WO2001053710A1 - Ball-and-socket joint - Google Patents
Ball-and-socket joint Download PDFInfo
- Publication number
- WO2001053710A1 WO2001053710A1 PCT/EP2000/013168 EP0013168W WO0153710A1 WO 2001053710 A1 WO2001053710 A1 WO 2001053710A1 EP 0013168 W EP0013168 W EP 0013168W WO 0153710 A1 WO0153710 A1 WO 0153710A1
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- Prior art keywords
- ball joint
- joint according
- leg
- spherical
- dome
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- 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
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C11/00—Pivots; Pivotal connections
- F16C11/04—Pivotal connections
- F16C11/06—Ball-joints; Other joints having more than one degree of angular freedom, i.e. universal joints
- F16C11/0619—Ball-joints; Other joints having more than one degree of angular freedom, i.e. universal joints the female part comprising a blind socket receiving the male part
- F16C11/0623—Construction or details of the socket member
- F16C11/0647—Special features relating to adjustment for wear or play; Wear indicators
Definitions
- the invention relates to a self-adjusting ball joint with a ball-bearing ball element which is pivotally received in an associated calotte, the calotte being composed of a first and a second calotte element which can be displaced relative to one another by means of a force-actuated adjusting device for wear compensation ,
- Such a ball joint used as a steering bearing in motor vehicle construction is previously known from US 3,250,555.
- a ball element carrying a bolt is accommodated in a housing.
- This housing contains two spherical dome elements which are arranged one above the other and which serve as sliding partners, the lower dome element being able to be displaced against the upper one when wear occurs, ie the dome elements approach each other. This is done in such a way that the lower cap element is acted upon by an adjusting screw.
- This screw is received via its external thread by an internal thread of a receiving opening of an additional component, which is also housed in the housing.
- the adjusting screw is connected to a spring element which generates a torque acting on it.
- the adjusting screw accommodated in the receiving opening of the additional component moves upwards due to the torque acting on it and thereby displaces the lower spherical cap element. towards the top so that there is no play between the partners involved in the articulation.
- the object of the invention is therefore to improve an articulated connection of the generic type while avoiding the previous disadvantages so that it has a simpler construction and has the same rigidity in all load directions.
- this object is achieved according to the characterizing part of claim 1 in that the spherical elements are positively connected via a threaded connection, but can be moved in a rotating and thus axial direction, with a permanently acting torque being applied to the threaded connection.
- the sliding partners themselves ie the dome elements
- the adjustment function to compensate for wear.
- the threaded connection of the calotte elements which is considerably larger in circumference than the adjusting screw, means that a multiple of force can also be transmitted without the partners involved being affected. This results in a rigid system in all spatial load directions, whose power transmission cannot be negatively influenced by the adjustment mechanism.
- the bearing play compensation mechanism is decoupled from the operating force of the operating forces. This enables the bearing preloads to be dimensioned in a manner that makes sense from an application point of view, regardless of the level of the operating forces. Preloads that were otherwise necessary for safety reasons and the resulting losses in efficiency are therefore eliminated.
- the torque is generated by spring force, gas or liquid pressure.
- the first dome element has an external thread with which it engages in an internal thread of the second dome element.
- the two dome elements are to be connected to one another via a spiral spring.
- the first dome element is to be L-shaped, a first leg having a recess in which the spiral spring is arranged and a second leg carrying the external thread, on the opposite side of which the dome-shaped recess is arranged is.
- the second dome element is L-shaped, a first leg carrying the internal thread and a second leg forming the dome-shaped recess.
- the spiral spring is connected to the second spherical element via an intermediate part which has a central part, the flanges of which are bent at both ends in the opposite direction, the first leg of the first spherical element and the second leg of the Cover the dome element.
- the intermediate part and the second spherical element are connected to one another via fastening screws or other connecting elements. It is apparent from claim 9 that both dome elements should be provided with a friction-reducing sliding coating.
- the ball joint is used in machine tools of the HEXAPOD system.
- these new generation machine tools move smaller masses.
- the consequence of this is that higher positioning speeds can be achieved, in particular the rigidity between the frame and the tool holder must be very high.
- Such a machine tool can consist of several arms which are articulated on the one hand on a frame and on the other hand on a tool holder.
