EP1071633A2 - Manually controlled lifting device with a pneumatic lift drive mechanism - Google Patents
Manually controlled lifting device with a pneumatic lift drive mechanismInfo
- Publication number
- EP1071633A2 EP1071633A2 EP99913081A EP99913081A EP1071633A2 EP 1071633 A2 EP1071633 A2 EP 1071633A2 EP 99913081 A EP99913081 A EP 99913081A EP 99913081 A EP99913081 A EP 99913081A EP 1071633 A2 EP1071633 A2 EP 1071633A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- load
- throttle
- lifting
- compressed air
- pressure chamber
- 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.)
- Granted
Links
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
- B66C13/00—Other constructional features or details
- B66C13/04—Auxiliary devices for controlling movements of suspended loads, or preventing cable slack
Definitions
- the invention relates to a hand-controlled lifting device with a pneumatic lifting drive, a lifting element connected to it, a load-carrying means arranged at the end of the lifting element, and a pneumatic switch which is integrated in a pressure line connecting a compressed air source with a pressure space of the lifting drive and which connects the pressure space of the lifting drive in connects in one position to the compressed air source and in another position to a ventilation device.
- the invention has for its object to provide such a lifting device with little additional technical effort, which achieves at least approximately the same lifting and lowering speeds in the entire working area and regardless of the load to be moved.
- this object is achieved in that a flow control flow lying in the load flow is integrated between two load-transmitting components, which is simultaneously switched on between the pneumatic switch and the pressure chamber of the linear actuator in the compressed air line, and the flow cross section under the action of the load acting on the load-carrying means the compressed air line automatically varies so that a) a larger flow cross-section occurs during a lifting operation at high load than at low load, and b) a smaller flow cross-section sets at lower load than at lower load.
- the flow control device can contain a) two adjustable throttle valves connected in parallel, to which b) a non-return valve is connected in series, and c) one in the direction of flow from the pneumatic switch to the pressure chamber a non-return valve is assigned a throttle valve, which increases the throttle cross section when the load increases and d) a non-return valve is assigned to the non-return valve opening in the opposite flow direction, which reduces the throttle cross section when the load increases.
- the throttle valves can be position-controlled in such a way that when their axial length changes, the throttle effect changes accordingly.
- Such throttle valves can be designed such that a spring-loaded actuating pin protrudes from an axially extending housing, the axial displacement of which changes the throttle cross-section inside the housing.
- the two throttle valves can be accommodated in a common outer housing in such a way that their two axial ends lie against the inner surfaces of two opposite walls of the outer housing, the mutual distance of which can be changed under elastic deformation, on the outer surfaces of which tensile or compressive forces from load-transmitting parts attack.
- FIG. 1 in partial longitudinal section, the schematic representation of a lifting device with einam rope as a lifting device
- Fig. 2 shows the side view of a lifting device with a mechanical boom as
- FIGS. 6 to 8 different embodiments of outer housings
- a pneumatic lifting drive 1 in the form of a pneumatic cylinder is provided, in which a pressure chamber 3 is arranged below a piston 2.
- a rope 5 is fastened as a lifting member, which carries a crane hook 6 as a load-carrying means at its lower end.
- the pressure chamber 3 is fed with compressed air from a compressed air source 8 via a pressure line 7. Behind the compressed air source 8, a pneumatic switch 9 is switched on in the pressure line 7 and subsequently a flow control device 10 behind it.
- the pneumatic switch 9 has three show positions I, 0 and I. In the switching position I shown, the switch allows the compressed air to flow freely from the compressed air source 8 to the flow control device. If the switch is switched to the switch position 0, this flow is prevented, as is a backflow of air via the pressure line 7. In this switch position, for example, a raised load is held in the position reached. Finally, in switch position II, the compressed air supply from the compressed air source 8 is completed, while the reflux of the air from the pressure chamber 3 to the ventilation device 11 is open.
- the compressed air line is branched and reaches two adjustable throttle valves D1 and D2 connected in parallel, each of which has a check valve R1 and R2 connected in series.
- the compressed air line then unites again and thus reaches the pressure chamber 3 of the linear actuator 1
- the compressed air coming from the compressed air source 8 flows to the flow control device 10, it can flow there through the adjustable throttle valve D1 and the check valve R1, which then opens, to the pressure chamber 3, while the second flow path is via the Throttle valve D2 is completed by the check valve R2.
- the throttle valve D1 is adjusted by the force F acting on the crane hook 6 in such a way that the throttle cross section is reduced when the load F is low, but increased when the load F rises. This ensures that the lifting speed is at least approximately the same regardless of the size of the load.
- the pneumatic switch 9 must be brought into the switching position ü. Characterized the pressure line 7 is connected to the venting device 1 1. The air emerging from the pressure chamber 3 when the piston 2 sinks flows via the pressure line 7 to the flow control device 10, where it now opens the non-return valve R2 and then flows through the adjustable throttle valve D2. The throttle valve becomes a function of the force acting on the crane hook 6 F is adjusted so that it decreases the throttle cross-section with increasing force F and thus prevents an abrupt drop in the load.
- a parallel log arm 13 and a bracket 14 are pivotably mounted on a standing column 12.
- a pneumatic lifting drive 1 is supported on the console 14 with the interposition of a flow control device 10 and engages with the piston rod 4 on the parallelogram boom 13, as a result of which the latter is raised and lowered can be.
- a load arm 15 is pivotally mounted on the parallelogram boom 13 and carries a crane hook 6 at its end. Above the crane hook 6 there is a pneumatic switch 9, which is connected via a pressure line 7 on the one hand to a compressed air source 8 and on the other hand to the flow control device 10, which in turn is connected to the pressure chamber of the linear actuator 1 via a pressure line 7.
- the course of action here is the same as described above in FIG. 1.
- FIG. 3 shows an adjustable throttle valve which consists of a housing 16, the interior 17 of which has an inlet air opening 18 and an outlet air opening 19.
- An intermediate wall 20, which has a throttle bore 21, is arranged in the interior 17 between these openings.
- a conical throttling needle 22 plunges into this, which is connected to a longitudinally displaceable cylindrical guide point 23 which is mounted in the housing 16 and which in turn has an actuating pin 24 projecting axially from the housing 16.
- the throttle needle is from the bottom to a pressure plate 25, which is under the action of a spring 26, which presses the throttle needle in an upper Endst ⁇ llung.
