EP1528267B1 - Locking device - Google Patents
Locking device Download PDFInfo
- Publication number
- EP1528267B1 EP1528267B1 EP04023895A EP04023895A EP1528267B1 EP 1528267 B1 EP1528267 B1 EP 1528267B1 EP 04023895 A EP04023895 A EP 04023895A EP 04023895 A EP04023895 A EP 04023895A EP 1528267 B1 EP1528267 B1 EP 1528267B1
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- EP
- European Patent Office
- Prior art keywords
- outer ring
- springs
- rod
- clamping
- load
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
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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
- F15B15/26—Locking mechanisms
- F15B15/262—Locking mechanisms using friction, e.g. brake pads
Definitions
- the invention relates to a device for jamming a rod under load by means of at least one acting on the rod circumference clamping element, wherein the clamping element is conically shaped at its outer periphery and slidably guided in a corresponding conically shaped outer ring, such that the clamping element when driving through the rod is pressed in the load direction self-reinforcing against the rod, wherein the outer ring is guided axially displaceably in a housing and biased by springs.
- clamping devices are used for example for fixing lifting tables, support cylinders, theater podiums and the like. Often they also act as fall protection for vertical axes of machine tools or handling equipment.
- the clamping devices are hydraulically or pneumatically held in the open position and effective at pressure drop.
- the energy of the sinking load is used to generate the clamping force.
- a clamping device having the feature of the preamble of claim 1 has become known from EP-A 538 962. It is the jamming of a push rod in a motor vehicle steering, wherein a mechanical, dependent on the steering wheel position displacement movement is superimposed with a hydraulic displacement movement.
- a similar clamping device is known from DE 38 11 225.
- the clamping elements are taken in the case of release of the rod in the load direction, wherein the conical outer contour of the clamping elements generates a self-reinforcing static friction on the rod.
- the clamping elements run - as far as the rated load is not significantly exceeded - not against a housing-fixed stop. Overloading can therefore lead to the destruction of the clamping device by plastic deformation. This feature limits the scope of use to those cases where overloads are excluded. Therefore, these clamping devices are not particularly suitable for dissipating the kinetic energy of a falling mass, they block the clamping bars, but are not suitable for braking.
- the present invention has the object to develop a clamping device which allows an exact limitation of the holding force, wherein in the overload case targeted slippage of the rod occurs without damaging the clamping device, in particular without plastic deformation of the relevant parts.
- the clamping device according to the invention should be characterized by low-cost and low tolerance-sensitive structure.
- clamping element is loaded by spring elements in the clamping direction, and that the bias of acting on the outer ring springs against the load direction is directed and dimensioned so that the displacement of the outer ring only when a predetermined, defined load enters the pole.
- this is a conical bush, which has one or more axial slots in its effective area. But it is also not excluded to work with several circumferentially juxtaposed clamping elements.
- the outer ring surrounding the clamping elements is expediently designed as a closed ring, but could also consist of several parts, but care must be taken to intercept the radial forces occurring.
- the clamping element runs only after exceeding the predetermined defined load axially against its stop, it is recommended that the bias of the outer ring engaging springs to select slightly higher than it would be required for holding the predetermined defined load (nominal load).
- the spring travel of the responsible for the bias of the outer ring springs is chosen so that the axial displacement of the outer ring does not push the springs in their blocking position, but said springs should a defined force on the outer ring and thus a defined holding or braking force generate the rod when the axial displacement of the clamping element is completed.
- the clamping element can run directly against the abovementioned stop. In terms of a compact design, it is recommended to interpose the responsible for the release of the clamping element release piston.
- the outer ring surrounding the clamping elements not only in the unloaded state, but also under load axially spaced from the release piston or to the stop is arranged, whereas the clamping element is always held in contact with the release piston. The latter takes place in that it is loaded in the usual way by spring elements in the clamping direction.
- the housing 1 is fixedly mounted in a manner not shown, while the rod 2 is the displaceable machine element to be held by the clamping device.
- the rod 2 is surrounded by clamping elements, which in the embodiment have the shape of a conical sleeve 3 on its outer periphery.
- This conical bush has axial slots in a known manner, so that it is elastic in the radial direction. It is in the inner cone of an outer ring 4, which will be discussed in more detail later and is loaded in the axial direction by a cup spring package 5 in the clamping direction.
- the clamping bush 3 At its end facing away from the spring assembly 5, the clamping bush 3 abuts against a release piston 6, which in turn is axially displaceably guided in the housing part 1 b.