- the ball joint according to the invention can be used advantageously. Compared to the roller-bearing joints used in this context, it is advantageous that ball bearings based on plain bearings have the same functionality and lower costs.
- bearings based on roller bearings used in such articulation points have the disadvantage that vibrations and pulsating loads in the operating state of the machine tool have a more negative effect on roller bearings than on plain bearings.
- FIG. 1 shows a perspective half-section of a ball joint according to the invention
- FIG. 2 is a schematic representation of a machine tool according to the HEXAPOD system. Detailed description of the drawings
- the articulated connection according to FIG. 1 consists of the ball element 2 which carries the bolt 1 and is received in a spherical cap (not shown) so that it can pivot about the axes X, Y, Z.
- This spherical cap is formed from the first spherical cap element 3 and the second spherical cap element 4, both of which are provided with a spherically designed sliding lining 5 in order to reduce friction.
- the first dome element 3 is L-shaped in section along the axis Z and has the first leg 6 and the second leg
- the second leg 7 is on its outer surface with the external thread
- the second dome element 4 is also L-shaped, the first leg 10 carrying the internal thread 9 and the second leg 11 carrying the sliding lining 5.
- the first leg 6 of the spherical element 3 is provided with the circumferential recess 12 in which the spiral spring 13 is accommodated. This is connected at one end via the pin 14 to the first dome element 3 and at the other end to the second dome element 4. This connection of the spiral spring 13 to the second spherical element 4 takes place via the intermediate part 16, the central part 17 of which ends at the upper and lower ends in two flanges 18 and 19 which are angled in the opposite direction.
- the lower flange 18 is connected to the second end of the spiral spring 13 via the pin 15, so that its torque can be transmitted to the second calotte element 4 via the intermediate part 16 and the fastening screws 20.
- the first leg 6 of the dome element 3 and the flange 18 of the intermediate part 16 each have a projection 22 and 21, the projection 21 projecting the projection 22 in the radial direction embraces.
- the second dome element 4 is rotated relatively clockwise relative to the first dome element 3 until the material contact of the two sliding elements coverings is restored with the bias corresponding to the coil spring 13.
- This process runs automatically and is always triggered when a load change occurs when wear occurs, ie the threaded connection is without load.
- the spiral spring 13 is designed in such a way that adjustment paths are achieved which correspond to the total lifetime wear of the bearing arrangement.
- the adjustment mechanism designed according to the invention works in a self-locking manner and in this way transmits the operating forces in any adjustment with great rigidity in the pulling direction (Z-axis), without the working memory (coil spring 13) being forcefully touched for the adjustment thereof.
- the machine tool 23 of the new HEXAPOD generation shown in FIG. 2 is provided with a plurality of telescopic arms 26 formed from nested tubes 24, 25. These telescopic arms 26 are articulated on the one hand on the frame 27 and on the other hand on the tool holder 28.
- the tool holder 28 is provided with a tool, not shown, which is driven by the motor 29.
- the tool holder 28 can be moved in any desired position in space by retracting or extending one or more telescopic arms 26.
