EP0195983B1 - One drum capstan - Google Patents

One drum capstan Download PDF

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Publication number
EP0195983B1
EP0195983B1 EP86103392A EP86103392A EP0195983B1 EP 0195983 B1 EP0195983 B1 EP 0195983B1 EP 86103392 A EP86103392 A EP 86103392A EP 86103392 A EP86103392 A EP 86103392A EP 0195983 B1 EP0195983 B1 EP 0195983B1
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EP
European Patent Office
Prior art keywords
capstan
load
head
cable
windings
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Expired
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EP86103392A
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German (de)
French (fr)
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EP0195983A1 (en
Inventor
Peter Bechmann
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Individual
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Individual
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Priority to AT86103392T priority Critical patent/ATE39676T1/en
Publication of EP0195983A1 publication Critical patent/EP0195983A1/en
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
    • B66D1/60—Rope, cable, or chain winding mechanisms; Capstans adapted for special purposes
    • B66D1/74—Capstans
    • B66D1/7442—Capstans having a horizontal rotation axis
    • B66D1/7447—Capstans having a horizontal rotation axis driven by motor only

Definitions

  • the invention relates to a single-head capstan winch of the type specified by the preamble of claim 1.
  • the clamping force required in the capstan winch for holding the load rope on the capstan head is generated by means of a synchronously driven clamping disc.
  • the clamping disc has a clamping groove in the transition from two disc parts axially preloaded against each other by compression springs, in which the rope length running from the capstan head is guided over a deflection roller arranged parallel to the axis after a preferably provided deflection, before it is only then forwarded without load to a rope storage device.
  • the deflection roller is always required to generate the necessary frictional connection between the multiple wrapping of the load rope and the jacket of the capstan head if the capstan winch is designed for a higher load transmission.
  • a multi-head capstan winch with a motor-driven capstan head and at least one axially parallel deflection pulley is known, by means of which a load-transmitting frictional engagement between a multiple looping of the load rope and the jacket of the capstan head is also generated. Furthermore, in this capstan winch there are pressure rollers that are biased by springs, each pressing only one turn of the load rope firmly anchored with its two rope ends to the capstan head and to the or each further provided deflection roller for mere guiding purposes.
  • the invention characterized by claims 1 or 2 solves the problem of designing a single-head capstan winch of the type specified in such a way that the clamping force required in the drive of the capstan head to hold the load rope on its jacket is load-dependent and at the same time translated without access to a by a clamping disc arrangement Spring force is provided, a safety factor comparable to that of the multi-head capstan winches for holding a load of the same order of magnitude attached to the load rope should be achievable on the basis of the same motor drive power.
  • the complementary and at the same time rotationally symmetrical design of the contact surface of the or each cable pressure roller for all cable turns complements the envelope surface of the multiple wrapping of the load cable, and the same throughput speed is obtained through the gap which is formed between the capstan head and each cable pressure roller.
  • This same throughput speed of all rope turns prevents any excessive deformation of the load rope, even taking into account the likelihood of axial migration of the multiple wrap, which is always present in such single-head capstan winches, which is typically caused by foreign substances adhering to the load rope and therefore changing its load-transmitting frictional connection with the jacket of the capstan head is caused.
  • the capstan winch shown in the drawing for a mobile embodiment including a drive motor with a power of 4 hp (2.9 kW) and a commercially available planetary gear change load bearing total weight of only about 16 kilograms comprises a support frame 1 welded together from individual carriers, which at its upper End is provided with an abutment formed by an eyelet 2.
  • the lower end of the support frame 1 is formed with two parallel beams 3 and 4, to each of which a guide rail 5 or 6 of a parallel guide provided for the capstan winch is attached.
  • the main beams of the support frame 1 can have a rectangular hollow profile 7.
  • the multiple wrap 28 has an arrangement axially displaced towards the annular flange 22.
  • the two rope lengths 30 and 31 are then functionally interchanged, which again ensures that one rope length 31 then runs onto the larger diameter area 27 so that the other rope length 30 can run from a smaller diameter area.
  • the output shaft 13 of the planetary gear change transmission results in the coupling of a drive motor, not shown in the drawing, to the drive shaft 12 of the drive shaft for the capstan head 15 when a claw coupling 32 provided for a drive connection is engaged.
  • the dog clutch 32 consists of a driver part 33, which is connected in a rotationally fixed manner to the output shaft 13 by means of a wedge 34 and is axially movable in the direction of the double arrow 35.
  • the claw coupling 32 comprises two claws 36 and 37, which can be seen in the illustration in FIG. 1, and which are fastened to the jacket 8 of the capstan head 15 at a distance of 180 degrees from one another by screws 38.
  • two somewhat larger engagement recesses 39 and 40 are formed corresponding to the claws 36 and 37, claws and engagement recesses also having complementary friction surfaces which, as shown in FIG. 2, at an inclination angle 1) obliquely to the axis of rotation 14 of the Capstan head 15 are aligned.
  • the parallel guide formed with the two guide rails 5, 6 of the support frame 1 is oriented at an angle y obliquely to the line of action of the tensile force Si, so that there is a corresponding to the tensile force Si for a guide flange 42 provided on the housing 11 for guidance by these guide rails results in an angular displacement guide in the direction of the double arrow 43.
  • a force component acting in the direction of arrow 44 is thus obtained for the counterforce acting in the direction of arrow 41 to the tensile force S 1 , which force component is therefore subject to the input and output shafts 12 and 13 of the planetary gear change transmission arranged in the axis of rotation 14 of the capstan head 15.
  • the force component acting in the direction of arrow 44 is further divided along two lines of action, which are indicated by arrows 45 and 46 and are spaced apart by more than 90 degrees.
  • the axes of rotation 47 and 48 of two rope pressure rollers 49 are arranged, which are rotatably mounted on the support frame 1 by a welded-on U-shaped support 50.
  • the axes of rotation 47, 48 are aligned at an angle to the axis of rotation 14 of the capstan head 15 such that for a rotationally symmetrical contact surface of the two rope pressure rollers 49, which is complementary to the envelope surface of the multiple loop 28 of the load rope, a frictional contact is simultaneously applied to all windings of the multiple loop 28 results, which are located on the assigned axial partial length of the jacket 8.
  • the force component acting in the direction of the arrow 44 thus becomes a load-dependent clamping force for this frictional engagement of the two rope pressure rollers 49 exerted on all turns of the multiple wrap 28.
  • the different angular orientation results from the different envelopes of the multiple looping of the load rope, respectively. from the different course of the curvature of the jacket 8 of the capstan head formed with the radii of curvature R.
  • the opposite to the direction of arrow 29 direction of rotation of capstan 15 and. its jacket 8 requires disengagement of the dog clutch 32 or alternatively the use of a reversing motor to be switched over for this purpose as the drive motor for the capstan head.
  • the support frame 1 When working with the capstan winch described above, for example in forestry, the support frame 1 is first anchored in place by means of a belt attached to the eyelet 2. Then, with the claw coupling 32 disengaged and the jacket 8 freely rotatable in the opposite direction to the arrow 29, the accruing rope length 30 is pulled with its free end towards the load which is to be brought to the anchorage location of the capstan winch.
  • the running rope length 31 is pulled from a rope storage device, which can either be attached to the support frame 1 to accommodate any desired rope length or is more appropriately separated so that the load rope can also be transported separately from the capstan winch.
  • the capstan head 15 is driven in the arrow direction 29 after the drive motor is switched on, the multiple looping 28 of the load rope without any hindrance to the throughput speed of the individual rope turns during the pulling of the load experiences load-dependent jamming between the rope pressure rollers 49 and the jacket 8.
  • the frictional surfaces which are complementary on the claws 36, 37 and the engagement recesses 39, 40 of the claw clutch 32 prevent the claw clutch from being disengaged for safety reasons.
  • FIG. 2 also shows a braking device 54 for the drive shaft 12 of the planetary gear changing mode, with which a rotation of the casing 8 opposite to the arrow direction 29 when the claw clutch 32 is disengaged can be braked.
  • This braking option then supplements the braking force exerted on the multiple wrap 28 in a load-dependent manner by means of the rope pressure rollers 51, which can be important in individual cases if the capstan winch is not only used for horizontal, but also for inclined and, in extreme cases using a hoist as an example, also vertical movement is used by loads.
  • the above-described single-head capstan winch can transmit a pulling force of up to 1200 kg.
  • the principle of load-dependent influencing of the clamping force exerted on the multiple looping of the load rope can also be applied to the transmission of significantly higher tensile forces.
  • a bearing that can be pivoted relatively to the rope pressure rollers can then be discussed for the capstan head instead of being supported by a sliding guide, but the implementation thereof is more complex.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)
  • Tension Adjustment In Filamentary Materials (AREA)
  • Types And Forms Of Lifts (AREA)
  • Crystals, And After-Treatments Of Crystals (AREA)
  • Jib Cranes (AREA)
  • Earth Drilling (AREA)
  • Iron Core Of Rotating Electric Machines (AREA)
  • Storing, Repeated Paying-Out, And Re-Storing Of Elongated Articles (AREA)