- the release piston 6 At its end facing away from the clamping bush 3, the release piston 6 forms a cylinder space 7 with the housing part 1 b.
- This cylinder space 7 can be acted upon by a housing bore with pressure medium - compressed air or hydraulic oil. so that he can move the clamping sleeve 3 from its clamping position to the left.
- the stroke of the release piston 6 is limited in the release position by a stop ring 8.
- This stop ring is suitably seated in a recess at the transition between the two housing halves 1 a and 1 b and is thus fixed axially.
- outer ring 4 is axially slidably guided in the housing part 1a and that it is biased by springs 9 - preferably a disc spring package - against the load direction, ie in the sense of jamming of the clamping bush 3.
- the disc springs 9 are arranged in an annular recess of the outer ring 4 and are based on their outer ring facing away from the end face on the abovementioned stop ring 8.
- the bias of the disc springs 9 is selected so that they yield only when a load occurs in the rod 2, which is above the rated load of the clamping device. This results in the following function:
- the rod 2 should be able to pass the clamping device in both directions.
- the cylinder chamber 7 is acted upon with pressure medium, so that the release piston 6 moves the clamping cone 3 against the spring elements acting on it 5 to the left in the release position and holds there. This condition is shown in FIG.
- the clamping state is triggered by the fact that the pressure in the cylinder chamber 7 is turned off. This allows the springs 5 to move the cone ring to the right, this displacement movement is supported by the movement of the rod 2 and brings about the known self-locking jamming.
- FIG. 4 shows the associated force / displacement diagram.
- the disc springs 9 Upon reaching the rated load or shortly thereafter, the disc springs 9 come into effect. Therefore, here the characteristic curves in a flat area, namely until the clamping bush 3 abuts on the release piston 6 on the housing 1, as shown in Figure 3. With further increase in load, the holding force of the clamping device is finally exceeded and it comes to slippage, wherein the holding or braking force is defined by the strength of the disc springs 9.
- the braking force is inventively greater than the weight of the moving mass, therefore, an effective braking of the mass is guaranteed.
- the invention thus offers the advantage that, while maintaining the conventional manufacturing tolerances, it is possible to specify a precisely defined limitation of the clamping force, above which targeted slipping of the rod is permitted.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Clamps And Clips (AREA)
- Actuator (AREA)
- Lock And Its Accessories (AREA)
Abstract
Description
Die Erfindung betrifft eine Vorrichtung zum Verklemmen einer unter Last stehenden Stange mittels zumindest eines am Stangen-Umfang angreifenden Klemmelementes, wobei das Klemmelement an seinem äußeren Umfang konisch geformt und in einem entsprechend konisch geformten Außenring verschiebbar geführt ist, derart, dass das Klemmelement bei Mitnahme durch die Stange in Lastrichtung selbstverstärkend gegen die Stange gepresst wird, wobei der Außenring axial verschiebbar in einem Gehäuse geführt und durch Federn vorgespannt ist.The invention relates to a device for jamming a rod under load by means of at least one acting on the rod circumference clamping element, wherein the clamping element is conically shaped at its outer periphery and slidably guided in a corresponding conically shaped outer ring, such that the clamping element when driving through the rod is pressed in the load direction self-reinforcing against the rod, wherein the outer ring is guided axially displaceably in a housing and biased by springs.
Derartige Klemmvorrichtungen werden beispielsweise zur Fixierung von Hubtischen, Stützzylindern, Theaterpodien und dergleichen eingesetzt. Häufig fungieren sie auch als Absturzsicherung für Vertikalachsen von Werkzeugmaschinen oder Handlinggeräten.Such clamping devices are used for example for fixing lifting tables, support cylinders, theater podiums and the like. Often they also act as fall protection for vertical axes of machine tools or handling equipment.
Üblicherweise werden die Klemmvorrichtungen hydraulisch oder pneumatisch in der Offenstellung gehalten und bei Druckabfall wirksam. Dabei wird die Energie der absinkenden Last zum Erzeugen der Klemmkraft herangezogen.Usually, the clamping devices are hydraulically or pneumatically held in the open position and effective at pressure drop. The energy of the sinking load is used to generate the clamping force.