- the joints designed according to the invention can be used in the illustrated machine tool 23 in an advantageous manner both on the frame 27 and on the tool holder 28.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Pivots And Pivotal Connections (AREA)
Abstract
Description
Kugelgelenk ball joint
Anwendungsgebiet der ErfindungField of application of the invention
Die Erfindung betrifft ein sich selbst nachstellendes Kugelgelenk mit einem einen Bolzen tragenden Kugelelement, das schwenkbar in einer zugeordneten Kalotte aufgenommen ist, wobei die Kalotte aus einem ersten und einem zweiten Kalottenelement zusammengesetzt ist, die zum Verschleißausgleich über eine mit einer Kraft beaufschlagten Nachstelleinrichtung gegeneinander verschiebbar sind.The invention relates to a self-adjusting ball joint with a ball-bearing ball element which is pivotally received in an associated calotte, the calotte being composed of a first and a second calotte element which can be displaced relative to one another by means of a force-actuated adjusting device for wear compensation ,
Hintergrund der ErfindungBackground of the Invention
Ein derartiges als Lenkungslager im Kraftfahrzeugbau eingesetztes Kugelgelenk ist aus der US 3,250,555 vorbekannt. Ein einen Bolzen tragendes Kugelelement ist in einem Gehäuse aufgenommen. Dieses Gehäuse enthält zwei sphärisch ausgebildete übereinander angeordnete Kalottenelemente, die als Gleitpartner dienen, wobei das untere Kalottenelement gegen das obere bei eintretendem Verschleiß verschoben werden kann, d. h. die Kalottenelemente nähern sich einander an. Dies erfolgt derart, dass das untere Kalottenelement von einer Nachstellschraube beaufschlagt ist. Diese Schraube ist über ihr Au- ßengewinde von einem Innengewinde einer Aufnahmeöffnung eines zusätzlichen Bauteiles aufgenommen, das ebenfalls im Gehäuse untergebracht ist. Am vom unteren Kalottenelement abgewandten Ende ist die Nachstellschraube mit einem Federelement verbunden, das ein auf diese wirkendes Drehmoment erzeugt. Tritt nun bei einem oder beiden Gleitpartnern Materialabtrag durch Verschleiß ein, so bewegt sich die in der Aufnahmeöffnung des zusätzlichen Bauteils untergebrachte Versteilschraube durch das auf sie einwirkende Drehmoment nach oben und verschiebt dabei das untere Kalottenelement ge- gen das obere, so dass Spielfreiheit zwischen den beteiligten Partnern der Gelenkverbindung hergestellt ist.Such a ball joint used as a steering bearing in motor vehicle construction is previously known from US 3,250,555. A ball element carrying a bolt is accommodated in a housing. This housing contains two spherical dome elements which are arranged one above the other and which serve as sliding partners, the lower dome element being able to be displaced against the upper one when wear occurs, ie the dome elements approach each other. This is done in such a way that the lower cap element is acted upon by an adjusting screw. This screw is received via its external thread by an internal thread of a receiving opening of an additional component, which is also housed in the housing. At the end facing away from the lower cap element, the adjusting screw is connected to a spring element which generates a torque acting on it. If material removal occurs due to wear on one or both sliding partners, the adjusting screw accommodated in the receiving opening of the additional component moves upwards due to the torque acting on it and thereby displaces the lower spherical cap element. towards the top so that there is no play between the partners involved in the articulation.
Nachteilig dabei ist, dass die Kraftaufnahme einer solchen Gelenkverbindung einerseits durch die Gewindetragfähigkeit der Verstel Ischraube und andererseits durch die Tragfähigkeit der Kontaktfläche zwischen der Stirnfläche der Versteilschraube und dem unteren Kalottenelement begrenzt ist. Es ist auch von Nachteil, dass das die Versteilschraube aufnehmende Bauteil zusätzlich zu fertigen und zu handhaben ist. Schließlich ist weiter von Nachteil, dass ein solches Kugelgelenk aufgrund seiner Bauweise in unterschiedlichen Richtungen unterschiedliche Steifigkeiten aufweist. Insbesondere bei Auftreten von relativ großen Kräften in Richtung Versteilschraube scheint eine solche Gelenkverbindung nicht allen Anforderungen gewachsen zu sein.The disadvantage here is that the force absorption of such a joint connection is limited on the one hand by the thread bearing capacity of the adjusting screw and on the other hand by the bearing capacity of the contact surface between the end face of the adjusting screw and the lower calotte element. It is also disadvantageous that the component receiving the adjusting screw must also be manufactured and handled. Finally, it is a further disadvantage that such a ball joint has different stiffnesses in different directions due to its design. Particularly when relatively large forces occur in the direction of the adjusting screw, such an articulated connection does not seem to be able to meet all requirements.
Zusammenfassung der ErfindungSummary of the invention
Aufgabe der Erfindung ist es daher, eine Gelenkverbindung der gattungsgemäßen Art unter Vermeidung der bisherigen Nachteile so zu verbessern, dass sie einfacher aufgebaut ist und in allen Belastungsrichtungen die gleiche Stei- figkeit aufweist.The object of the invention is therefore to improve an articulated connection of the generic type while avoiding the previous disadvantages so that it has a simpler construction and has the same rigidity in all load directions.