Abstract

A single head capstan winch comprises a capstan head which is movably arranged on a supporting frame for being guided relative to a pressing roller and is also rotatably arranged on this supporting frame and provided with a dynamically balanced surface of a shape that complements the enveloping surface of a multiplicity of windings of a cable or rope of the winch to thereby obtain a load-controlled clamping force necessary for the hauling-in of a load by means of the forward extending portion of the cable or rope the rearward extension of which runs off free of any load from the capstan head.

Description

Die Erfindung bezieht sich auf eine Einkopf-Spillwinde der durch den Oberbegriff des Patentanspruchs 1 angegebenen Gattung.The invention relates to a single-head capstan winch of the type specified by the preamble of claim 1.

Bei einer aus der FR-A 2 513 236 bekannten Einkopf-Spillwinde dieser Art wird die im Antrieb der Spillwinde für das Halten des Lastseils am Spillkopf benötigte Klemmkraft mittels einer synchron angetriebenen Klemmscheibe erzeugt. Die Klemmscheibe weist dafür im Übergang von zwei durch Druckfedem axial gegeneinander vorgespannten Scheibenteilen eine Klemmrille auf, in welcher die vom Spillkopf ablaufende Seillänge nach einer bevorzugt vorgesehenen Umlenkung über eine achsparallel angeordnete Umlenkrolle geführt ist, bevor sie erst anschließend zu einem Seilspeicher hin lastfrei weitergeleitet wird. Die Umlenkrolle wird dabei immer dann zur Erzeugung des notwendigen Reibungsschlusses zwischen der Mehrfachumschlingung des Lastseils und dem Mantel des Spillkopfes benötigt, wenn die Spillwinde für eine höhere Lastübertragung ausgelegt wird.In a single-head capstan winch of this type known from FR-A 2 513 236, the clamping force required in the capstan winch for holding the load rope on the capstan head is generated by means of a synchronously driven clamping disc. For this purpose, the clamping disc has a clamping groove in the transition from two disc parts axially preloaded against each other by compression springs, in which the rope length running from the capstan head is guided over a deflection roller arranged parallel to the axis after a preferably provided deflection, before it is only then forwarded without load to a rope storage device. The deflection roller is always required to generate the necessary frictional connection between the multiple wrapping of the load rope and the jacket of the capstan head if the capstan winch is designed for a higher load transmission.

