer Situation, in dem der Unterschied zwischen dem Soll- und dem Istwert eine vorgegebene Größe überschreitet (großer Schleppabstand), das heißt für den Fall, dass in der zweiten Hydraulikkammer 22 ein deutlich geringerer Druck herrscht, oder für den Fall, dass eine Schnellschlusssituation eintritt, das heißt der Druck in der zweiten Hydraulikkammer 22 auf Null abfällt, öffnet der Schaltteller 42 die Kolbenflanschausnehmung 26 und die Schaltdosenausnehmung 36, da auf ihn immer eine aufgrund der äußeren Kraft 54 vorhandene Druckkraft einwirkt. Dadurch kann die Hydraulikflüssigkeit ohne großen Strömungswiderstand von der ersten Hydraulikkammer 20 in die dritte Hydraulikkammer 24 fließen (Pfeil F in
Die äußere Kraft 54 kann beispielsweise über ein Federelement erzeugt werden. Dabei kann das Federelement außen oder innen an der Kolbenstange angreifen.The
In
In
Claims (10)
- Hydraulic device (10.2) with- a jacket tube (16),- a piston rod (12) sealingly mounted longitudinally displaceably in the jacket tube (16) and having a piston flange (14),- hydraulic chambers (20, 22, 24) present sealingly between the jacket tube (16) and the piston rod (12), and- a hydraulic regulating arrangement (34) with at least one valve unit (32.2), with a pump unit and with a tank unit, the respectively desired position of the piston rod (12) being capable of being set by means of the hydraulic regulating arrangement (34) by pressure variation within the corresponding hydraulic chamber (20, 22, 24),- a first hydraulic chamber (20) being formed on one side of the piston flange (14) by the inner wall of the jacket tube (16) and by the outer wall of the piston rod (12) having a piston flange (14),- a switch box (40) being sealingly mounted fixedly on the other side of the piston flange (14) on the piston rod (12) having a piston flange (14) and subdividing the space formed by the inner wall of the jacket tube (16) and by the outer wall of the piston rod (12) having a piston flange (14) into a second and a third hydraulic chamber (22, 24), the second hydraulic chamber (22) being loadable with pressure via a first valve unit (32.2),- the piston flange (14) having at least one continuous piston-flange recess (26),- the switch box (40) having at least one continuous switch-box recess (36),- a sealingly longitudinally displaceable switch plate (42.2) being arranged inside the switch box (40), that is to say in the second hydraulic chamber (22), characterized in that- the switch plate (42.2) has a continuous throttle recess (70), with the result that there is a communication connection between the first and the second hydraulic chamber (20, 22),- in the normal operating state the switch plate (42.2) sealingly closes the piston-flange recess (26) and the switch-box recess (36), since the said switch plate is designed in terms of its sealing geometry such that the pressure force acting upon it on account of the pressure set in the second hydraulic chamber (22) via the first valve unit (32.2) is higher than the pressure force acting upon it in the opposite direction on account of the pressure in the first hydraulic chamber (20), and- in the quick-action closing case, that is to say in the case where the piston rod (12) has to be moved abruptly as far as its limit stop (52), the switch plate (42.2) releases the piston-flange recess (26) and the switch-box recess (36) from the point when a stipulated pressure difference between the first and the second hydraulic chambers (20, 22) is exceeded, since, in this state, the pressure set via the first valve unit (32.2) in the second hydraulic chamber (22) is set to zero or is very greatly reduced, thus giving rise to a communication connection between the first hydraulic chamber (20) and the third hydraulic chamber (24), so that the hydraulic fluid flows from the first hydraulic chamber (20) into the third hydraulic chamber (24) on account of the pressure prevailing in the first hydraulic chamber (20), until the piston rod (12) reaches a limit stop (52) or the stipulated pressure difference is undershot again, and thereupon the switch plate (42.2) closes the piston-flange recess (26) and the switch-box recess (36) again.