Erfindungsgemäß wird diese Aufgabe nach dem kennzeichnenden Teil von Anspruch 1 dadurch gelöst, dass die Kalottenelemente über einen Gewindeverbund formschlüssig, jedoch in rotativer und damit axialer Richtung beweg- lieh verbunden sind, wobei auf den Gewindeverbund ein dauerhaft wirkendes Drehmoment aufgebracht ist.According to the invention, this object is achieved according to the characterizing part of claim 1 in that the spherical elements are positively connected via a threaded connection, but can be moved in a rotating and thus axial direction, with a permanently acting torque being applied to the threaded connection.
Auf diese Weise sind die Gleitpartner selbst, d. h. die Kalottenelemente, direkt mit der Verstellfunktion zum Verschleißausgleich ausgestattet. Durch den im Vergleich zur Versteilschraube im Umfang wesentlich größeren Gewindeverbund der Kalottenelemente ist auch ein Vielfaches an Kraft übertragbar, ohne dass die beteiligten Partner in Mitleidenschaft gezogen werden. Dadurch bedingt ergibt sich in allen räumlichen Belastungsrichtungen ein steifes System, dessen Kraftübertragung nicht vom Nachstellmechanismus negativ beeinflussbar ist.In this way, the sliding partners themselves, ie the dome elements, are directly equipped with the adjustment function to compensate for wear. The threaded connection of the calotte elements, which is considerably larger in circumference than the adjusting screw, means that a multiple of force can also be transmitted without the partners involved being affected. This results in a rigid system in all spatial load directions, whose power transmission cannot be negatively influenced by the adjustment mechanism.
Der Lagerspielausgleichsmechanismus ist vom Kraftlauf der Betriebskräfte abgekoppelt. Dadurch ist man in der Lage, die Lagervorspannkräfte unabhängig von der Höhe der Betriebskräfte anwendungstechnisch sinnvoll zu dimensionieren. Vorspannungen, die sonst aus Sicherheitsgründen notwendig waren, und die daraus resultierenden Wirkungsgradverluste entfallen somit.The bearing play compensation mechanism is decoupled from the operating force of the operating forces. This enables the bearing preloads to be dimensioned in a manner that makes sense from an application point of view, regardless of the level of the operating forces. Preloads that were otherwise necessary for safety reasons and the resulting losses in efficiency are therefore eliminated.
Vorteilhafte Ausführungsformen der Erfindung sind in den Unteransprüchen 2 bis 10 beschrieben.Advantageous embodiments of the invention are described in subclaims 2 to 10.
So ist nach Anspruch 2 vorgesehen, dass das Drehmoment durch Federkraft, Gas oder Flüssigkeitsdruck erzeugt ist. Aus Anspruch 3 geht hervor, dass das erste Kalottenelement ein Außengewinde aufweist, mit dem es in ein Innengewinde des zweiten Kalottenelementes eingreift. Nach einem weiteren Merkmal der Erfindung gemäß Anspruch 4 sollen die beiden Kalottenelemente über eine Spiralfeder miteinander verbunden sein. Nach einem weiteren zusätzlichen Merkmal der Erfindung gemäß Anspruch 5 soll das erste Kalottenelement L-förmig ausgebildet sein, wobei ein erster Schenkel eine Ausnehmung aufweist, in der die Spiralfeder angeordnet ist und ein zweiter Schenkel das Außengewinde trägt, auf dessen abgewandter Seite die kalottenförmige Ausnehmung angeordnet ist. Aus Anspruch 6 geht hervor, dass das zweite Kalottenelement L-förmig ausgebildet ist, wobei ein erster Schenkel das Innenge- winde trägt und ein zweiter Schenkel die kalottenförmige Ausnehmung bildet. Nach einem weiteren Merkmal der Erfindung gemäß Anspruch 7 ist vorgesehen, dass die Spiralfeder mit dem zweiten Kalottenelement über ein Zwischenteil verbunden ist, das einen Mittelteil aufweist, dessen an beiden Enden in entgegengesetzter Richtung abgewinkelte Flansche den ersten Schenkel des ersten Kalottenelements und den zweiten Schenkel des Kalottenelements überdecken. In diesem Fall ist nach Anspruch 8 vorgesehen, daß Zwischenteil und zweites Kalottenelement über Befestigungsschrauben