Aus der GB-A 1 035 652 ist eine Mehrkopf-Spillwinde mit einem motorisch angetriebenen Spillkopf und wenigstens einer achsparallel angeordneten Umlenkrolle bekannt, mittels welcher auch dabei ein lastübertragender Reibungsschluß zwischen einer Mehrfachumschlingung des Lastseils und dem Mantel des Spillkopfes erzeugt wird. Weiterhin sind bei dieser Spillwinde noch durch Federn vorgespannte Andrückrollen vorhanden, die jeweils nur eine Windung des mit seinen beiden Seilenden fest verankerten Lastseils an den Spillkopf und an die oder jede weitere vorgesehene Umlenkrolle für bloße Führungszwecke andrücken.From GB-A 1 035 652 a multi-head capstan winch with a motor-driven capstan head and at least one axially parallel deflection pulley is known, by means of which a load-transmitting frictional engagement between a multiple looping of the load rope and the jacket of the capstan head is also generated. Furthermore, in this capstan winch there are pressure rollers that are biased by springs, each pressing only one turn of the load rope firmly anchored with its two rope ends to the capstan head and to the or each further provided deflection roller for mere guiding purposes.

Die durch die Patentansprüche 1 oder 2 gekennzeichnete Erfindung löst die Aufgabe, eine Einkopf-Spillwinde der angegebenen Gattung derart auszubilden, daß die im Antrieb des Spillkopfes zum Halten des Lastseils an seinem Mantel benötigte Klemmkraft lastabhängig und dabei gleichzeitig ohne Zugriff auf eine durch eine Klemmscheibenanordnung übersetzte Federkraft bereit gestellt wird, wobei unter Zugrundelegung einer gleichen motorischen Antriebsleistung ein mit den Mehrkopf-Spillwinden vergleichbarer Sicherheitsfaktor für das Halten einer an das Lastseil angehängten Last gleicher Größenordnung erreichbar sein soll.The invention characterized by claims 1 or 2 solves the problem of designing a single-head capstan winch of the type specified in such a way that the clamping force required in the drive of the capstan head to hold the load rope on its jacket is load-dependent and at the same time translated without access to a by a clamping disc arrangement Spring force is provided, a safety factor comparable to that of the multi-head capstan winches for holding a load of the same order of magnitude attached to the load rope should be achievable on the basis of the same motor drive power.

Die mit der erfindungsgemäßen Einkopf-Spillwinde erreichten Vorteile liegen im wesentlichen darin, daß jetzt der bei jedem Spillkopf den lastübertragenden Reibungsschluß der Mehrfachumschlingung des Lastseils primär bestimmende Reibungswinkel eine lastabhängige Ergänzung durch die Druckkraft erfährt, die von der bzw. jeder an dem Stützrahmen drehbar gelagerten Seilandrückrolle gleichzeitig auf alle Seilwindungen ausgeübt wird. Weil diese auch von dem Eigengewicht des Spillkopfes unter Einschluß seines Antriebes beeinflußte Druckkraft eine Abhängigkeit von der winkelmäßigen Ausrichtung der Zugkraft aufweist, kann damit jetzt gleichzeitig ohne jede Beschränkung der Seillänge eine wesentlich höhere Lastübertragung für solche Einkopf-Spillwinden unter Einhaltung eines gleichen Sicherheitsfaktors wie bei den Mehrkopf-Spillwinden garantiert werden. Dabei ist auch wesentlich, daß durch die zu der Hüllfläche der Mehrfachumschlingung des Lastseils komplementäre und gleichzeitig rotationssymmetrische Ausbildung der Anlagefläche der bzw. jeder Seilandrückrolle für alle Seilwindungen eine gleiche Durchlaufgeschwindigkeit durch den Spalt erhalten wird, der zwischen dem Spillkopf und jeder Seilandrückrolle ausgebildet ist. Diese gleiche Durchlaufgeschwindigkeit aller Seilwindungen verhindert jede übermäßige Verformung des Lastseils auch unter Einbeziehung der bei solchen Einkopf-Spillwinden immer vorhandenen Wahrscheinlichkeit eines axialen Wanderns der Mehrfachumschlingung, was typischerweise durch an dem Lastseil anhaftende und daher dessen last- übertragenden Reibungsschluß mit dem Mantel des Spillkopfes verändernde Fremdstoffe verursacht wird.The advantages achieved with the single-head capstan winch according to the invention are essentially that now the friction angle, which determines the load-transmitting frictional connection of the multiple looping of the load rope with each capstan head, is subjected to a load-dependent addition by the compressive force that is exerted by the or each rope pressure roller rotatably mounted on the support frame is applied to all turns of the rope at the same time. Because this pressure force, which is also influenced by the weight of the capstan head including its drive, is dependent on the angular orientation of the tensile force, it is now possible to transfer a much higher load for such single-head capstan winches while maintaining the same safety factor as the ones without any restriction on the cable length Multi-head capstan winches are guaranteed. It is also essential that the complementary and at the same time rotationally symmetrical design of the contact surface of the or each cable pressure roller for all cable turns complements the envelope surface of the multiple wrapping of the load cable, and the same throughput speed is obtained through the gap which is formed between the capstan head and each cable pressure roller. This same throughput speed of all rope turns prevents any excessive deformation of the load rope, even taking into account the likelihood of axial migration of the multiple wrap, which is always present in such single-head capstan winches, which is typically caused by foreign substances adhering to the load rope and therefore changing its load-transmitting frictional connection with the jacket of the capstan head is caused.

Ein Ausführungsbeispiel der erfindungsgemäßen Einkopf-Spillwinde ist in der Zeichnung schematisch dargestellt und wird nachfolgend näher beschrieben. Es zeigt

  • Figur 1 eine teilweise geschnittene Stirnansicht der Spillwinde in der Pfeilrichtung gemäß Figur 2,
  • Figur 2 eine teilweise geschnittene Seitenansicht der Spillwinde gemäß Figur 1 und
  • Figur 3 eine teilweise geschnittene Seitenansicht einer für die Spillwinde vorgesehenen Klauenkupplung.
An embodiment of the single-head capstan winch according to the invention is shown schematically in the drawing and is described in more detail below. It shows
  • FIG. 1 shows a partially sectioned end view of the capstan winch in the direction of the arrow according to FIG. 2,
  • Figure 2 is a partially sectioned side view of the capstan winch according to Figure 1 and
  • Figure 3 is a partially sectioned side view of a claw coupling provided for the capstan winch.