- this throttle valve is installed in a flow control device in such a way that the actuating pin 24 is pressed into the housing 16 as the load increases, the throttle cross section is thereby increasingly reduced.
- the variant of a throttle valve shown in FIG. 4 differs from that of FIG. 3 only in that the throttle needle 22 is conical in the opposite direction, so that in this case the throttle cross section is enlarged when the actuating pin 24 is pushed into the housing 16.
- FIG. 5 shows an embodiment of a double-acting throttle valve.
- an inlet air bore 18 opens into the interior 17 of the housing 16.
- Two exhaust air openings 19 and 27 are provided at an axial distance from one another.
- an intermediate wall 20 is provided in the interior 17, each one Have throttle bore 21.
- a conical throttle needle 22 is immersed, which is connected to one another and is conical in opposite directions. If the actuating pin is pressed down in this case, the throttle cross section between the supply air opening 18 and the exhaust air opening 19 is simultaneously increasingly reduced, while at the same time the throttle cross section between the supply air bore 18 and the exhaust air bore 27 is increased.
- This throttle valve thus replaces the two throttle valves D1 and D2 shown in FIG. 1.
- FIG. 6 shows a pot-shaped outer housing 28, in which an inverted cup-shaped hollow piston 29 is mounted so as to be longitudinally lockable.
- the outer housing 28 is closed at its open end by an inserted cover 30, through which a tension bolt 31 projects, which also projects by means of a screw the bottom of the hollow piston 29 is connected.
- a plate spring assembly 32 Arranged between the bottom of the hollow piston 29 on the one hand and the cover 30 on the other hand is a plate spring assembly 32 which presses the hollow piston 29 downward in the outer housing 28.
- two adjustable throttle valves 33 and 34 are used, which are supported on the one hand on the closed bottom of the outer housing and on the other hand on the closed bottom of the hollow piston with their actuating pins 24.
- the throttle valves 33 and 34 are in one case a throttle valve according to FIG. 3 and in the other case one according to FIG. 4. If this component is used e.g. in the rope 5 according to Flg. 1 installed, the rope forces act on the one hand on the tension bolt 31 and on the other hand on the bottom of the outer housing 28, the hollow piston 29 being moved upward against the action of the spring assembly 32 with increasing load, as a result of which the actuating pins 24 continue to move out of the housings of the throttle valves 33 and 34 emerge and thus the throttle cross sections are changed inside.
- FIG. 7 A reverse variant is shown in FIG. 7.
- an outer housing 35 is provided, in which a hollow piston 36 is mounted so as to be longitudinally displaceable and secured by a snap ring 37 so that it can emerge downwards.
- An action acts between the bottom of the outer housing 35 and the end face of the hollow piston 36 Disc spring package 38, in the center of which a support !! 39 is provided, against which the actuating pin 24 of a throttle valve 40 is supported, which is a double-acting throttle valve according to FIG. 5.
- this component which is stressed by the load to be moved by the lifting device, can be used, for example, in an embodiment according to FIG. 2.
- Fig. 8 finally shows a relatively simple variant, in which a double-acting throttle valve 40 is inserted into a metal ring 41, which deforms in the longitudinal direction of the throttle valve under the action of tensile or compressive forces, so that the actuating pin 24 in one Fall is pushed into the throttle valve, - or can continue to emerge from it in the other case.
Abstract
The invention relate to a manually controlled lifting device with a pneumatic lift drive mechanism (1), a lifting organ (5, 13) connected thereto, load receiving means (6) arranged on the end of the lifting organ and a pneumatic switch (9) that is integrated into a pressure line (7) connecting a compressed air source (8) to a pressure chamber (3) of the lift drive mechanism (1) and connecting the pressure chamber (3) of the lift drive mechanism (1) to the compressed air source (8) in one position (I) and to a ventilation device (11) in another position (II). A flow-through control device (10) located in the load flow is integrated in-between both load-transmitting components (5-5; 13-14). Said device is simultaneously connected between the pneumatic switch (9) and the pressure chamber (3) of the lift drive mechanism (1) in the compressed air line (7). Said device automatically varies the through-flow cross section of the compressed air line (7) under the influence of the load engaged in the load receiving means (6) in such a way that a) the through-flow cross section during a lifting operation with a heavy load is larger than when the load is lighter and b) the through-flow cross section during a lowering operation with a heavy load is smaller than when the load is lighter.
Description
Handgesteuertes Hebegerät mit einem pneumatischen Hubantrieb Hand-operated lifting device with a pneumatic lifting drive
Die Erfindung betrifft ein handgesteuertes Hebegerät mit einem pneumatischen Hubantrieb, einem mit diesem verbundenen Huborgan, einem am Ende des Huborgans angeordneten Lastaufnahmemittel und einem pneumatischen Schalter, der in eine eine Druckluftquelle mit einem Druckraum des Hubantriebs verbindende Druckleitung integriert ist und der den Druckraum des Hubantriebs in einer Stellung mit der Druckluftquelle und in einer anderen Stellung mit einer Entlüftungseinrichtung verbindet.The invention relates to a hand-controlled lifting device with a pneumatic lifting drive, a lifting element connected to it, a load-carrying means arranged at the end of the lifting element, and a pneumatic switch which is integrated in a pressure line connecting a compressed air source with a pressure space of the lifting drive and which connects the pressure space of the lifting drive in connects in one position to the compressed air source and in another position to a ventilation device.