oder andere Verbindungselemente miteinander verbunden sind. Aus Anspruch 9 geht hervor, dass beide Kalottenelemente mit einem die Reibung vermindernden Gleitbelag versehen sein sollen. Schließlich ist nach einem letzten Merkmal der Erfindung gemäß Anspruch 10 vorgesehen, dass das Kugelgelenk in Werkzeugmaschinen des HEXAPOD-Systems eingesetzt ist. Diese Werkzeugmaschinen einer neueren Generation bewegen im Gegensatz zu konventionellen Werkzeugmaschinen geringere Massen. Dies hat zu Folge, dass höhere Stellgeschwindigkeiten gefahren werden können wobei insbesondere die Steifigkeit zwischen Rahmen und Werkzeugaufnahme sehr hoch sein muss. Eine solche Werkzeugmaschine kann aus mehreren Armen bestehen, die einerseits an einem Rahmen und andererseits an einer Werkzeugaufnahme gelenkig befestigt sind. Dabei kann das erfindungsgemäße Kugelgelenk in vorteilhafter weise eingesetzt werden. Gegenüber in diesem Zusammenhang auch eingesetzten wälzgelagerten Gelenken ist von Vorteil, dass bei Kugelgelenken auf Gleitlagerbasis bei gleicher Funktionalität geringere Kosten verursacht werden. Außerdem haben in derartigen Anlenkungspunkten eingesetzte Gelenke auf Wälzlagerbasis den Nachteil, dass sich Vibrationen und pulsierende Belastungen im Betriebszustand der Werkzeugmaschine eher negativ auf Wälzlager als auf Gleitlager auswirken.It is provided according to claim 2 that the torque is generated by spring force, gas or liquid pressure. It can be seen from claim 3 that the first dome element has an external thread with which it engages in an internal thread of the second dome element. According to a further feature of the invention according to claim 4, the two dome elements are to be connected to one another via a spiral spring. According to a further additional feature of the invention according to claim 5, the first dome element is to be L-shaped, a first leg having a recess in which the spiral spring is arranged and a second leg carrying the external thread, on the opposite side of which the dome-shaped recess is arranged is. It can be seen from claim 6 that the second dome element is L-shaped, a first leg carrying the internal thread and a second leg forming the dome-shaped recess. According to a further feature of the invention according to claim 7 it is provided that the spiral spring is connected to the second spherical element via an intermediate part which has a central part, the flanges of which are bent at both ends in the opposite direction, the first leg of the first spherical element and the second leg of the Cover the dome element. In this case it is provided according to claim 8 that the intermediate part and the second spherical element are connected to one another via fastening screws or other connecting elements. It is apparent from claim 9 that both dome elements should be provided with a friction-reducing sliding coating. Finally, according to a last feature of the invention, it is provided that the ball joint is used in machine tools of the HEXAPOD system. In contrast to conventional machine tools, these new generation machine tools move smaller masses. The consequence of this is that higher positioning speeds can be achieved, in particular the rigidity between the frame and the tool holder must be very high. Such a machine tool can consist of several arms which are articulated on the one hand on a frame and on the other hand on a tool holder. The ball joint according to the invention can be used advantageously. Compared to the roller-bearing joints used in this context, it is advantageous that ball bearings based on plain bearings have the same functionality and lower costs. In addition, bearings based on roller bearings used in such articulation points have the disadvantage that vibrations and pulsating loads in the operating state of the machine tool have a more negative effect on roller bearings than on plain bearings.
Die Erfindung wird an nachstehendem Ausführungsbeispiel näher erläutert.The invention is explained in more detail using the following exemplary embodiment.