- Hydraulic device according to Claim 1,- characterized in that- the first valve unit (32.2) is designed as a servovalve unit.
- Hydraulic device according to one or more of the preceding claims,- characterized in that- the switch box (40) has a mechanical limit stop (44) for the switch plate (42.1; 42.2) in the open position.
- Hydraulic device according to one or more of the preceding claims,- characterized in that- the piston-flange recesses (26) are present in the form of a grid along a circular contour in the piston flange (14).
- Hydraulic device according to Claim 4,- characterized in that- the piston-flange recesses (26) are designed as bores.
- Hydraulic device according to one or more of the preceding claims,- characterized in that- the switch-box recesses are present in the form of a grid along a circular contour in the wall of the switch box (40).
- Hydraulic device according to Claim 6,- characterized in that- the switch-box recesses (36) are formed by a crown structure present at the free circumferential margin of the switch box (40).
- Hydraulic device according to one or more of the preceding claims,- characterized in that- the switch plate (42.1; 42.2) is designed such that the pressure surface (A2) facing the second hydraulic chamber (22) is larger than the pressure surface (A1) facing the first hydraulic chamber (20).
- Hydraulic device according to one or more of the preceding claims,- characterized in that- the piston flange (14) is connected in one piece to the piston rod (12).
- Hydraulic device according to one or more of the preceding claims,- characterized in that- in the wall of the jacket tube (16), an annular space (38) is present, which is in communication connection with the second hydraulic chamber (22) via bores running within the piston rod (12) and which can be loaded with pressure via the second valve unit (30) or the first valve unit (32.2).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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DE200610018733 DE102006018733B3 (en) | 2006-04-20 | 2006-04-20 | hydraulic device |
PCT/DE2007/000690 WO2007121718A1 (en) | 2006-04-20 | 2007-04-19 | Hydraulic device |
Publications (2)
Publication Number | Publication Date |
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EP2007989A1 EP2007989A1 (en) | 2008-12-31 |
EP2007989B1 true EP2007989B1 (en) | 2013-06-12 |
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Application Number | Title | Priority Date | Filing Date |
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EP07722248.7A Not-in-force EP2007989B1 (en) | 2006-04-20 | 2007-04-19 | Hydraulic device |
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EP (1) | EP2007989B1 (en) |
DE (1) | DE102006018733B3 (en) |
WO (1) | WO2007121718A1 (en) |
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CN109642593B (en) * | 2016-08-05 | 2023-04-18 | 康斯博格汽车股份公司 | Position actuator with pneumatic venting |
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DE1263432B (en) * | 1963-07-03 | 1968-03-14 | Participations Eau Soc Et | Pressure medium operated valve especially for gas turbine systems |
CH496536A (en) | 1968-06-26 | 1970-09-30 | Hehl Karl | Hydraulic drive for plastics injection mould - ing machine |
DE2419314C3 (en) | 1974-04-22 | 1981-07-02 | Hehl, Karl, 7298 Loßburg | Hydraulic working cylinder for the mold clamping device of a plastic injection molding machine |
DD223783A1 (en) * | 1984-03-16 | 1985-06-19 | Magdeburger Armaturenwerke | CONTROL VALVE WITH SAFETY DISCONNECTION FUNCTION |
AT404640B (en) | 1994-02-18 | 1999-01-25 | Engel Gmbh Maschbau | METHOD FOR OPERATING THE CLOSING DEVICE OF A TWO-PLATE INJECTION MOLDING MACHINE |
-
2006
- 2006-04-20 DE DE200610018733 patent/DE102006018733B3/en not_active Expired - Fee Related
-
2007
- 2007-04-19 EP EP07722248.7A patent/EP2007989B1/en not_active Not-in-force
- 2007-04-19 WO PCT/DE2007/000690 patent/WO2007121718A1/en active Application Filing
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EP2007989A1 (en) | 2008-12-31 |
WO2007121718A1 (en) | 2007-11-01 |
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