Es ist eine Vielzahl derartiger Hebβgeräte bekannt geworden, bei denen das Huborgan im einfachsten Fall durch ein Seil gebildet Ist, In anderen Fällen aber auch z.B. durch den Ausleger eines Manipulators, das Scherensystem einer Hebebühne od.dgl. Alle diese Ausführungen weisen die nachteilige Erscheinung auf, daß die Hub- und Senkgeschwindigkeit sehr stark von der zu bewegenden Last abhängt. Die Ursache dafür liegt in der Grundbeziehung p - V=coπst.: Bei gegebenem Hub muß dem Druckraum des Hubantriebs z.B. bei doppelter Last die zweifache Luftmenge zugeführt werden, was sich in entsprechend verringerter Hubgeschwindigkeit auswirkt. Dies kann zu unangenehmen und sogar gefährlichen
Betriebszuständen führen, wenn z.B das Huborgan unbelastet angehoben wird Insbesondere wenn dieses als quasi masselosβs Seil ausgeführt ist, fuhrt das zu einem schlagartigen Hochschnellen, was das gefürchtete und für die Bedienungs- persoπ äußerst gefährliche Seilpeltscheπ auslost. Eine ähnliche Erscheinung tritt beim Absenken einer Last auf, wenn beim Entlüften des Druckraumes des Hubantriebs sich die Last mit hoher Geschwindigkeit absenkt und auf eine Unterlage aufschlagt.A large number of such lifting devices have become known in which the lifting member is formed in the simplest case by a rope, but in other cases also by the arm of a manipulator, the scissor system of a lifting platform or the like. All these designs have the disadvantageous appearance that the lifting and lowering speed depends very much on the load to be moved. The reason for this lies in the basic relationship p - V = coπst .: For a given stroke, twice the amount of air must be supplied to the pressure chamber of the stroke drive, for example with a double load, which results in a correspondingly reduced stroke speed. This can be uncomfortable and even dangerous Operating conditions lead, for example, when the lifting element is lifted unloaded. Especially when it is designed as a quasi massless rope, this leads to a sudden surge, which triggers the feared and extremely dangerous rope operator for the operating personnel. A similar phenomenon occurs when lowering a load, if the load lowers at high speed when venting the pressure chamber of the linear actuator and hits a base.
Der Erfindung liegt die Aufgabe zugrunde, bei geringem technischen Mehraufwand ein derartiges Hebegerat zu schaffen, das im gesamten Arbeitsbereich und unabhängig von der zu bewegenden Last wenigstens annähernd gleiche Hub- und Senkgeschwindigkeiten erreicht.The invention has for its object to provide such a lifting device with little additional technical effort, which achieves at least approximately the same lifting and lowering speeds in the entire working area and regardless of the load to be moved.
Nach der Erfindung wird diese Aufgabe dadurch gelöst, daß zwischen zwei lastübertragende Bauteile eine im Lastfluß liegende Durchflußsteueremπchtung integriert Ist, die gleichzeitig zwischen dem pneumatischen Schalter und dem Druckraum des Hubantriebs in die Druckluftleitung eingeschaltet ist, und die unter Einwirkung der am Lastaufnahmemittel angreifenden Last den Durchflußquerschnitt der Druckluftleitung selbsttätig so variiert, daß sich a) bei einem Hubvorgang bei hoher Last ein größerer Durchflußquerschnitt einstellt, als bei geringer Last und b) bei einem Absenkvorgaπg bei hoher Last ein kleinerer Durchflußquerschnitt einstellt, als bei geringerer Last.According to the invention, this object is achieved in that a flow control flow lying in the load flow is integrated between two load-transmitting components, which is simultaneously switched on between the pneumatic switch and the pressure chamber of the linear actuator in the compressed air line, and the flow cross section under the action of the load acting on the load-carrying means the compressed air line automatically varies so that a) a larger flow cross-section occurs during a lifting operation at high load than at low load, and b) a smaller flow cross-section sets at lower load than at lower load.
Durch diese Maßnahmen wird unabhängig von der zu bewegenden Last stets eine nahezu gleiche Hub- bzw. Senkgeschwtndigkeit erzielt.These measures always achieve almost the same lifting or lowering speed regardless of the load to be moved.
Zur konstruktiven Realisierung dieser Maßnahmen kann die Durchflußsteuer- einrichtung a) zwei zueinander parallel geschaltete verstellbare Drosselventile enthalten, zu denen b) je ein Rückschlagventil in Serie geschaltet ist, und wobei c) dem einen in Fließrichtung vom pneumatischen Schalter zum Druckraum
öffnenden Rückschlagventil ein Drosselventil zugeordnet ist, welches bei ansteigender Last den Drosselquerschnltt vergrößert und d) dem in entgegengesetzter Fließrichtung öffnenden Rückschlagventil ein Drosselventil zugeordnet ist, welches bei ansteigender Last den Drosselquerschnitt verkleinert.To constructively implement these measures, the flow control device can contain a) two adjustable throttle valves connected in parallel, to which b) a non-return valve is connected in series, and c) one in the direction of flow from the pneumatic switch to the pressure chamber a non-return valve is assigned a throttle valve, which increases the throttle cross section when the load increases and d) a non-return valve is assigned to the non-return valve opening in the opposite flow direction, which reduces the throttle cross section when the load increases.
Durch diese Kombination von je zwei verstellbaren Drosselventilen und zwei Rückschlagventilen wird erreicht, daß die oben beschriebenen gefährlichen schnellen Hub- bzw. Seπkvorgänge mit Sicherheit vermieden werden.This combination of two adjustable throttle valves and two check valves ensures that the dangerous rapid lifting and lowering processes described above are avoided with certainty.
Die Drosselventile können derart weggesteuert sein, daß sich bei Änderung ihrer axialen Länge eine entsprechende Änderung der Drosselwirkung ergibt. Konstruktiv können solche Drosselventile so ausgeführt sein, daß aus einem sich axial erstreckenden Gehäuse ein federbelasteter Betätigungsstift herausragt, bei dessen Axialverschiebung der Drosselquerschnitt im Gehäuseinnern verändert wird.The throttle valves can be position-controlled in such a way that when their axial length changes, the throttle effect changes accordingly. Such throttle valves can be designed such that a spring-loaded actuating pin protrudes from an axially extending housing, the axial displacement of which changes the throttle cross-section inside the housing.
Urn eine möglichst kompakte Konstruktion zu erreichen, kann es zweckmäßig sein, die beiden Drosselventile, oder alternativ beide Drosselventile und beide Rückschlagventile zu einer gemeinsamen Baueinheit zusammenzufassen.In order to achieve the most compact possible construction, it may be expedient to combine the two throttle valves, or alternatively both throttle valves and both check valves, into a common structural unit.
Die beiden Drosselventile können so in einem gemeinsamen Außengehäuse untergebracht werden, daß sie mit ihren beiden axialen Enden gegen die Innenflächen zweier einander gegenüberliegender Wände des Außengehäuses, deren gegenseitiger Abstand unter elastischer Verformung veränderbar ist, anliegen, an deren Außenflächen Zug- oder Druckkräfte aus lastübertragenden Teilen angreifen.The two throttle valves can be accommodated in a common outer housing in such a way that their two axial ends lie against the inner surfaces of two opposite walls of the outer housing, the mutual distance of which can be changed under elastic deformation, on the outer surfaces of which tensile or compressive forces from load-transmitting parts attack.