Eine Klemmvorrichtung mit dem Merkmal des Oberbegriffes von Anspruch 1 ist durch die EP-A 538 962 bekannt geworden. Dabei handelt es sich um die Verklemmung einer Schubstange bei einer Kraftfahrzeug-Lenkung, wobei eine mechanische, von der Lenkrad-Stellung abhängige Verschiebebewegung mit einer hydraulischen Verschiebebewegung überlagert wird.A clamping device having the feature of the preamble of
Eine ähnliche Klemmvorrichtung ist durch die DE 38 11 225 bekannt. Dabei werden die Klemmelemente im Auslösefall von der Stange in Lastrichtung mitgenommen, wobei die konische Außenkontur der Klemmelemente eine sich selbstverstärkende Haftreibung an der Stange erzeugt. Die Klemmelemente laufen dabei - soweit die Nennbelastung nicht wesentlich überschritten wird - nicht gegen einen gehäusefesten Anschlag. Überlasten können deshalb zum Zerstören der Klemmvorrichtung durch plastische Verformung führen. Diese Eigenschaft begrenzt die Einsatzmöglichkeiten auf solche Fälle, bei denen Überlasten ausgeschlossen sind. Deshalb sind diese Klemmvorrichtungen insbesondere nicht geeignet, die kinetische Energie einer abstürzenden Masse zu dissipieren, sie blockieren die Klemmstangen, sind jedoch nicht zum Abbremsen geeignet.A similar clamping device is known from DE 38 11 225. The clamping elements are taken in the case of release of the rod in the load direction, wherein the conical outer contour of the clamping elements generates a self-reinforcing static friction on the rod. The clamping elements run - as far as the rated load is not significantly exceeded - not against a housing-fixed stop. Overloading can therefore lead to the destruction of the clamping device by plastic deformation. This feature limits the scope of use to those cases where overloads are excluded. Therefore, these clamping devices are not particularly suitable for dissipating the kinetic energy of a falling mass, they block the clamping bars, but are not suitable for braking.
Theoretisch wäre es zwar denkbar, die Teile so zu fertigen, dass ein Anschlag für die Axialverschiebung des Klemmelementes gerade so gelegt wird, dass sich eine bestimmte Klemmkraft ergibt, oberhalb der Rutschen eintritt. Damit wäre der genannte Nachteil vermieden. Praktisch ist dies jedoch mit erreichbaren Toleranzforderungen nicht zu gewährleisten.Theoretically, it would indeed be conceivable to manufacture the parts so that a stop for the axial displacement of the clamping element is just placed so that a certain clamping force results above the chutes occurs. This would avoid the mentioned disadvantage. Practically, however, this can not be guaranteed with achievable tolerance requirements.
Hiervon ausgehend liegt der vorliegenden Erfindung die Aufgabe zugrunde, eine Klemmvorrichtung zu entwickeln, die eine exakte Begrenzung der Haltekraft gestattet, wobei im Überlastungsfall ein gezieltes Durchrutschen der Stange ohne Beschädigung der Klemmvorrichtung, insbesondere ohne plastische Verformung der maßgeblichen Teile eintritt. Des weiteren soll sich die erfindungsgemäße Klemmvorrichtung durch kostengünstigen und wenig toleranzempfindlichen Aufbau auszeichnen.Proceeding from this, the present invention has the object to develop a clamping device which allows an exact limitation of the holding force, wherein in the overload case targeted slippage of the rod occurs without damaging the clamping device, in particular without plastic deformation of the relevant parts. Furthermore, the clamping device according to the invention should be characterized by low-cost and low tolerance-sensitive structure.
Diese Aufgabe wird erfindungsgemäß dadurch gelöst, dass das Klemmelement durch Federelemente in Klemmrichtung belastet ist, und dass die Vorspannung der auf den Außenring wirkenden Federn entgegen der Lastrichtung so gerichtet und so bemessen ist, dass die Verschiebung des Außenringes erst bei Überschreiten einer vorgegebenen, definierten Last in der Stange eintritt.This object is achieved in that the clamping element is loaded by spring elements in the clamping direction, and that the bias of acting on the outer ring springs against the load direction is directed and dimensioned so that the displacement of the outer ring only when a predetermined, defined load enters the pole.