Die in der Zeichnung für eine mobile Ausführungsform mit einem einschließlich eines Antriebsmotors einer Leistung von 4 PS (2,9 kW) und eines handelsüblichen Planetenräderwechselgetriebes tragfähigen Gesamtgewicht von nur etwa 16 Kilogramm gezeigte Spillwinde umfaßt einen aus einzelnen Trägern zusammengeschweißten Stützrahmen 1, der an seinem oberen Ende mit einem durch eine Öse 2 gebildeten Widerlager versehen ist. Das untere Ende des Stützrahmens 1 ist mit zwei parallel verlaufenden Trägern 3 und 4 gebildet, an welchen je eine Führungsschiene 5 bzw. 6 einer für die Spillwinde vorgesehenen Parallelführung befestigt sind. Die Hauptträger des Stützrahmens 1 können ein rechteckiges Hohlprofil 7 aufweisen.The capstan winch shown in the drawing for a mobile embodiment including a drive motor with a power of 4 hp (2.9 kW) and a commercially available planetary gear change load bearing total weight of only about 16 kilograms comprises a support frame 1 welded together from individual carriers, which at its upper End is provided with an abutment formed by an eyelet 2. The lower end of the support frame 1 is formed with two parallel beams 3 and 4, to each of which a guide rail 5 or 6 of a parallel guide provided for the capstan winch is attached. The main beams of the support frame 1 can have a rectangular hollow profile 7.

Ein für eine kraftübertragende Mehrfachumschlingung eines Lastseils längs einer axialen Teillänge eingerichteter trommelförmiger Mantel 8 des bezüglich der Breitseite des Stützrahmens 1 vorstehend angeordneten Spillkopfes der Spillwinde ist mittels zweier Nadellager 9 und 10 auf dem Gehäuse 11 eines Planetenräderwechselgetriebes drehbar gelagert, dessen Antriebs- und Abtriebswellen 12 und 13 koaxial zu der Drehachse 14 des Spillkopfes 15 angeordnet sind. Die beiden Nadellager 9, 10 sind durch einen Distanzring 16 voneinander beabstandet und zwischen zwei Dichtungen 17 und 18 angeordnet, die in zwei abgestufte Zentrierbohrungen des Mantels 8 eingesetzt sind. Der Mantel 8 wird durch Sicherungsringe 19 und 20 axial unbeweglich an dem Gehäuse 11 gehalten und weist eine rotationssymmetrische Mantelfläche auf, deren gekrümmter Verlauf zwischen zwei an den axialen Mantelenden ausgebildeten ringförmigen Flanschen 21 und 22 mit einem auf zwei Mittelpunkte 23 bezogenen Krümmungshalbmesser R wesentlich größer als der Außendurchmesser des Mantels 8 gebildet ist. Mit diesem gekrümmten Verlauf der Mantelfläche wird ein kleinster Durchmesserbereich 25 im Übergang von zwei axial ungleich großen Teillängen des Mantels 8 erhalten, die an den ringförmigen Flanschen 21 und 22 jeweils in einem größeren Durchmesserbereich 26 bzw. 27 enden. Diese beiden Teillängen sind für eine in Abhängigkeit von der Drehrichtung des Spillkopfes 15 abwechselnde Aufnahme einer Mehrfachumschlingung 28 des Lastseils eingerichtet, die bei der in Figur 2 mit dem Richtungspfeil 29 angegebenen Drehrichtung der Abtriebswelle 13 beispielsweise mit sechs Windungen gebildet sein kann. Diese sechs Windungen sind dabei auf die auf den größeren Durchmesserbereich 26 auflaufende Seillänge 30 sowie auf die mit zwei Windungen den kleineren Durchmesserbereich 25 überlappende ablaufende Seillänge 31 bezogen. Mit dieser Mehrfachumschlingung 28 des Lastseils wird im Antrieb des Spillkopfes 15 in bezug auf den Mantel 8 ein lastübertragender Reibungsschluß erzeugt, der die folgenden Gleichungen erfüllt:

  • U = Si - S2
  • Si=S2.eä
  • U=S2(eä-1)
  • wobei: U = übertragbare Umfangskraft des Mantels 8
  • Si, S2 = Zugkräfte der auf- und ablaufenden Seillängen 30 und 31
  • a = Umschlingungswinkel
  • µ = Reibungswinkel
A drum-shaped jacket 8 of the capstan head of the capstan winch, which is arranged above for the broad side of the support frame 1, is arranged for a force-transmitting multiple looping of a load rope along an axial partial length and is rotatably mounted on the housing 11 of a planetary gear change transmission by means of two needle bearings 9 and 10, the input and output shafts 12 and 13 are arranged coaxially with the axis of rotation 14 of the capstan head 15. The two needle bearings 9, 10 are spaced apart from one another by a spacer ring 16 and are arranged between two seals 17 and 18, which are inserted into two stepped centering bores in the casing 8. The jacket 8 is held axially immovably on the housing 11 by retaining rings 19 and 20 and has a rotationally symmetrical jacket surface, the curved course of which between two on the axial Shaped ends formed annular flanges 21 and 22 with a curvature radius R related to two centers 23 is formed substantially larger than the outer diameter of the jacket 8. With this curved course of the lateral surface, a smallest diameter region 25 is obtained in the transition from two axially unequal partial lengths of the jacket 8, which each end in a larger diameter region 26 and 27 on the annular flanges 21 and 22. These two partial lengths are set up to accommodate a multiple looping 28 of the load rope, which is alternating depending on the direction of rotation of the capstan head 15 and which can be formed, for example, with six turns in the direction of rotation of the output shaft 13 indicated by the arrow 29 in FIG. These six turns are related to the rope length 30 running onto the larger diameter area 26 and to the running rope length 31 overlapping the smaller diameter area 25 with two turns. With this multiple loop 28 of the load rope, a load-transmitting frictional engagement is generated in the drive of the capstan head 15 with respect to the sheath 8, which friction fit fulfills the following equations:
  • U = S i - S 2
  • Si = S2.eä
  • U = S 2 (eä-1)
  • where: U = transferable circumferential force of the jacket 8
  • Si, S 2 = tensile forces of the up and down rope lengths 30 and 31
  • a = wrap angle
  • µ = friction angle