Die lastabhängige elastische Verformung des Außengehäuses wirkt damit so auf die Drosselventile ein, daß sich In allen Betriebszuständen nahezu gleiche Hubbzw. Senkgeschwindigkeit einstellt.
In den Zeichnungen sind Ausführungsbeispiele der Erfindung dargestellt. Es zeigen:The load-dependent elastic deformation of the outer housing thus acts on the throttle valves so that almost the same stroke or in all operating states. Sets lowering speed. Exemplary embodiments of the invention are shown in the drawings. Show it:
Fig. 1 im Teil-Längsschnitt die schematische Darstellung eines Hebegerätes mit einam Seil als Huborgan, Fig. 2 die Seitenansicht eines Hebegeräts mit einem mechanischen Ausleger alsFig. 1 in partial longitudinal section, the schematic representation of a lifting device with einam rope as a lifting device, Fig. 2 shows the side view of a lifting device with a mechanical boom as
Huborgan, Fig. 3 bis 5 Längsschnitte durch unterschiedliche Ausführungsarten vonLifting device, Fig. 3 to 5 longitudinal sections through different designs of
Drosselventilen und Fig. 6 bis 8 unterschiedliche Ausführungsformen von Außengehäusen zurThrottle valves and FIGS. 6 to 8 different embodiments of outer housings
Unterbringung von Drosselventilen.Housing throttle valves.
Bei dem in Fig. 1 dargestellten Hebegerät ist ein pneumatischer Hubantrieb 1 in Form eines Pnβumatikzylinders vorgesehen, bei dem unterhalb eines Kolbens 2 ein Druckraum 3 angeordnet ist. An der Kolbenstange 4 Ist ein Seil 5 als Huborgan befestigt, welches an seinem unteren Ende einen Kranhaken 6 als Lastaufnahmemittel trägt.In the lifting device shown in FIG. 1, a pneumatic lifting drive 1 in the form of a pneumatic cylinder is provided, in which a pressure chamber 3 is arranged below a piston 2. On the piston rod 4, a rope 5 is fastened as a lifting member, which carries a crane hook 6 as a load-carrying means at its lower end.
Der Druckraum 3 wird über eine Druckleitung 7 von einer Druckluftquelle 8 mit Druckluft gespeist. Hinter der Druckluftquelle 8 ist in die Druckleitung 7 ein pneumatischer Schalter 9 eingeschaltet und In weiterer Folge hinter diesem eine Durchflußsteuerβinrichtung 10.The pressure chamber 3 is fed with compressed air from a compressed air source 8 via a pressure line 7. Behind the compressed air source 8, a pneumatic switch 9 is switched on in the pressure line 7 and subsequently a flow control device 10 behind it.
Der pneumatische Schalter 9. weist drei Schaustellungen I , 0 und I auf. In der dargestellten Schaltstellung I läßt der Schalter die Druckluft von der Druckluftquelle 8 zur Durchflußsteuereinrichtung ungehindert durchströmen. Wird der Schalter in die Schal-Stellung 0 gebracht, so ist dieses Durchströmen verhindert, ebenso wie ein Rückströmen von Luft über die Druckleitung 7. In dieser Schaltstellung wird z.B. eine angehobene Last in der erreichten Stellung gehalten. In Schaltstellung II schließlich ist die Druckluftzufuhr von der Druckluftquelle 8 abgeschlossen, während der Rückfluß der Luft vom Druckraum 3 zur Entlüftungseinrichtung 11 geöffnet Ist.
Wenn die Druckluft nach Verlassen des Schalters 9 weiterstromt, erreicht sie die Durchflußstβuereinrichtung 10, wo die Druckiuftleitung verzweigt ist und zu zwei parallel zueinander geschalteten verstellbaren Drosselventilen D1 und D2 gelangt, denen je ein Rückschlagvenbtil Rl und R2 in Serie nachgeschaltet ist. Anschlies- send vereinigt sich die Druckluftleitung wieder und gelangt so zum Druckraum 3 des Hubantriebs 1The pneumatic switch 9 . has three show positions I, 0 and I. In the switching position I shown, the switch allows the compressed air to flow freely from the compressed air source 8 to the flow control device. If the switch is switched to the switch position 0, this flow is prevented, as is a backflow of air via the pressure line 7. In this switch position, for example, a raised load is held in the position reached. Finally, in switch position II, the compressed air supply from the compressed air source 8 is completed, while the reflux of the air from the pressure chamber 3 to the ventilation device 11 is open. If the compressed air continues to flow after leaving the switch 9, it reaches the flow control device 10, where the compressed air line is branched and reaches two adjustable throttle valves D1 and D2 connected in parallel, each of which has a check valve R1 and R2 connected in series. The compressed air line then unites again and thus reaches the pressure chamber 3 of the linear actuator 1
Strömt in der dargestellten Stellung des pneumatischen Schalters 9 die von der Druckluftquelle 8 kommende Druckluft zu der Durchflußsteuereinrichtung 10, so kann sie dort durch das verstellbare Drosselventil D1 und das Rückschlagventil R1 , welches dann öffnet, zum Druckraum 3 strömen, während der zweite Stromungsweg über das Drosselventil D2 durch das Rückschlagventil R2 abgeschlossen ist. Das Drosselventil D1 wird durch die auf den Kranhaken 6 wirkende Kraft F derart verstellt, daß der Drosselquerschnitt bei geringer Last F verringert, bei ansteigender Last F |edoch vergrößert wird. Dadurch wird erreicht, daß die Hubgeschwindigkeit unabhängig von der Große der Last wenigstens annähernd gleich ist.If, in the position shown of the pneumatic switch 9, the compressed air coming from the compressed air source 8 flows to the flow control device 10, it can flow there through the adjustable throttle valve D1 and the check valve R1, which then opens, to the pressure chamber 3, while the second flow path is via the Throttle valve D2 is completed by the check valve R2. The throttle valve D1 is adjusted by the force F acting on the crane hook 6 in such a way that the throttle cross section is reduced when the load F is low, but increased when the load F rises. This ensures that the lifting speed is at least approximately the same regardless of the size of the load.