Hierdurch ergibt sich folgende Wirkungsweise: Bis zum Erreichen der vorgegebenen definierten Last - im allgemeinen der Nennlast - nimmt die Stange im Auslösefall die Klemmelemente mit, ohne dass deren Axialverschiebung durch einen Anschlag gebremst wird. Erst bei Überschreiten der vorgegebenen Last nehmen die Klemmelemente den unter Vorspannung stehenden Außenring mit, wobei die für die Vorspannung verantwortlichen Federn zusammengedrückt werden, bis die Klemmelemente schließlich durch einen Anschlag an einer weiteren Axialverschiebung gehindert werden. Die für die Vorspannung verantwortlichen Federn ergeben somit eine sehr genau definierbare maximale Haltekraft, bei deren Überschreiten das Durchrutschen der Stange beginnt.This results in the following mode of action: Until reaching the predetermined defined load - generally the nominal load - the rod takes in the triggering case with the clamping elements, without their axial displacement is braked by a stop. Only when the predetermined load is exceeded, the clamping elements take with the biased outer ring, wherein the springs responsible for the bias are compressed until the clamping elements are finally prevented by a stop at a further axial displacement. The responsible for the bias springs thus give a very precisely definable maximum holding force beyond which the slipping of the rod begins.
Für die Ausbildung der Klemmelemente bieten sich dem Fachmann verschiedene Möglichkeiten. Zweckmäßig handelt es sich dabei um eine konische Buchse, die in ihrem wirksamen Bereich einen oder mehrere Axialschlitze aufweist. Es ist aber auch nicht ausgeschlossen, mit mehreren in Umfangsrichtung nebeneinander angeordneten Klemmelementen zu arbeiten.For the formation of the clamping elements offer the expert various possibilities. Appropriately, this is a conical bush, which has one or more axial slots in its effective area. But it is also not excluded to work with several circumferentially juxtaposed clamping elements.
Der die Klemmelemente umgebende Außenring ist zweckmäßig als geschlossener Ring ausgebildet, könnte aber auch aus mehreren Teilen bestehen, wobei aber Sorge dafür getragen werden muss, die auftretenden Radialkräfte abzufangen.The outer ring surrounding the clamping elements is expediently designed as a closed ring, but could also consist of several parts, but care must be taken to intercept the radial forces occurring.
Damit das Klemmelement erst nach Überschreiten der vorgegebenen definierten Last axial gegen seinen Anschlag läuft, empfiehlt es sich, die Vorspannung der am Außenring angreifenden Federn geringfügig höher zu wählen als es für das Halten der vorgegebenen definierten Last (Nennlast) erforderlich wäre. Außerdem wird der Federweg der für die Vorspannung des Außenringes verantwortlichen Federn so gewählt, dass die Axialverschiebung des Außenringes die Federn noch nicht in ihre Blockierposition drückt, vielmehr sollen die genannten Federn eine definierte Kraft auf den Außenring und somit eine definierte Halte- bzw. Bremskraft an der Stange erzeugen, wenn die Axialverschiebung des Klemmelementes beendet ist.Thus, the clamping element runs only after exceeding the predetermined defined load axially against its stop, it is recommended that the bias of the outer ring engaging springs to select slightly higher than it would be required for holding the predetermined defined load (nominal load). In addition, the spring travel of the responsible for the bias of the outer ring springs is chosen so that the axial displacement of the outer ring does not push the springs in their blocking position, but said springs should a defined force on the outer ring and thus a defined holding or braking force generate the rod when the axial displacement of the clamping element is completed.
Grundsätzlich kann das Klemmelement unmittelbar gegen den genannten Anschlag laufen. Im Sinne einer kompakten Bauweise empfiehlt es sich aber, den für das Lösen des Klemmelementes verantwortlichen Lösekolben zwischenzuschalten.In principle, the clamping element can run directly against the abovementioned stop. In terms of a compact design, it is recommended to interpose the responsible for the release of the clamping element release piston.
Des weiteren ist es zweckmäßig, dass der die Klemmelemente umgebende Außenring nicht nur in unbelastetem Zustand, sondern auch unter Last axial beabstandet zum Lösekolben bzw. zu dem Anschlag angeordnet ist, wogegen das Klemmelement stets in Anlage am Lösekolben gehalten wird. Letzteres erfolgt dadurch, dass es in üblicher Weise durch Federelemente in Klemmrichtung belastet ist.Furthermore, it is expedient that the outer ring surrounding the clamping elements not only in the unloaded state, but also under load axially spaced from the release piston or to the stop is arranged, whereas the clamping element is always held in contact with the release piston. The latter takes place in that it is loaded in the usual way by spring elements in the clamping direction.
Wesentlich ist des weiteren, dass die für die Vorspannung des Außenringes verantwortlichen Federn um ein Mehrfaches stärker sind, als die Federelemente, die auf das Klemmelement einwirken.It is also essential that the responsible for the bias of the outer ring springs are many times stronger than the spring elements acting on the clamping element.