In der zu dem Richtungspfeil 29 entgegengesetzten Drehrichtung des Spillkopfes 15 weist die Mehrfachumschlingung 28 eine hin zu dem ringförmigen Flansch 22 axial verlagerte Anordnung auf. Die beiden Seillängen 30 und 31 sind dann funktionell vertauscht, womit wieder sicher gestellt ist, daß dann die eine Seillänge 31 auf den größeren Durchmesserbereich 27 aufläuft, damit die andere Seillänge 30 von einem kleineren Durchmesserbereich ablaufen kann.In the direction of rotation of the capstan head 15 opposite to the direction arrow 29, the multiple wrap 28 has an arrangement axially displaced towards the annular flange 22. The two rope lengths 30 and 31 are then functionally interchanged, which again ensures that one rope length 31 then runs onto the larger diameter area 27 so that the other rope length 30 can run from a smaller diameter area.

Die Abtriebswelle 13 des Plantenräderwechselgetriebes ergibt bei einer Ankuppelung eines in der Zeichnung nicht dargestellten Antriebsmotors an dessen Antriebswelle 12 die Antriebswelle für den Spillkopf 15, wenn eine für eine Antriebsverbindung vorgesehene Klauenkupplung 32 eingerückt ist. Die Klauenkupplung 32 besteht aus einem Mitnehmerteil 33, der mittels eines Keils 34 mit der Abtriebswelle 13 drehfest und in Richtung des Doppelpfeils 35 axial beweglich verbunden ist. Weiterhin umfaßt die Klauenkupplung 32 zwei aus der Darstellung in Figur 1 ersichtliche Klauen 36 und 37, die an dem Mantel 8 des Spillkopfes 15 über 180 Bogengrade voneinander beabstandet durch Schrauben 38 befestigt sind. An dem Mitnehmerteil 33 sind zwei etwas größer dimensionierte Eingriffsaussparungen 39 und 40 korrespondierend zu den Klauen 36 und 37 ausgebildet, wobei Klauen und Eingriffsaussparungen noch komplementär ausgebildete Reibflächen aufweisen, die gemäß der Darstellung in Figur 2 unter einem Neigungswinkel 1) schräg zu der Drehachse 14 des Spillkopfes 15 ausgerichtet sind.The output shaft 13 of the planetary gear change transmission results in the coupling of a drive motor, not shown in the drawing, to the drive shaft 12 of the drive shaft for the capstan head 15 when a claw coupling 32 provided for a drive connection is engaged. The dog clutch 32 consists of a driver part 33, which is connected in a rotationally fixed manner to the output shaft 13 by means of a wedge 34 and is axially movable in the direction of the double arrow 35. Furthermore, the claw coupling 32 comprises two claws 36 and 37, which can be seen in the illustration in FIG. 1, and which are fastened to the jacket 8 of the capstan head 15 at a distance of 180 degrees from one another by screws 38. On the driver part 33, two somewhat larger engagement recesses 39 and 40 are formed corresponding to the claws 36 and 37, claws and engagement recesses also having complementary friction surfaces which, as shown in FIG. 2, at an inclination angle 1) obliquely to the axis of rotation 14 of the Capstan head 15 are aligned.

Aus der Darstellung in Figur 2 ist ableitbar, daß das mit der Öse 2 gebildete Widerlager des Stützrahmens 1 in der Fluchtlinie der Zugkraft S1 angeordnet ist, die im Antrieb des Spillkopfes 15 durch eine an die auflaufende Seillänge 30 des Lastseils angehängte Last ausgeübt wird. Über das mit der Öse 2 gebildete Widerlager des Stützrahmens 1 muß daher für eine mit der Mehrfachumschlingung 28 des Lastseils mögliche Lastübertragung entsprechend der Darstellung in Figur 1 primär eine entsprechend große Gegenkraft auf den Stützrahmen 1 ausgeübt werden, deren zu der Zugkraft Si parallele Wirklinie dort mit dem Richtungspfeil 41 angegeben ist. Die mit den beiden Führungsschienen 5,6 des Stützrahmens 1 gebildete Parallelführung ist unter einem Winkel y schräg zu der Wirklinie der Zugkraft Si ausgerichtet, so daß sich für einen zur Führung durch diese Führungsschienen vorgesehenen Führungsflansch 42 an dem Gehäuse 11 eine zu der Zugkraft Si entsprechend im Winkel ausgerichtete Verschiebeführung in Richtung des Doppelpfeils 43 ergibt. Es wird damit für die in Richtung des Pfeils 41 wirkende Gegenkraft zu der Zugkraft S1 eine in Richtung des Pfeils 44 wirkende Kraftkomponente erhalten, welcher somit die in der Drehachse 14 des Spillkopfes 15 angeordneten Antriebs-und Abtriebswellen 12 und 13 des Plantenräderwechselgetriebes unterliegen.From the illustration in Figure 2 it can be deduced that the abutment of the support frame 1 formed with the eyelet 2 is arranged in the alignment of the tensile force S 1, which is exerted in the drive of the capstan head 15 by a load attached to the ascending rope length 30 of the load rope. Via the abutment of the support frame 1 formed with the eyelet 2, a correspondingly large counterforce must therefore be exerted on the support frame 1 for a load transmission possible with the multiple loop 28 of the load rope, the line of action of which parallel to the tensile force S i there is indicated by the directional arrow 41. The parallel guide formed with the two guide rails 5, 6 of the support frame 1 is oriented at an angle y obliquely to the line of action of the tensile force Si, so that there is a corresponding to the tensile force Si for a guide flange 42 provided on the housing 11 for guidance by these guide rails results in an angular displacement guide in the direction of the double arrow 43. A force component acting in the direction of arrow 44 is thus obtained for the counterforce acting in the direction of arrow 41 to the tensile force S 1 , which force component is therefore subject to the input and output shafts 12 and 13 of the planetary gear change transmission arranged in the axis of rotation 14 of the capstan head 15.