Soll die am Kranhaken 6 wirkende Last abgesenkt werden, so muß der pneumatische Schalter 9 in die Schaltstβllung ü gebracht werden. Dadurch wird die Druckleitung 7 mit der Entlüftungseinrichtung 1 1 verbunden. Die beim Absinken des Kolbens 2 aus dem Druckraum 3 austretende Luft strömt dabei über die Druckleitung 7 zu der Durchflußsteuereinrichtung 10, wo sie nun das Ruckschlagventil R2 öffnet und anschließend das verstellbare Drosselventil D2 durchströmt Dabei wird das Drosselventil in Abhängigkeit von der am Kranhaken 6 wirkenden Kraft F so verstellt, daß es bei ansteigender Kraft F den Drosselquerschnitt verkleinert und damit ein abruptes Absinken der Last verhindert.If the load acting on the crane hook 6 is to be lowered, the pneumatic switch 9 must be brought into the switching position ü. Characterized the pressure line 7 is connected to the venting device 1 1. The air emerging from the pressure chamber 3 when the piston 2 sinks flows via the pressure line 7 to the flow control device 10, where it now opens the non-return valve R2 and then flows through the adjustable throttle valve D2. The throttle valve becomes a function of the force acting on the crane hook 6 F is adjusted so that it decreases the throttle cross-section with increasing force F and thus prevents an abrupt drop in the load.
Bei der in Fig. 2 dargestellten Variante eines Hebegeräts ist auf einer Standsäule 12 ein Parallβlogrammausleger 13 und eine Konsole 14 schwenkbar gelagert. Auf der Konsole 14 stützt sich ein pneumatischer Hubantrieb 1 unter Zwischenschaltung einer Durchflußsteuereinrichtung 10 ab und greift mit der Kolbenstange 4 an dem Parallelogrammausleger 13 an, wodurch der letztere gehoben und gesenkt
werden kann. An dem Parallelogrammausleger 13 ist ein Lastarm 15 schwenkbar gelagert, der an seinem Ende einen Kranhaken 6 trägt. Oberhalb des Kranhakens 6 Ist ein pneumatischer Schalter 9 angeordnet, der über eine Druckleitung 7 einerseits mit einer Druckluftquelle 8 und andrerseits mit der Durchflußstβuer- elnrichtung 10 verbunden ist, welche Ihrerseits über eine Druckleitung 7 mit dem Druckraum des Hubantriebs 1 in Verbindung steht. Der Wirkungsablauf ist hier der gleiche, wie oben bei Fig. 1 beschrieben.In the variant of a lifting device shown in FIG. 2, a parallel log arm 13 and a bracket 14 are pivotably mounted on a standing column 12. A pneumatic lifting drive 1 is supported on the console 14 with the interposition of a flow control device 10 and engages with the piston rod 4 on the parallelogram boom 13, as a result of which the latter is raised and lowered can be. A load arm 15 is pivotally mounted on the parallelogram boom 13 and carries a crane hook 6 at its end. Above the crane hook 6 there is a pneumatic switch 9, which is connected via a pressure line 7 on the one hand to a compressed air source 8 and on the other hand to the flow control device 10, which in turn is connected to the pressure chamber of the linear actuator 1 via a pressure line 7. The course of action here is the same as described above in FIG. 1.
In Fig. 3 ist ein verstellbares Drosselventil dargestellt, welches aus einem Gehäuse 16 besteht, dessen Innenraum 17 eine Zuluftöffnung 18 und eine Abluftöffnung 19 aufweist. Zwischen diesen Öffnungen ist im Innenraum 17 eine Zwischenwand 20 angeordnet, die eine Drosselbohrung 21 aufweist. In diese taucht eine kegelige Drossβlnadel 22 ein, die mit einem längsverschieblich Im Gehäuse 16 gelagerten zylindrischen Führungstell 23 verbunden ist, welches seinerseits einen axial aus dem Gehäuse 16 herausragendeπ Betätigungsstift 24 aufweist. Gegen' die Drosselnadel liegt von unten eine Druckplatte 25 an, die unter Einwirkung einer Feder 26 steht, welche die Drosselnadel in eine obere Endstθllung drückt.3 shows an adjustable throttle valve which consists of a housing 16, the interior 17 of which has an inlet air opening 18 and an outlet air opening 19. An intermediate wall 20, which has a throttle bore 21, is arranged in the interior 17 between these openings. A conical throttling needle 22 plunges into this, which is connected to a longitudinally displaceable cylindrical guide point 23 which is mounted in the housing 16 and which in turn has an actuating pin 24 projecting axially from the housing 16. Against 'the throttle needle is from the bottom to a pressure plate 25, which is under the action of a spring 26, which presses the throttle needle in an upper Endstθllung.
Wenn dieses Drosselventil so in eine Durchflußsteuereinrichtung installiert wird, daß bei ansteigender Last der Betätigungsstift 24 in das Gehäuse 16 hineingedrückt wird, so wird dadurch der Drosselquerschnitt zunehmend verringert.If this throttle valve is installed in a flow control device in such a way that the actuating pin 24 is pressed into the housing 16 as the load increases, the throttle cross section is thereby increasingly reduced.
Die in Fig. 4 dargestellte Variante eines Drosselventils unterscheidet, sich von der nach Fig. 3 lediglich dadurch, daß die Drosselnadel 22 in entgegengesetzter Richtung kegelig ausgeführt ist, sodaß in diesem Falle beim Hineindrücken des Betätigungsstiftes 24 in das Gehäuse 16 der Drosselquerschnitt vergrößert wird.The variant of a throttle valve shown in FIG. 4 differs from that of FIG. 3 only in that the throttle needle 22 is conical in the opposite direction, so that in this case the throttle cross section is enlarged when the actuating pin 24 is pushed into the housing 16.