Kurze Beschreibung der ZeichnungenBrief description of the drawings
Es zeigen:Show it:
Figur 1 einen perspektivischen Halbschnitt eines erfindungsgemäßen Kugelgelenks und1 shows a perspective half-section of a ball joint according to the invention and
Figur 2 eine schematische Darstellung einer Werkzeugmaschine nach dem HEXAPOD-System. Ausführliche Beschreibung der ZeichnungenFigure 2 is a schematic representation of a machine tool according to the HEXAPOD system. Detailed description of the drawings
Die Gelenkverbindung gemäß Figur 1 besteht aus dem den Bolzen 1 tragen- den Kugelelement 2, das um die Achsen X, Y, Z schwenkbar in einer nicht bezeichneten Kalotte aufgenommen ist. Diese Kalotte wird aus dem ersten Kalottenelement 3 und dem zweiten Kalottenelement 4 gebildet, wobei beide zur Reibungsverminderung mit je einem sphärisch ausgebildeten Gleitbelag 5 versehen sind. Das erste Kalottenelement 3 ist im Schnitt längs zur Achse Z L-förmig gestaltet und weist den ersten Schenkel 6 und den zweiten SchenkelThe articulated connection according to FIG. 1 consists of the ball element 2 which carries the bolt 1 and is received in a spherical cap (not shown) so that it can pivot about the axes X, Y, Z. This spherical cap is formed from the first spherical cap element 3 and the second spherical cap element 4, both of which are provided with a spherically designed sliding lining 5 in order to reduce friction. The first dome element 3 is L-shaped in section along the axis Z and has the first leg 6 and the second leg
7 auf. Der zweite Schenkel 7 ist an seiner Mantelfläche mit dem Außengewinde7 on. The second leg 7 is on its outer surface with the external thread
8 versehen, das mit dem Innengewinde 9 des zweiten Kalottenelements 4 einen Gewindeverbund bildet. Das zweite Kalottenelement 4 ist ebenfalls L-förmig ausgebildet, wobei der erste Schenkel 10 das Innengewinde 9 und der zweite Schenkel 11 den Gleitbelag 5 trägt. Der erste Schenkel 6 des Kalottenelements 3 ist mit der umlaufenden Ausnehmung 12 versehen, in der die Spiralfeder 13 untergebracht ist. Diese ist an einem Ende über den Stift 14 mit dem ersten Kalottenelement 3 und am anderen Ende mit dem zweiten Kalottenelement 4 verbunden. Diese Verbindung der Spiralfeder 13 mit dem zweiten Kalottenelement 4 erfolgt über das Zwischenteil 16, dessen Mittelteil 17 am oberen und unteren Ende in zwei in entgegengesetzter Richtung abgewinkelte Flansche 18 und 19 endet. Der untere Flansch 18 ist über den Stift 15 mit dem zweiten Ende der Spiralfeder 13 verbunden, so dass deren Drehmoment über das Zwischenteil 16 und die Befestigungsschrauben 20 auf das zweite Kalot- tenelement 4 übertragen werden kann. Um eine sichere radiale Führung der beiden rotationssymmetrisch ausgebildeten Kalottenelemente 3 und 4 ineinander zu gewährleisten, weisen der erste Schenkel 6 des Kalottenelements 3 und der Flansch 18 des Zwischenteiles 16 je einen Vorspruch 22 und 21 auf, wobei der Vorsprung 21 den Vorsprung 22 in radialer Richtung umgreift.8 provided, which forms a threaded connection with the internal thread 9 of the second dome element 4. The second dome element 4 is also L-shaped, the first leg 10 carrying the internal thread 9 and the second leg 11 carrying the sliding lining 5. The first leg 6 of the spherical element 3 is provided with the circumferential recess 12 in which the spiral spring 13 is accommodated. This is connected at one end via the pin 14 to the first dome element 3 and at the other end to the second dome element 4. This connection of the spiral spring 13 to the second spherical element 4 takes place via the intermediate part 16, the central part 17 of which ends at the upper and lower ends in two flanges 18 and 19 which are angled in the opposite direction. The lower flange 18 is connected to the second end of the spiral spring 13 via the pin 15, so that its torque can be transmitted to the second calotte element 4 via the intermediate part 16 and the fastening screws 20. In order to ensure reliable radial guidance of the two rotationally symmetrical dome elements 3 and 4 into one another, the first leg 6 of the dome element 3 and the flange 18 of the intermediate part 16 each have a projection 22 and 21, the projection 21 projecting the projection 22 in the radial direction embraces.