Die in Richtung des Pfeils 44 wirkende Kraftkomponente erfährt eine weitere Aufteilung längs zweier Wirklinien, die mit den Pfeilen 45 und 46 angegeben und über 90 Bogengrade voneinander beabstandet sind. In diesen Wirklinien sind die Drehachsen 47 und 48 von zwei Seilandrückrollen 49 angeordnet, die an dem Stützrahmen 1 durch je einen angeschweißten U-förmigen Träger 50 drehbar gelagert sind. Die Drehachsen 47, 48 sind dabei im Winkel zu der Drehachse 14 des Spillkopfes 15 derart ausgerichtet, daß sich für eine zu der Hüllfläche der Mehrfachumschlingung 28 des Lastseils komplementär ausgebildete, rotationssymmetrische Anlagefläche der beiden Seilandrückrollen 49 jeweils eine reibschlüssige Anlage gleichzeitig an alle Windungen der Mehrfachumschlingung 28 ergibt, die sich auf der zugeordneten axialen Teillänge des Mantels 8 befinden. Unter Berücksichtigung der in Richtung des Doppelpfeils 43 bezüglich des Stützrahmens 1 wirksamen Verschiebeführung und der auf die Wirklinien entsprechend der Pfeile 45 und 46 erfolgten Aufteilung der in Richtung des Pfeils 44 wirkenden Kraftkomponente wird damit aber für diese reibschlüssige Anlage der beiden Seilandrückrollen 49 eine mithin lastabhängige Klemmkraft auf alle Windungen der Mehrfachumschlingung 28 ausgeübt.The force component acting in the direction of arrow 44 is further divided along two lines of action, which are indicated by arrows 45 and 46 and are spaced apart by more than 90 degrees. In these lines of action, the axes of rotation 47 and 48 of two rope pressure rollers 49 are arranged, which are rotatably mounted on the support frame 1 by a welded-on U-shaped support 50. The axes of rotation 47, 48 are aligned at an angle to the axis of rotation 14 of the capstan head 15 such that for a rotationally symmetrical contact surface of the two rope pressure rollers 49, which is complementary to the envelope surface of the multiple loop 28 of the load rope, a frictional contact is simultaneously applied to all windings of the multiple loop 28 results, which are located on the assigned axial partial length of the jacket 8. Taking into account the effective displacement guidance in the direction of the double arrow 43 with respect to the support frame 1 and the division of the force component acting on the lines of action according to the arrows 45 and 46, the force component acting in the direction of the arrow 44 thus becomes a load-dependent clamping force for this frictional engagement of the two rope pressure rollers 49 exerted on all turns of the multiple wrap 28.

Damit die gleiche, lastabhängig beeinflußte Klemmkraft auch in der zu der Pfeilrichtung 29 entgegengesetzten Drehrichtung des Spillkopfes 15 erhalten wird, in welcher dann die Mehrfachumschlingung 28 hin zu dem größeren Durchmesserbereich 27 des Mantels 8 verlagert ist, sind auch für dessen andere axiale Teillänge zwei Seilandrückrollen 51 in entsprechender Weise mittels weiterer U-förmiger Träger 52 an dem Stützrahmen 1 drehbar gelagert. Auch diese weiteren Seilandrückrollen 51 sind mit einer zu der Hüllfläche der Mehrfachumschlingung 28 des Lastseils komplementär ausgebildeten, rotationssymmetrischen Anlagefläche versehen, wodurch ihre Drehachsen 53 ebenfalls in einem von den Drehachsen 47, 48 der Seilandrückrollen 49 allerdings abweichenden Winkel zu der Drehachse 14 des Spillkopfes 15 ausgerichtet sind. Die unterschiedliche Winkelausrichtung ergibt sich dabei aus den unterschiedlichen Hüllkurven der Mehrfachumschlingung des Lastseils resp. aus dem unterschiedlichen Verlauf der mit den Krümmungsradien R gebildeten Krümmung des Mantels 8 des Spillkopfes. Die zu der Pfeilrichtung 29 entgegengesetzte Drehrichtung des Spillkopfes 15 resp. seines Mantels 8 setzt ein Ausrücken der Klauenkupplung 32 voraus oder alternativ die Verwendung eines dafür dann umzuschaltenden Umkehrmotors als Antriebsmotor für den Spillkopf.So that the same load-dependent clamping force is also obtained in the direction of rotation of the capstan head 15 opposite to the arrow direction 29, in which the multiple wrap 28 is then shifted towards the larger diameter region 27 of the jacket 8, are also for the sen other axial part length two rope pressure rollers 51 in a corresponding manner rotatably mounted on the support frame 1 by means of further U-shaped carrier 52. These further rope pressure rollers 51 are also provided with a rotationally symmetrical contact surface which is complementary to the envelope surface of the multiple loop 28 of the load rope, as a result of which their axes of rotation 53 are also oriented at an angle to the axis of rotation 14 of the capstan head 15 that is different from the axes of rotation 47, 48 of the rope pressure rollers 49 are. The different angular orientation results from the different envelopes of the multiple looping of the load rope, respectively. from the different course of the curvature of the jacket 8 of the capstan head formed with the radii of curvature R. The opposite to the direction of arrow 29 direction of rotation of capstan 15 and. its jacket 8 requires disengagement of the dog clutch 32 or alternatively the use of a reversing motor to be switched over for this purpose as the drive motor for the capstan head.