Schließlich empfiehlt es sich im Sinne einer kompakten Bauweise, dass sich die für die Vorspannung verantwortlichen Federn an einem ortsfesten Ring abstützen, der zugleich den Stellweg des Lösekolbens begrenzt, nämlich seine Löseposition definiert.Finally, it is recommended in terms of a compact design that the responsible for the bias springs are supported on a stationary ring, which also limits the travel of the release piston, namely defines its release position.
Weitere Merkmale und Vorteile der Erfindung ergeben sich aus der nachfolgenden Beschreibung eines Ausführungsbeispieles anhand der Zeichnung und aus der Zeichnung selbst; dabei zeigt
Figur 1- einen Axialschnitt der Klemmvorrichtung in gelöstem Zustand,
Figur 2- den oberen Teil des Axialschnittes von
Figur 1, jedoch in wirksamer Stellung, wobei die Last in der Stange unterhalb der Nennlast liegt; Figur 3- einen Schnitt
entsprechend Figur 2, wobei jedoch die Last in der Stange oberhalb der Nennlast liegt; Figur 4- ein Kraft-/Weg-Diagramm der erfindungsgemäßen Klemmvorrichtung.
- FIG. 1
- an axial section of the clamping device in a dissolved state,
- FIG. 2
- the upper part of the axial section of Figure 1, but in an effective position, wherein the load in the bar is below the rated load;
- FIG. 3
- a section corresponding to Figure 2, but with the load in the bar above the rated load;
- FIG. 4
- a force / displacement diagram of the clamping device according to the invention.
Ein zylindrisches Gehäuse 1, das aus zwei axial benachbarten Gehäuseteilen 1 a und 1 b besteht, wird in seinem Zentrum von einer Stange 2 durchquert. Das Gehäuse 1 ist in nicht dargestellter Weise ortsfest montiert, während die Stange 2 das verschiebbare Maschinenelement darstellt, das von der Klemmvorrichtung festgehalten werden soll. Dazu ist die Stange 2 von Klemmelementen umgeben, die im Ausführungsbeispiel die Form einer an ihrem äußeren Umfang konischen Buchse 3 haben. Diese konische Buchse hat in bekannter Weise Axialschlitze, so dass sie in Radialrichtung elastisch ist. Sie steckt im Innenkonus eines Außenringes 4, auf den später näher eingegangen wird und wird in Axialrichtung durch ein Tellerfederpaket 5 in Klemmrichtung belastet. An ihrem dem Federpaket 5 abgewandten Ende stößt die Klemmbuchse 3 gegen einen Lösekolben 6, der seinerseits axial verschiebbar in dem Gehäuseteil 1 b geführt ist. An seiner der Klemmbuchse 3 abgewandten Stirnseite bildet der Lösekolben 6. mit dem Gehäuseteil 1 b einen Zylinderraum 7. Dieser Zylinderraum 7 ist über eine Gehäusebohrung mit Druckmittel - Druckluft oder Hydrauliköl - beaufschlagbar, so dass er die Klemmbuchse 3 aus Ihrer Klemmstellung heraus nach links verschieben kann. Der Hubweg des Lösekolbens 6 wird in der Lösestellung durch einen Anschlagring 8 begrenzt. Dieser Anschlagring sitzt zweckmäßig in einer Ausdrehung am Übergang zwischen den beiden Gehäusehälften 1a und 1b und ist somit axial festgelegt.A
Wesentlich ist nun, dass der bereits genannte Außenring 4 axial verschiebbar in dem Gehäuseteil 1a geführt ist und dass er durch Federn 9 - vorzugsweise ein Tellerfederpaket - entgegen der Lastrichtung, also im Sinne einer Verklemmung der Klemmbuchse 3 vorgespannt ist. Die Tellerfedern 9 sind in einer ringförmigen Aussparung des Außenringes 4 angeordnet und stützen sich an ihrer dem Außenring abgewandten Stirnseite an dem bereits genannten Anschlagring 8 ab. Die Vorspannung der Tellerfedern 9 ist so gewählt, dass sie erst dann nachgeben, wenn in der Stange 2 eine Last auftritt, die oberhalb der Nennlast der Klemmvorrichtung liegt. Dadurch ergibt sich folgende Funktion:It is essential that the already mentioned
Bei Normalbetrieb soll die Stange 2 die Klemmvorrichtung in beiden Richtungen passieren können. Dazu ist der Zylinderraum 7 mit Druckmittel beaufschlagt, so dass der Lösekolben 6 den Klemmkonus 3 entgegen der auf ihn einwirkenden Federelemente 5 nach links in die Lösestellung verschiebt bzw. dort hält. Dieser Zustand ist in Figur 1 dargestellt.During normal operation, the