Die Fig. 5 schließlich zeigt eine Ausführung eines doppeltwirkenden Drosselventils. Bei diesem mündet in den Iπnenraum 17 des Gehäuses 16 eine Zuluftbohrung 18. Es sind iη axialem Abstand voneinander zwei Abluftöffnungen 19 und 27 vorgesehen. Zwischen der Zuluftöffnung 18 und jeder der Abluftöffnungen 19 und 27 ist im Innenraum 17 je eine Zwischenwand 20 vorgesehen, die je eine
Drosselbohrung 21 aufweisen. In jede dieser Drosselbohrungen taucht eine kegelige Drosselnadel 22 ein, die miteinander verbunden und gegensinnig kegelig ausgeführt sind. Wird in diesem Fall der Betätigungsstift nach unten gedrückt, so wird gleichzeitig der Drosselquerschnitt zwischen der Zuluftöffnung 18 und der Abluftöffnung 19 zunehmend verringert, während gleichzeitig der Drosselquer- εchnitt zwischen der Zuluftbohrung 18 und der Abluftbohrung 27 vergrößert wird. Damit ersetzt dieses Drosselventil die beiden in Fig. 1 dargestellten Drosselventile D1 und D2.5 shows an embodiment of a double-acting throttle valve. In the latter, an inlet air bore 18 opens into the interior 17 of the housing 16. Two exhaust air openings 19 and 27 are provided at an axial distance from one another. Between the supply air opening 18 and each of the exhaust air openings 19 and 27, an intermediate wall 20 is provided in the interior 17, each one Have throttle bore 21. In each of these throttle bores, a conical throttle needle 22 is immersed, which is connected to one another and is conical in opposite directions. If the actuating pin is pressed down in this case, the throttle cross section between the supply air opening 18 and the exhaust air opening 19 is simultaneously increasingly reduced, while at the same time the throttle cross section between the supply air bore 18 and the exhaust air bore 27 is increased. This throttle valve thus replaces the two throttle valves D1 and D2 shown in FIG. 1.
In Fig. 6 ist ein topfförmlges Außengehäuse 28 dargestellt, in dem ein umgekehrt topf örmiger Hohlkolben 29 längsverschlβblich gelagert ist, Das Außengehäuse 28 ist an seinem offenen Ende durch einen eingesetzten Deckel 30 verschlossen, durch den ein Zugbolzen 31 hindurchragt, der mittels einer Schraube mit dem Boden des Hohlkαlbens 29 verbunden ist. Zwischen dem Boden des Hohlkolbens 29 einerseits und dem Deckel 30 andrerseits ist ein Tellerfederpaket 32 angeordnet, welches den Hohlkolben 29 im Außengehäuse 28 .nach unten drückt. In dem von dem Außengehäuse 28 und dem Hohlkolben 29 eingeschlossenen Hohlraum sind zwei verstellbare Drosselventile 33 uind 34 eingesetzt, die sich einerseits am geschlossenen Boden des Außengehäuses und andrerseits am geschlossenen Boden des Hohlkolbens mit Ihren Betätigungsstiften 24 abstützen. Bei den Drosselventilen 33 und 34 handelt es sich im einen Fall um ein Drosselventil entsprechend Fig. 3 und im andern Fall um eines entsprechend Fig. 4. Wird dieses Bauteil z.B. in das Seil 5 entsprechend Flg. 1 eingebaut, so greifen die Seilkräfte einerseits am Zugbolzen 31 und andrerseits am Boden des Außengehäuses 28 an, wobei mit steigender Last der Hohlkolben 29 gegen die Wirkung des Federpaketes 32 nach oben verschoben wird, wodurch die Betätigungsstifte 24 weiter aus den Gehäusen der Drosselventile 33 und 34 heraustreten und damit im Innern die Drosselquerschnitte verändert werden.6 shows a pot-shaped outer housing 28, in which an inverted cup-shaped hollow piston 29 is mounted so as to be longitudinally lockable. The outer housing 28 is closed at its open end by an inserted cover 30, through which a tension bolt 31 projects, which also projects by means of a screw the bottom of the hollow piston 29 is connected. Arranged between the bottom of the hollow piston 29 on the one hand and the cover 30 on the other hand is a plate spring assembly 32 which presses the hollow piston 29 downward in the outer housing 28. In the cavity enclosed by the outer housing 28 and the hollow piston 29, two adjustable throttle valves 33 and 34 are used, which are supported on the one hand on the closed bottom of the outer housing and on the other hand on the closed bottom of the hollow piston with their actuating pins 24. The throttle valves 33 and 34 are in one case a throttle valve according to FIG. 3 and in the other case one according to FIG. 4. If this component is used e.g. in the rope 5 according to Flg. 1 installed, the rope forces act on the one hand on the tension bolt 31 and on the other hand on the bottom of the outer housing 28, the hollow piston 29 being moved upward against the action of the spring assembly 32 with increasing load, as a result of which the actuating pins 24 continue to move out of the housings of the throttle valves 33 and 34 emerge and thus the throttle cross sections are changed inside.
In Fig. 7 ist eine umgekehrte Variante dargestellt. Auch hier Ist ein Außengehäuse 35 vorgesehen, in dem ein Hohlkolben 36 längsverschieblich gelagert und durch einen Sprengring 37 am Heraustreten nach unten hin gesichert ist. Zwischen dem Boden des Außengehäuses 35 und der Stirnfläche des Hohlkolbens 36 wirkt ein
Tellerfederpaket 38, in dessen Zentrum ein Stützte!! 39 vorgesehen ist, gegen welches sich der Betätigungsstift 24 eines Drosselventils 40 abstützt, bei dem es sich um ein doppeltwirkendes Drosselventil entsprechend Fig. 5 handelt. In diesem Fall kann dieses Bauteil, welches durch die von dem Hebegerät zu bewegende Last auf Druck beansprucht wird, z.B. in einer Ausführung gemäß Fig. 2 eingesetzt werden.A reverse variant is shown in FIG. 7. Here too, an outer housing 35 is provided, in which a hollow piston 36 is mounted so as to be longitudinally displaceable and secured by a snap ring 37 so that it can emerge downwards. An action acts between the bottom of the outer housing 35 and the end face of the hollow piston 36 Disc spring package 38, in the center of which a support !! 39 is provided, against which the actuating pin 24 of a throttle valve 40 is supported, which is a double-acting throttle valve according to FIG. 5. In this case, this component, which is stressed by the load to be moved by the lifting device, can be used, for example, in an embodiment according to FIG. 2.
Fig. 8 schließlich zeigt eine relativ einfache Variante, bei welcher ein doppeltwirkendes Drosselventil 40 in einen Metallring 41 eingesetzt ist, der sich bei Einwirkung von Zug- oder Druckkräften an Stellen, die in Längsrichtung des Drosselventils liegen, derart verformt daß der Betätigungsstift 24 im einen Fall in das Drosselventil hineingedrückt wird,- oder im anderen Fall weiter aus diesem austreten kann.