Bei durch Verschleiß der Gleitbeläge 5 auftretendem Lagerspiel wird das zweite Kalottenelement 4 im Uhrzeigersinn gegenüber dem ersten Kalottenelement 3 relativ verdreht, bis der werkstoffliche Kontakt der beiden Gleit- beläge mit der der Spiralfeder 13 entsprechenden Vorspannung wiederhergestellt ist. Dieser Vorgang läuft automatisch ab und wird immer dann ausgelöst, wenn bei eintretendem Verschleiß ein Lastwechsel eintritt, d. h. der Gewindeverbund ohne Last ist. Die Spiralfeder 13 ist dabei so ausgelegt, dass Nach- stellwege erreicht werden, die dem gesamten Lebensdauerverschleiß der Lageranordnung entsprechen. Der erfindungsgemäß ausgebildete Verstellmechanismus arbeitet selbsthemmend und überträgt auf diese Weise in jeder beliebigen Nachstellung mit großer Steifigkeit die Betriebskräfte auch in Zugrichtung (Z-Achse), ohne dass der Arbeitsspeicher (Spiralfeder 13) für die Nach- Stellung davon kräftemäßig berührt ist.If bearing play occurs due to wear of the sliding linings 5, the second dome element 4 is rotated relatively clockwise relative to the first dome element 3 until the material contact of the two sliding elements coverings is restored with the bias corresponding to the coil spring 13. This process runs automatically and is always triggered when a load change occurs when wear occurs, ie the threaded connection is without load. The spiral spring 13 is designed in such a way that adjustment paths are achieved which correspond to the total lifetime wear of the bearing arrangement. The adjustment mechanism designed according to the invention works in a self-locking manner and in this way transmits the operating forces in any adjustment with great rigidity in the pulling direction (Z-axis), without the working memory (coil spring 13) being forcefully touched for the adjustment thereof.
Die in Figur 2 abgebildete Werkzeugmaschine 23 der neuen HEXAPOD- Generation ist mit mehreren, aus ineinandergesteckten Rohren 24, 25 gebildeten Teleskoparmen 26 versehen. Diese Teleskoparme 26 sind einerseits am Rahmen 27 und andererseits an der Werkzeugaufnahme 28 gelenkig befestigt. Die Werkzeugaufnahme 28 ist mit einem nicht dargestellten Werkzeug versehen, das vom Motor 29 angetrieben wird. Durch Ein- bzw. Ausfahren eines oder mehrere Teleskoparme 26 lässt sich die Werkzeugaufnahme 28 in jeder gewünschten Position im Raum bewegen. Die erfindungsgemäß ausgebildeten Gelenke können bei der abgebildeten Werkzeugmaschine 23 sowohl am Rahmen 27 als auch an der Werkzeugaufnahme 28 in vorteilhafter weise eingesetzt werden. The machine tool 23 of the new HEXAPOD generation shown in FIG. 2 is provided with a plurality of telescopic arms 26 formed from nested tubes 24, 25. These telescopic arms 26 are articulated on the one hand on the frame 27 and on the other hand on the tool holder 28. The tool holder 28 is provided with a tool, not shown, which is driven by the motor 29. The tool holder 28 can be moved in any desired position in space by retracting or extending one or more telescopic arms 26. The joints designed according to the invention can be used in the illustrated machine tool 23 in an advantageous manner both on the frame 27 and on the tool holder 28.
Bezugszeichenreference numeral
Bolzenbolt
Kugelelement erstes Kalottenelement zweites KalottenelementBall element first dome element second dome element
Gleitbelag erster Schenkel zweiter SchenkelSliding surface first leg second leg
Außengewindeexternal thread
Innengewinde erster Schenkel zweiter SchenkelInternal thread first leg second leg
Ausnehmungrecess
Spiralfederspiral spring
Stiftpen
Stiftpen
Zwischenteilintermediate part
Mittelteilmidsection
Flanschflange
Flanschflange
Befestigungsschraubefixing screw
Vorsprunghead Start
Vorsprunghead Start
Werkzeugmaschinemachine tool
Rohrpipe
Rohrpipe
Teleskoparmtelescopic arm
Rahmenframe
Werkzeugaufnahmetool holder
Motor engine
Claims
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| AU2001223687A AU2001223687A1 (en) | 2000-01-22 | 2000-12-22 | Ball-and-socket joint |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE2000102757 DE10002757B4 (en) | 2000-01-22 | 2000-01-22 | ball joint |