Der Klemmzustand wird dadurch ausgelöst, dass der Druck im Zylinderraum 7 abgeschaltet wird. Dadurch können die Federn 5 den Konusring nach rechts verschieben, wobei diese Verschiebebewegung durch die Bewegung der Stange 2 unterstützt wird und die bekannte selbsthemmende Verklemmung herbeiführt.The clamping state is triggered by the fact that the pressure in the cylinder chamber 7 is turned off. This allows the
Solange die Last in der Stange unterhalb der Nennlast liegt, halten die Tellerfedern 9 den Außenring 4 in seiner linken Anschlagposition, wogegen die Klemmbuchse 3 von der Stange 2 in Lastrichtung mitgenommen wird. Dieser Zustand ist in Figur 2 dargestellt.As long as the load in the rod is below the rated load, the disc springs 9 hold the
Wird die Nennlast um einen gewissen Betrag überschritten, so können die Tellerfedern 9 den Außenring 4 nicht mehr in der linken Anschlagposition halten. Er wird dann zusammen mit der Klemmbuchse 3 und dem an ihr anliegenden Lösekolben 6 nach rechts verschoben, bis der Lösekolben 6 und damit die Klemmbuchse 3 am Gehäuse 1 b anstößt. Dieser Zustand ist in Figur 3 dargestellt.If the rated load is exceeded by a certain amount, the disc springs 9 can no longer hold the
Falls die Last in der Stange 2 weiter zunimmt, tritt Durchrutschen ein. Dieses Durchrutschen erfolgt aber im Gegensatz zu den bekannten Klemmvorrichtungen bei einer genau definierten Bremskraft. Diese Bremskraft ist gegeben durch die Federkraft der Tellerfedern 9, den Konuswinkel und die Reibbeiwerte. Hingegen ist diese Bremskraft unabhängig von der Last in der Stange 2.If the load in the
Figur 4 zeigt das zugehörige Kraft-/Weg-Diagramm. Man erkennt zunächst einen geradlinigen Anstieg der Haltekraft bis zum Erreichen der Nennlast. Dieser Teil der Kennlinie beruht auf der Verschiebung der Klemmbuchse 3 relativ zum Au-ßenring 4 und der dadurch eintretenden selbsthemmenden Verstärkung der Klemmkraft.FIG. 4 shows the associated force / displacement diagram. One first recognizes a rectilinear increase in the holding force until the rated load is reached. This part of the characteristic is based on the displacement of the clamping
Bei Erreichen der Nennlast oder kurz danach kommen die Tellerfedern 9 zur Wirkung. Daher knickt hier die Kennlinie in einen flachen Bereich um, und zwar bis die Klemmbuchse 3 über den Lösekolben 6 am Gehäuse 1 anstößt, wie dies in Figur 3 dargestellt ist. Bei weiterer Lastzunahme wird schließlich die Haltekraft der Klemmvorrichtung überschritten und es kommt zum Durchrutschen, wobei die Halte- bzw. Bremskraft durch die Stärke der Tellerfedern 9 definiert wird. Die Bremskraft ist dabei erfindungsgemäß größer als das Gewicht der bewegten Masse, deshalb ist ein wirksames Abbremsen der Masse gewährleistet.Upon reaching the rated load or shortly thereafter, the disc springs 9 come into effect. Therefore, here the characteristic curves in a flat area, namely until the clamping
Zusammenfassend bietet die Erfindung also den Vorteil, dass man unter Beibehaltung der herkömmlichen Fertigungstoleranzen eine genau definierte Begrenzung der Klemmkraft vorgeben kann, oberhalb der ein gezieltes Durchrutschen der Stange erlaubt ist.In summary, the invention thus offers the advantage that, while maintaining the conventional manufacturing tolerances, it is possible to specify a precisely defined limitation of the clamping force, above which targeted slipping of the rod is permitted.
Claims (8)
- A device for clamping a loaded rod (2) by means of at least one clamping element (3) acting on the circumference of the rod, wherein the clamping element (3) is conically shaped on its outer circumference and movably guided in a corresponding conically shaped outer ring (4), in such a way that when the clamping element (3) is entrained by the rod (2) it is pressed in a self-reinforcing manner against the rod (2) in the load direction, wherein the outer ring (4) is guided so as to be axially movable in a housing (1) and is biased by springs (9), characterised in that the clamping element (3) is loaded by spring elements (5) in the clamping direction, and that the bias of the springs (9) acting on the outer ring (4) is directed against the load direction and is of such a magnitude that the displacement of the outer ring (4) only occurs when a predetermined defined load in the rod (2) is exceeded.