Bei einem Arbeiten mit der vorbeschriebenen Spillwinde beispielsweise im Forstwesen wird zuerst der Stützrahmen 1 mittels eines an der Öse 2 befestigten Gurtes ortsfest verankert. Es wird dann bei ausgerückter Klauenkupplung 32 und einer dadurch ermöglichten freien Drehbarkeit des Mantels 8 entgegengesetzt zu der Pfeilrichtung 29 die auflaufende Seillänge 30 mit ihrem freien Ende hin zu der Last gezogen, die zu dem Verankerungsort der Spillwinde hin herangeholt werden soll. Die ablaufende Seillänge 31 wird dabei aus einem Seilspeicher nachgezogen, der zur Aufnahme jeder beliebig gewünschten Seillänge entweder ebenfalls an dem Stützrahmen 1 noch befestigt sein kann oder zweckmäßiger getrennt ist, so daß mit ihm das Lastseil auch getrennt von der Spillwinde transportiert werden kann. Wenn dann die Last an das Lastseil angehängt und die Klauenkupplung 32 eingerückt ist, wird nach einem Einschalten des Antriebsmotors der Spillkopf 15 in der Pfeilrichtung 29 angetrieben, wobei während des Heranholens der Last die Mehrfachumschlingung 28 des Lastseils ohne jede Behinderung der Druchlaufgeschwindigkeit der einzelnen Seilwindungen eine lastabhängige Verklemmung zwischen den Seilandrückrollen 49 und dem Mantel 8 erfährt. Bei diesem Antrieb des Spillkopfes 15 wird dabei gleichzeitig durch die an den Klauen 36, 37 und den Eingriffsaussparungen 39, 40 der Klauenkupplung 32 komplementär ausgebildeten Reibflächen ein aus Sicherheitsgründen unerwünschtes Ausrücken der Klauenkupplung verhindert.When working with the capstan winch described above, for example in forestry, the support frame 1 is first anchored in place by means of a belt attached to the eyelet 2. Then, with the claw coupling 32 disengaged and the jacket 8 freely rotatable in the opposite direction to the arrow 29, the accruing rope length 30 is pulled with its free end towards the load which is to be brought to the anchorage location of the capstan winch. The running rope length 31 is pulled from a rope storage device, which can either be attached to the support frame 1 to accommodate any desired rope length or is more appropriately separated so that the load rope can also be transported separately from the capstan winch. If the load is then attached to the load rope and the claw coupling 32 is engaged, the capstan head 15 is driven in the arrow direction 29 after the drive motor is switched on, the multiple looping 28 of the load rope without any hindrance to the throughput speed of the individual rope turns during the pulling of the load experiences load-dependent jamming between the rope pressure rollers 49 and the jacket 8. With this drive of the capstan head 15, the frictional surfaces which are complementary on the claws 36, 37 and the engagement recesses 39, 40 of the claw clutch 32 prevent the claw clutch from being disengaged for safety reasons.

In Figur 2 ist für die Antriebswelle 12 des Planetenräderwechselbetriebes noch eine Bremseinrichtung 54 gezeigt, mit der eine zu der Pfeilrichtung 29 bei ausgerückter Klauenkupplung 32 entgegengesetzte Drehung des Mantels 8 gebremst werden kann. Diese Bremsmöglichkeit ergänzt dann die mittels der Seilandrückrollen 51 auf die Mehrfachumschlingung 28 lastabhängig ausgeübte Bremskraft, was im Einzelfall dann von Bedeutung sein kann, wenn die Spillwinde nicht nur für ein horizontales, sondern auch für ein schräges und am Beispiel eines Hebezeuges im Extremfall auch vertikales Bewegen von Lasten eingesetzt wird. Auch bei einem vertikalen Bewegen von Lasten ist selbstverständlich die mittels der Verschiebeführung des Spillkopfes an dem Stützrahmen und mittels der Seilandrückrollen lastabhängig bewirkte Klemmkraft für die Mehrfachumschlingung des Lastseils wieder derart beschaffen, daß in jeder der beiden möglichen Drehrichtungen des Spillkopfes für alle Seilwindungen eine gleiche momentane Durchlaufgeschwindigkeit durch den Spalt zwischen dem Spillkopf und den Seilandrückrollen als Folge einer gleichen momentanen Drehzahlübersetzung erhalten wird.FIG. 2 also shows a braking device 54 for the drive shaft 12 of the planetary gear changing mode, with which a rotation of the casing 8 opposite to the arrow direction 29 when the claw clutch 32 is disengaged can be braked. This braking option then supplements the braking force exerted on the multiple wrap 28 in a load-dependent manner by means of the rope pressure rollers 51, which can be important in individual cases if the capstan winch is not only used for horizontal, but also for inclined and, in extreme cases using a hoist as an example, also vertical movement is used by loads. Even when loads are moved vertically, the clamping force for multiple wrapping of the load rope caused by the displacement of the capstan head on the support frame and by means of the rope pressure rollers is of course such that in all of the two possible directions of rotation of the capstan head the same instantaneous throughput speed for all rope turns is obtained by the gap between the capstan head and the rope pressure rollers as a result of the same instantaneous speed ratio.

Mittels der vorbeschriebenen Einkopf-Spillwinde läßt sich eine Zugkraft bis etwa 1200 kg übertragen. Bei Verwendung von entsprechend leistungsstärkeren Antriebsmotoren und einer dann zweckmäßig stationären Anordnung der Spillwinde kann das Prinzip der lastabhängigen Beeinflussung der auf die Mehrfachumschlingung des Lastseils ausgeübten Klemmkraft auch auf die Übertragung wesentlich höherer Zugkräfte angewendet werden. Für stationäre Anordnungen kann dabei dann für den Spillkopf anstelle einer Lagerung durch eine Verschiebeführung auch eine zu den Seilandrückrollen relativ verschwenkbare Lagerung zur Diskussion stehen, deren Verwirklichung aber aufwendiger ist.The above-described single-head capstan winch can transmit a pulling force of up to 1200 kg. When using correspondingly more powerful drive motors and then a suitably stationary arrangement of the capstan winch, the principle of load-dependent influencing of the clamping force exerted on the multiple looping of the load rope can also be applied to the transmission of significantly higher tensile forces. For stationary arrangements, a bearing that can be pivoted relatively to the rope pressure rollers can then be discussed for the capstan head instead of being supported by a sliding guide, but the implementation thereof is more complex.