Fig. 8 finally shows a relatively simple variant, in which a double-acting throttle valve 40 is inserted into a metal ring 41, which deforms in the longitudinal direction of the throttle valve under the action of tensile or compressive forces, so that the actuating pin 24 in one Fall is pushed into the throttle valve, - or can continue to emerge from it in the other case.
BezugszeichenlisteReference list
1 Hubabtrieb 22 Drosselnadel1 linear actuator 22 throttle needle
2 Kolben 23 Führungsteil2 pistons 23 guide part
3 Druckraum 24 Betätigungsstift3 pressure chamber 24 actuating pin
4 Kolbenstange 25 Druckplatte4 piston rod 25 pressure plate
5 Seil 26 Feder5 rope 26 spring
6 Kranhaken 27 Abluftöffnung6 crane hooks 27 exhaust opening
7 Druckleitung 28 Außengehäuse7 pressure line 28 outer housing
8 Druckluftquelle 29 Hohlkolben8 compressed air source 29 hollow piston
9 pneumatischer Schalter 30 Deckel9 pneumatic switch 30 cover
10 Druckluftsteuereinrichtung 31 Zugbolzen10 Compressed air control device 31 Draw stud
11 Entlüftungsθinrlchtung 32 Tellerfederpaket11 Venting device 32 Belleville spring assembly
12 Standsäule 33 Drosselventil12 pillar 33 throttle valve
13 Parallelogrammausleger 34 Drosselventil13 parallelogram boom 34 throttle valve
14 Konsole 35 Außengehäuse14 console 35 outer housing
15 Lastarm 36 Hohlkolben15 load arm 36 hollow piston
16 Gehäuse 37 Sprengring16 housing 37 snap ring
17 Innenraum 38 Tellerfederpaket17 Interior 38 Disc spring package
18 Zuluftöffnung 39 Stützteil18 Inlet air opening 39 Support part
19 Abluftöffnung 40 Drosselventil19 Exhaust air opening 40 Throttle valve
20 Zwischenwand 41 Metallring20 partition 41 metal ring
21 Drosselbohrung21 throttle bore
Dl verstellbares Drosselventil R1 Rückschlagventil D2 verstellbares Drosselventil R2 Rückschlagventil
Dl adjustable throttle valve R1 check valve D2 adjustable throttle valve R2 check valve
Claims
1. Handgesteuertes Hebegerät mit einem pneumatischen Hubantrieb (1 ), einem mit diesem verbundenen Huborgan (5, 13), einem am Ende des Huborgans angeordneten Lastaufnahmemittel (6) und einem pneumatischen Schalter (9), der in eine eine Druckluftquelle (8) mit einem Druckraum (3) des Hubantriθbs (1 ) verbindende Druckleitung (7) Integriert ist und der den Druckraum (3) des Hubantriθbs (1 ) in einer Stellung ( I ) mit der Druckluftquelle (8) und in einer anderen Stellung ( II ) mit einer Entlüftungseinrichtung (11 ) verbindet, dadurch gekennzeichnet, daß zwischen zwei lastübertragende Bauteile (5-5; 13-14) eine im Lastfluß liegende Durchflußsteuerelπrichtung (10) integriert ist, die gleichzeitig zwischen dem pneumatischen Schalter (9) und dem Druckraum (3) des Hubantriebs (1 ) in die Druckluftleitung (7) eingeschaltet ist, und die unter Einwirkung der am Lastaufnahmemittel (6) angreifenden Last den Durchflußquerschnitt der Druckluftleitung (7) selbsttätig so variiert, daß sich a) bei einem Hubvorgang bei hoher Last ein größerer Durchflußquerschnitt einstellt, als bei geringer Last und b) bei einem Absenkvorgang bei hoher Last ein kleinerer Durchflußquerschnitt einstellt, als bei geringer Last.
1.Hand-controlled lifting device with a pneumatic lifting drive (1), a lifting element (5, 13) connected to it, a load-carrying means (6) arranged at the end of the lifting element and a pneumatic switch (9) which is connected to a compressed air source (8) a pressure chamber (3) of the stroke drive (1) connecting pressure line (7) is integrated and the pressure chamber (3) of the stroke drive (1) in one position (I) with the compressed air source (8) and in another position (II) A venting device (11) connects, characterized in that a flow control device (10) lying in the load flow is integrated between two load-transmitting components (5-5; 13-14), which simultaneously between the pneumatic switch (9) and the pressure chamber (3) of the linear actuator (1) is switched on in the compressed air line (7), and the flow cross section of the compressed air line (7) automatically varies under the action of the load acting on the load-carrying means (6) so that sic h a) sets a larger flow cross-section during a lifting process with a high load than with a low load and b) sets a smaller flow cross-section with a lowering process under a high load than with a low load.
2. Hebegerät nach Anspruch 1 , dadurch gekennzeichnet, daß die Durchfluß- steuereinrichtung (10) a) zwei zueinander parallel geschaltete verstellbare Drosselventile (D1 , D2) enthält, zu denen b) je ein Rückschlagventil (Ri , R2) in Serie geschaltet ist, und wobei c) dem einen in Fließrichtung vom pneumatischen Schalter (9) zum Druckraum (3) öffnenden Rückschlagventil (R1 ) ein Drosselventil (D1 ) zugeordnet ist, welches bei ansteigender Last den Drosselqusrschnitt vergrößert und d) dem in entgegengesetzter Fließrichtung öffnenden Rückschlagventil (R2) ein Drosselventil (D2) zugeordnet ist, welches bei ansteigender Last den Drosselquer- schnitt verkleinert.2. Lifting device according to claim 1, characterized in that the flow control device (10) a) contains two mutually parallel adjustable throttle valves (D1, D2), to which b) a check valve (Ri, R2) is connected in series, and wherein c) the one check valve (R1) opening in the flow direction from the pneumatic switch (9) to the pressure chamber (3) is assigned a throttle valve (D1), which increases the throttle cross section when the load increases, and d) the check valve (R2 opening in the opposite flow direction) ) a throttle valve (D2) is assigned, which reduces the throttle cross-section when the load increases.