- Device as claimed in Claim 1, characterised in that the theoretical travel of the springs (9) which effect the bias is greater than the maximum axial displacement of the outer ring (4) under load.
- Device as claimed in Claim 1, characterised in that the clamping element (3) moves in the load direction against a stop in the housing (1) - preferably with at least one release piston (6) interposed.
- Device as claimed in Claim 1, characterised in that the outer ring (4) - under load - is disposed axially spaced from the release piston (6).
- Device as claimed in Claim 3, characterised in that the clamping element (3) rests axially on the release piston (6).
- Device as claimed in Claim 1, characterised in that the springs (9) which are responsible for biasing the outer ring (4) are several times stronger than the spring elements (5) acting on the clamping bush (3).
- Device as claimed in Claim 1, characterised in that the springs (9) which are responsible for biasing the outer ring (4) are designed so that the retaining force produced by the springs is greater than the maximum load acting on the rod (2).
- Device as claimed in Claim 1, characterised in that the springs (9) which are responsible for the biasing are supported on a stationary stop ring (8) which simultaneously limits the control path of the release piston (6) in the release position.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE10350225 | 2003-10-27 | ||
| DE10350225A DE10350225A1 (en) | 2003-10-27 | 2003-10-27 | Locking device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP1528267A1 EP1528267A1 (en) | 2005-05-04 |
| EP1528267B1 true EP1528267B1 (en) | 2007-01-24 |
Family
ID=34399573
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP04023895A Expired - Lifetime EP1528267B1 (en) | 2003-10-27 | 2004-10-07 | Locking device |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US7178639B2 (en) |
| EP (1) | EP1528267B1 (en) |
| JP (1) | JP2005132632A (en) |
| AT (1) | ATE352721T1 (en) |
| CA (1) | CA2485613A1 (en) |
| DE (2) | DE10350225A1 (en) |
Families Citing this family (17)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102005052755B4 (en) * | 2005-06-14 | 2014-11-20 | Bosch Rexroth Aktiengesellschaft | Hydraulically operated clamping unit and thus executed hydraulic control axis |
| DE102006004659A1 (en) * | 2006-01-31 | 2007-08-02 | Sitema Gmbh & Co. Kg | clamping device |
| US20070246785A1 (en) * | 2006-04-20 | 2007-10-25 | Asml Netherlands B.V. | Locking device, adjustment mechanism and lithographic apparatus |
| US8020893B2 (en) * | 2007-09-27 | 2011-09-20 | Caterpillar Inc. | Steering column assembly including a mechanical strut and machine using same |
| US7748785B2 (en) * | 2007-09-27 | 2010-07-06 | Caterpillar Inc | Seat assembly including a mechanical strut and machine using same |
| DE102009011003A1 (en) * | 2009-03-02 | 2010-09-09 | Sitema Gmbh & Co. Kg | Clamping unit, in particular for use as a mold clamping unit |
| DE102010023701A1 (en) | 2010-06-14 | 2011-12-15 | Pintsch Bubenzer Gmbh | Ventilating apparatus for use in brake system, has brake head adjustable between braking and ventilating positions by working positioning device, where brake head occupies brake position under effect of engagement force applied by clutch |
| DE102010023700B4 (en) | 2010-06-14 | 2012-01-26 | Pintsch Bubenzer Gmbh | Adjusting device for a self-energizing brake device and self-energizing brake device |
| DE102010023699B4 (en) | 2010-06-14 | 2012-02-23 | Pintsch Bubenzer Gmbh | Self-energizing brake device |
| CN102425586B (en) * | 2011-12-21 | 2014-12-10 | 徐州重型机械有限公司 | Hydraulic cylinder, hydraulic system and engineering machine |