Claims (11)

1. A single head capstan winch, comprising a capstan head (15) which is driven by a motor and provided a smooth drum-shaped surface (8) for a multiplicity (28) of power-transmitting windings of a load cable that is held over a partial axial length of said surface by a clamping force acting opposite to the tractive force which when the capstan winch is driven is being effected by a hauling-in load that is coupled to a forward portion (30) of the load cable which is being continuously guided over a larger- sized diameter portion at one axial end of said surface while a rearward portion free of any load of said load cable runs off from a smaller-sized diameter portion at a position intermediate its two axial ends, characterized in that the capstan head (15) is provided with a slide and guide means (5, 6, 42) on a supporting frame (1) and extending in a direction with an acute angle (y) in respect to the tractive force, and in that at least one cable pressing roller (49, 51) is rotatably arranged on said supporting frame (1) for effecting the clamping force by its frictional contact with all windings of said multiplicity (28) of windings of said load-cable, said cable pressing roller having a dynamically balanced surface of a shape that complements the enveloping surface of said multiplicity (28) of windings.
2. A single head capstan winch, comprising a capstan head (15) which is driven by a motor and provided with a smooth drum-shaped surface (8) for a multiplicity (28) of power-transmitting windings of a load cable that is held over a partial axial length of said surface by a clamping force acting opposite to the tractive force which when the capstan winch is driven is being effected by a hauling-in load that is coupled to a forward portion (30) of the load cable which is being continously guided over a larger- sized diameter portion at one axial end of said surface while a rearward portion free of any load of said load cable runs off from a smaller-sized diameter portion at a position intermediate its two axial ends, characterized in that the capstan head (15) is pivotally arranged on a supporting frame (1) relative to at least one cable pressing roller (49, 51) which is rotatably arranged for effecting the clamping force by its frictional contact with all windings of said multiplicity (28) of windings of said load-cable, said cable pressing roller having a dynamically balanced surface of a shape that complements the enveloping surface of said multiplicity (28) of windings.
3. A single head capstan winch according to claim 1 or claim 2 wherein said supporting frame (1) is provided with at least two cable pressing rollers (49, 51) for alternately contacting said multiplicity (28) of windings of said load cable as it is axially shifted on said surface whenever the capstan head (15) changes its direction of rotation.
4. A single head capstan winch according to claim 1, 2 or 3, wherein for each rotational direction of the capstan head (15) two cable pressing rollers (49, 51) are provided as spaced apart over an arc of 90°.
5. A single head capstan winch according to claim 1 wherein said slide and guide means (5, 6, 42) of the capstan head (15) comprises a stop means provided on said supporting frame (1) as optionally adjustable for limiting the clamping force which is effected on the windings of said multiplicity (28) of windings of said load cable to a maximal allowable nipping force.
6. A single head capstan winch according to claim 1 wherein said supporting frame (1) comprises individual brackets (3, 4) that are welded together and provided with two guide rails (5, 6) of a parallel motion guide means for a guide flange (42) of the capstan head (15) and also provided with bearings (50) for said for each cable pressing roller (49, 51).
7. A single head capstan winch according to claim 6 wherein said supporting frame (1) is provided with an eyelet (2) which as an abutment means for the tractive force is arranged in the same alignment.
8. A single head capstan winch according to any of the claims 1 to 7 whereby said capstan head (15) is driven by the connectable output shaft (13) of a planetary gearing and wherein the surface (8) of said capstan head (15) is rotatably arranged on a housing (11) of the planetary gearing which is slidably guided or pivoted on said supporting frame (1) and which is connectable to said output shaft (13) by means of a driving member (33) of a claw clutch (32) that is interconnected with said output shaft in a non-rotatable and axially shiftable manner.
9. A single head capstan winch according to any of the claims 1 to 8 wherein the rotation of the capstan head (15) or its surface (8) may be braked by a braking means (54).
10. A single head capstan winch according to claim 8 wherein said claw clutch (32) is formed with at least two claws (36, 37) on the surface (8) of the capstan head (15) and with two complementary shaped engaging recesses (39, 40) of the driving member (33).
11. A single head capstan winch according to claim 10 wherein said claws (36, 37) and said engaging recesses (39, 40) are provided with complementary shaped friction surfaces that extend in an angular direction in respect to the rotational axis (14) of the capstan head (15).
EP86103392A 1985-03-21 1986-03-13 One drum capstan Expired EP0195983B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT86103392T ATE39676T1 (en) 1985-03-21 1986-03-13 SINGLE HEAD CASTER WINCH.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19853510282 DE3510282A1 (en) 1985-03-21 1985-03-21 SPILL WINCH
DE3510282 1985-03-21

Publications (2)

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EP0195983A1 EP0195983A1 (en) 1986-10-01
EP0195983B1 true EP0195983B1 (en) 1989-01-04

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EP86103392A Expired EP0195983B1 (en) 1985-03-21 1986-03-13 One drum capstan

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US (1) US4666128A (en)
EP (1) EP0195983B1 (en)
JP (1) JPS61221093A (en)
AT (1) ATE39676T1 (en)
CA (1) CA1234093A (en)
DE (2) DE3510282A1 (en)

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US7850146B2 (en) * 2008-06-13 2010-12-14 Production Resource Group, Llc Lineset winch with braking parts

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Also Published As

Publication number Publication date
DE3510282C2 (en) 1987-02-19
CA1234093A (en) 1988-03-15
US4666128A (en) 1987-05-19
EP0195983A1 (en) 1986-10-01
DE3661621D1 (en) 1989-02-09
ATE39676T1 (en) 1989-01-15
DE3510282A1 (en) 1986-10-02
JPS61221093A (en) 1986-10-01

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