3. Hθbegerät nach Anspruch 2, dadurch gekennzeichnet, daß die Drosselventile (Dl , D2) derart weggesteuert sind, .daß sich bei Änderung ihrer axialen Länge eine entsprechende Änderung der Drosselwirkung ergibt.3. Hθbgerät according to claim 2, characterized in that the throttle valves (Dl, D2) are controlled in such a way. That there is a corresponding change in the throttle effect when changing their axial length.
4. Hebegerät nach Anspruch 2 oder 3, dadurch gekennzeichnet, daß die beiden Drosselventile (D1, D2) zu einer Baueinheit zusammengefaßt sind.4. Lifting device according to claim 2 or 3, characterized in that the two throttle valves (D1, D2) are combined to form a structural unit.
5. Hθbegerät nach Anspruch 2 oder 3, dadurch gekennzeichnet, daß die beiden Drosselventile (D1 , D2) und die beiden Rückschlagventile (R1 , R2) zu einer gemeinsamen Baueinheit zusammengefaßt sind.5. Hθbgerät according to claim 2 or 3, characterized in that the two throttle valves (D1, D2) and the two check valves (R1, R2) are combined to form a common structural unit.
6. Hebegerät nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Drosselventile ( Dl , D2) in einem Außengehäuse (28, 35) untergebracht sind, in dem sie mit ihren beiden axialen Enden gegen die Innenflächen zweier einander gegenüberliegender Wände des Außengehäuses (28, 35 ), deren gegenseitiger Abstand unter elastischer Verformung veränderbar ist, anliegen, an deren Außenflächen Zug- oder Druckkräfte aus lastübertragenden Bauteilen (5-5; 13-14) angreifen.
6. Lifting device according to one of the preceding claims, characterized in that the throttle valves (Dl, D2) are housed in an outer housing (28, 35) in which they with their two axial ends against the inner surfaces of two opposite walls of the outer housing (28 , 35), the mutual distance of which can be changed under elastic deformation, rest on the outer surfaces of which tensile or compressive forces from load-transmitting components (5-5; 13-14) act.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE29802606U DE29802606U1 (en) | 1998-02-16 | 1998-02-16 | Hand-operated lifting device with a pneumatic lifting drive |
| DE29802606U | 1998-02-16 | ||
| PCT/DE1999/000472 WO1999041185A2 (en) | 1998-02-16 | 1999-02-16 | Manually controlled lifting device with a pneumatic lift drive mechanism |
Publications (3)
| Publication Number | Publication Date |
|---|---|
| EP1071633A2 true EP1071633A2 (en) | 2001-01-31 |
| EP1071633B1 EP1071633B1 (en) | 2002-09-25 |
| EP1071633A3 EP1071633A3 (en) | 2002-12-11 |
Family
ID=8052714
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP99913081A Expired - Lifetime EP1071633B1 (en) | 1998-02-16 | 1999-02-16 | Manually controlled lifting device with a pneumatic lift drive mechanism |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US6389950B1 (en) |
| EP (1) | EP1071633B1 (en) |
| DE (2) | DE29802606U1 (en) |
| ES (1) | ES2180288T3 (en) |
| WO (1) | WO1999041185A2 (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19955750B4 (en) * | 1999-11-11 | 2004-05-27 | Demag Mobile Cranes Gmbh | Process for pressure compensation in hydraulic motors for driving the lifting and closing cables of a cable crane |
| DE10123157C1 (en) | 2001-04-27 | 2002-11-14 | Demag Cranes & Components Gmbh | pneumatic valve |
| JP6532181B2 (en) * | 2016-02-26 | 2019-06-19 | 三菱重工コンプレッサ株式会社 | Valve system and steam turbine |
| US20190136876A1 (en) * | 2017-06-10 | 2019-05-09 | Shahin Fallahi | Electro-hydraulic or electro-pneumatic servo-actuator using khayyam triangle |
| DE102019133183A1 (en) * | 2019-12-05 | 2021-06-10 | RWE Nuclear GmbH | Load-bearing device and corresponding method |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3894476A (en) * | 1974-04-05 | 1975-07-15 | Us Energy | Self-adjusting load balancing pneumatic hoist |
| JPS62201797A (en) * | 1986-02-28 | 1987-09-05 | 有限会社日立重機製造 | Fluid controller |
| FR2615500B1 (en) * | 1987-05-20 | 1989-07-28 | Reel Sa | LOAD COMPENSATOR DEVICE FOR A HANDLING MACHINE AND METHOD FOR IMPLEMENTING SUCH COMPENSATION |
| US5644966A (en) * | 1995-07-05 | 1997-07-08 | Hirotaka Engineering Co., Ltd. | Pressure regulating circuit |
| JP3794743B2 (en) * | 1995-12-27 | 2006-07-12 | アイコクアルファ株式会社 | Material handling machine by force control method |
| JPH1030609A (en) * | 1996-04-19 | 1998-02-03 | Hirotaka Eng:Kk | Pressure adjusting circuit |
| US5816132A (en) * | 1996-07-12 | 1998-10-06 | Ross Operating Valve Company | Load-sensing pneumatic control system |
-
1998
- 1998-02-16 DE DE29802606U patent/DE29802606U1/en not_active Expired - Lifetime
-
1999
- 1999-02-16 ES ES99913081T patent/ES2180288T3/en not_active Expired - Lifetime
- 1999-02-16 EP EP99913081A patent/EP1071633B1/en not_active Expired - Lifetime
- 1999-02-16 DE DE59902847T patent/DE59902847D1/en not_active Expired - Fee Related
- 1999-02-16 WO PCT/DE1999/000472 patent/WO1999041185A2/en active IP Right Grant
-
2000
- 2000-08-16 US US09/640,247 patent/US6389950B1/en not_active Expired - Fee Related
Non-Patent Citations (1)
| Title |
|---|
| See references of WO9941185A2 * |
Also Published As
| Publication number | Publication date |
|---|---|
| DE59902847D1 (en) | 2002-10-31 |
| US6389950B1 (en) | 2002-05-21 |
| EP1071633B1 (en) | 2002-09-25 |
| ES2180288T3 (en) | 2003-02-01 |
| DE29802606U1 (en) | 1998-04-23 |
| WO1999041185A3 (en) | 2002-10-24 |
| WO1999041185A2 (en) | 1999-08-19 |
| EP1071633A3 (en) | 2002-12-11 |
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