| CN102628463A (en) * | 2012-04-03 | 2012-08-08 | 无锡亿利大机械有限公司 | Mechanical self-locking hydraulic cylinder |
| CN103362896B (en) * | 2013-07-23 | 2016-08-24 | 云南兴长江实业有限公司 | A kind of safe locking device being suitable for hydraulic jack |
| KR101512471B1 (en) * | 2014-09-11 | 2015-04-16 | 한국뉴매틱(주) | Rod materials locking device using lock-block |
| DE102015212851A1 (en) * | 2015-07-09 | 2017-01-12 | Sms Group Gmbh | Hydraulic cylinder, device for forming workpieces, use of a front cover part |
| US10040152B2 (en) * | 2015-08-17 | 2018-08-07 | GM Global Technology Operations LLC | Mechanical lock for a work support |
| FI127824B (en) * | 2018-01-22 | 2019-03-15 | Valmet Technologies Oy | Mass damper and arrangement in a fibre web machine |
| CN110513377A (en) * | 2019-09-19 | 2019-11-29 | 中国科学院武汉岩土力学研究所 | Locking devices and impact devices |
Family Cites Families (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2632425A (en) * | 1950-05-26 | 1953-03-24 | Reginald L Grover | Piston lock |
| DE1804857B2 (en) * | 1968-10-24 | 1971-11-25 | Hänchen, Siegfried, 7304 Ruit | DEVICE FOR CLAMPING AN AXIALLY MOVABLE PISTON ROD |
| DE2845266C2 (en) * | 1978-10-18 | 1983-03-03 | Ringspann Albrecht Maurer Kg, 6380 Bad Homburg | Safety parking brake for hydraulic lifts, lifting platforms and the like. |
| DE3118449A1 (en) * | 1981-05-09 | 1982-12-02 | Sitema Gesellschaft für Sicherheitstechnik und Maschinenbau mbH, 7500 Karlsruhe | "CLAMPING DEVICE" |
| SE441468B (en) * | 1982-08-20 | 1985-10-07 | Atlas Copco Ab | DISPOSABLE LOADING DEVICE FOR A PRESSURE MANUFACTURED PISTON CYLINDER |
| DE3707046A1 (en) * | 1987-03-05 | 1988-09-15 | Haenchen Kg Herbert | Clamping device for rods |
| DE8804418U1 (en) * | 1988-04-02 | 1988-05-19 | Sitema Gesellschaft für Sicherheitstechnik und Maschinenbau mbH, 7500 Karlsruhe | Braking and locking device |
| DE3811225C2 (en) * | 1988-04-02 | 1996-07-11 | Sitema | Hydraulic support device for vehicles |
| DE3907780A1 (en) * | 1989-03-10 | 1990-09-13 | Bosch Gmbh Robert | Brake device for a piston rod |
| DE4126897A1 (en) * | 1991-08-14 | 1993-02-18 | Rexroth Mannesmann Gmbh | Hydraulic clamp for vehicle rear wheel - has housing with clamping sleeve to control motion and cage assembly between sleeve and rod. |
| FR2682925B1 (en) * | 1991-10-25 | 1997-08-29 | Renault | DEVICE FOR STEERING THE STEERING WHEELS OF A VEHICLE. |
| DE19508175A1 (en) * | 1995-03-09 | 1996-09-12 | Montan Hydraulik Gmbh & Co Kg | Clamping device for cylindrical, axially displaceable or rotating parts |
| JP3856934B2 (en) * | 1998-01-27 | 2006-12-13 | Ｓｍｃ株式会社 | Fluid pressure cylinder with lock mechanism |
| US6367591B1 (en) * | 1999-12-21 | 2002-04-09 | Caterpillar Inc. | Automatic brake clearance adjuster |
-
2003
- 2003-10-27 DE DE10350225A patent/DE10350225A1/en not_active Withdrawn
-
2004
- 2004-10-07 EP EP04023895A patent/EP1528267B1/en not_active Expired - Lifetime
- 2004-10-07 DE DE502004002749T patent/DE502004002749D1/en not_active Expired - Lifetime
- 2004-10-07 AT AT04023895T patent/ATE352721T1/en not_active IP Right Cessation
- 2004-10-21 CA CA002485613A patent/CA2485613A1/en not_active Abandoned
- 2004-10-27 JP JP2004311853A patent/JP2005132632A/en active Pending
- 2004-10-27 US US10/974,269 patent/US7178639B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| ATE352721T1 (en) | 2007-02-15 |
| EP1528267A1 (en) | 2005-05-04 |
| DE502004002749D1 (en) | 2007-03-15 |
| DE10350225A1 (en) | 2005-05-19 |
| US20050087405A1 (en) | 2005-04-28 |
| US7178639B2 (en) | 2007-02-20 |
| JP2005132632A (en) | 2005-05-26 |
| CA2485613A1 (en) | 2005-04-27 |
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