| DE10002757.1 | 2000-01-22 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| WO2001053710A1 true WO2001053710A1 (en) | 2001-07-26 |
Family
ID=7628446
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| PCT/EP2000/013168 Ceased WO2001053710A1 (en) | 2000-01-22 | 2000-12-22 | Ball-and-socket joint |
Country Status (3)
| Country | Link |
|---|---|
| AU (1) | AU2001223687A1 (en) |
| DE (1) | DE10002757B4 (en) |
| WO (1) | WO2001053710A1 (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1424447A4 (en) * | 2001-09-04 | 2007-10-03 | Shanghai Meglev Transp Dev Co | A adjustable bearing |
| US7476050B2 (en) | 2005-06-30 | 2009-01-13 | Deere & Company | Grease actuated ball and socket joint |
| CN102506055A (en) * | 2011-08-23 | 2012-06-20 | 中国北方车辆研究所 | Ball head pin locking device |
| CN102506054A (en) * | 2011-08-23 | 2012-06-20 | 中国北方车辆研究所 | Vehicle suspension ball head pin assembly |
| CN103410845A (en) * | 2013-07-09 | 2013-11-27 | 郑州飞机装备有限责任公司 | Tensile ball hinge structure |
| ES2754875A1 (en) * | 2018-10-17 | 2020-04-20 | Frenell Gmbh | BEARING FOR SOLAR MODULES (Machine-translation by Google Translate, not legally binding) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10204277B4 (en) * | 2002-02-02 | 2012-03-22 | Bayerische Motoren Werke Aktiengesellschaft | Ball joint with a preloaded bearing shell |
| DE102023003485A1 (en) * | 2023-08-24 | 2024-03-28 | Mercedes-Benz Group AG | Ball joint, chassis and motor vehicle |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE660304C (en) * | 1935-12-29 | 1938-05-23 | Fritz Faudi | Ball joint |
| US3250555A (en) | 1961-12-13 | 1966-05-10 | William C Wehner | Swivel joint |
| US3384397A (en) * | 1965-10-18 | 1968-05-21 | Moog Industries Inc | Ball joint |
| US4974986A (en) * | 1989-08-28 | 1990-12-04 | Cook Robert W | Connector for variable-shape spaceframe structural system |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB992100A (en) * | 1964-03-03 | 1965-05-12 | William Charles Wehner | Swivel joint |
| DE3241551A1 (en) * | 1982-11-10 | 1984-05-10 | Rau Swf Autozubehoer | Driving linkage, in particular for windscreen-cleaning systems in motor vehicles |
-
2000
- 2000-01-22 DE DE2000102757 patent/DE10002757B4/en not_active Expired - Fee Related
- 2000-12-22 AU AU2001223687A patent/AU2001223687A1/en not_active Abandoned
- 2000-12-22 WO PCT/EP2000/013168 patent/WO2001053710A1/en not_active Ceased
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE660304C (en) * | 1935-12-29 | 1938-05-23 | Fritz Faudi | Ball joint |
| US3250555A (en) | 1961-12-13 | 1966-05-10 | William C Wehner | Swivel joint |
| US3384397A (en) * | 1965-10-18 | 1968-05-21 | Moog Industries Inc | Ball joint |
| US4974986A (en) * | 1989-08-28 | 1990-12-04 | Cook Robert W | Connector for variable-shape spaceframe structural system |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1424447A4 (en) * | 2001-09-04 | 2007-10-03 | Shanghai Meglev Transp Dev Co | A adjustable bearing |
| US7476050B2 (en) | 2005-06-30 | 2009-01-13 | Deere & Company | Grease actuated ball and socket joint |
| CN102506055A (en) * | 2011-08-23 | 2012-06-20 | 中国北方车辆研究所 | Ball head pin locking device |
| CN102506054A (en) * | 2011-08-23 | 2012-06-20 | 中国北方车辆研究所 | Vehicle suspension ball head pin assembly |
| CN102506055B (en) * | 2011-08-23 | 2014-03-12 | 中国北方车辆研究所 | Ball head pin locking device |
| CN103410845A (en) * | 2013-07-09 | 2013-11-27 | 郑州飞机装备有限责任公司 | Tensile ball hinge structure |
| ES2754875A1 (en) * | 2018-10-17 | 2020-04-20 | Frenell Gmbh | BEARING FOR SOLAR MODULES (Machine-translation by Google Translate, not legally binding) |
| US10866011B2 (en) | 2018-10-17 | 2020-12-15 | Frenell Gmbh | Support for solar modules |
Also Published As
| Publication number | Publication date |
|---|---|
| DE10002757A1 (en) | 2001-07-26 |
| AU2001223687A1 (en) | 2001-07-31 |
| DE10002757B4 (en) | 2010-12-02 |
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