EP1125885B1 - Capstan - Google Patents

Abstract

The motor (11) driving the winch drum (2) through a reduction gear, is seated on a mounting (1) inside the winch. The mounting also serves as a bearing for the drum.

Description

The invention relates to a winch for ropes, in particular for running good, such as traps and pods on sailing vessels. Such winches usually have a rotatable winch drum mounted in a direction Holze, which is mounted on a base part, for example on the deck of a boat, mounted Winschfuß- or -sockel. A winch gear drives the winch drum.

There are already known hydraulic or electric motors driven winches known, for example, from the company publication HARKEN Yacht Equipment, 1995 HARKEN Piwaukee, Wisconsin, USA, pages 166-183. The engines are flanged to the underside of the winches, with the disadvantage that the engine-gear unit must be installed below deck and the deck area is weakened by a relatively large opening for the passage of the drive shaft flange. Often, the necessary space is at the for the winch position cheapest place not available and the engine bothers in the passage to aft cabins or in the interior of the sailing yacht. Even with a costly cladding of the engine-transmission unit headroom is often compromised, which involves a particular accident risk in rough seas. A mounting of such a motor winch on a mast to operate the traps is hardly possible.

US 4,084,793 shows a winch with an electric motor disposed inside the drum, which is flanged to the base and drives the winch drum via a gear arranged on top of the winch drum. It is a winch in which one end of the rope to be retrieved is attached to a flange which rotates together with the winch drum. So you can only get as much rope as the winding capacity of the winch drum. For many purposes aboard a ship, therefore, it is not useful, for example as a Schotwinsch, because there, for example. at a turn, the sheet must be thrown completely. Also disturbs the large, the gear-containing head and it is not possible to manual operation.

Task and solution

The object of the invention is to provide a motor winch as compact as possible, in which restrictions with respect to mounting locations are largely eliminated.

This object is achieved by a winch with the features of claim 1.

Due to the fully integrated mounting of the motor within the winch body, which does not need to be larger than that of a manually operable winch, all restrictions in the assembly are eliminated. The winch can be mounted at the point where the trouble-free running of the ropes to be operated by her, such as traps or pods, is guaranteed and where she disturbs the least on deck. It is only necessary to lay the supply lines, which can usually be done between the deck structure and a ceiling panel of the cabin. The attachment to the mast is possible with a standard winch console.

When equipped with an electric motor, a control unit is provided with a starting contactor, which is controlled via a low-current control circuit from an operating switch on the deck. The controller may further include an overcurrent fuse similar to a circuit breaker that serves to limit a maximum pull force in addition to the fuse function. Because of the proportionality between traction and power consumption overloading of the rope or the associated sails can be prevented even if accidentally too long operation.

When talking about ropes above, so are all elongated, flexible tension elements meant that can be placed around a winch drum.

The motor takes place in a tubular support body and can be mounted there with the axis of rotation parallel to the axis of rotation. The tubular support body on which the winch drum can be mounted via needle bearings, at the same time represents an equally lightweight and stable support structure for the winch drum and transmits the forces acting on the winch considerable rope forces well on the winch.

Preferably, the winch on an additional manual drive, which, as in mechanical winches, via a pluggable into the upper winch head winch handle is actuated. The drive shaft for this can protrude eccentrically through the engine compartment and so pass the slightly eccentric motor.

To allow the motor winch to get a free-end rope in a continuous process without an operator engages mechanically to tighten the rope, a known Selbstholeinrichtung can be used, which forms the head of the winch drum and in the Rope is introduced via a guide. Preferably, the width of the gripping groove is variable in order to adapt to different rope diameters can, wherein the lower Nutbegrenzung an upper flange of the winch drum may be and the upper Nutbegrenzung a resiliently axially movable annular disc.

The motor may be a gear motor with an integrated motor gear, for example a planetary gear, which forms a gear precursor. The motor itself is preferably a DC shunt motor which has a very favorable speed / torque characteristic in the present case, i. its torque increases as the speed decreases. Due to a high idling speed of the order of 14,000 revolutions per minute, it can bring high performance with a small size. The gear pre-stage sets this speed down three to five times, so that the desired winch drum idling speed of about 80 - 100 revolutions per minute is achieved in the downstream winch gear stages with low gear number. With a winch drum diameter in the order of 100 mm, this results in a Seilholgeschwindigkeit between 25 and 30 meters per minute; for the application on yachts an ideal value.

The winch gear and the motor gear are preferably not self-locking spur gear, compared to commonly used worm gears also have a very good efficiency. This is especially true when preferred the winch gear runs in an oil bath, which can be designed maintenance-free by appropriate lubricants for life. This eliminates the time-consuming and difficult on-board periodic winch maintenance.

The winch gear can preferably be arranged in the base and contain three gear levels, each forming a gear stage. These can be made up of at least two disks stacked one above the other like a disk be, wherein one of the boards may be formed by the support body for the winch drum. Preferably, the transmission direction is from bottom to top, ie the motor shaft projects through to the end of the winch socket and the individual gear stages are built on it, so then the last gear with a transmission gear reach the inner edge of the winch drum and can drive this.

Freewheel lock prevent one hand, a reverse rotation of the winch drum and on the other hand ensure that the motor drive the manual drive train does not run, so not accidentally plugged winch handle leads to the risk of accidents. Advantageously, it is also provided that a freewheel uncouples the engine during manual operation so that it does not need to be rotated.

Previous motor-driven winches are exclusively for retrieving a rope, that is, to promote in one direction provided. However, there is often the need to fieren a rope or to skew, that is controlled something to relax. This is especially necessary for trimming the sails. According to a preferred embodiment of the invention, the winch may be provided with a finning device containing an electrical control device with which the rope under tension can be loosened. The electric motor can be used as a regulated brake.

Since because of the return of the winch drum and thus the drive of the manual drive can not be disconnected easily via a freewheel, in this case, the manual drive is preferably connectable via a manually operable clutch.

In order to perform a reverse rotation of the winch drum against the direction Holrichtung, the winch drum freewheel must be turned off. This can be done by electrical actuation, for example by electromagnets or electric servomotors, which disengage the pawls of the freewheel during the reverse rotation process and hold there. Because the pawls are normally braced when the winch is under the tension of the rope, this tension can be overcome by first driving the engine slightly in the haul direction, for example a fraction of the amount corresponding to a locking pitch, and then the Latches are disengaged. Then, when the winch drum turns back under the pull of the rope, the motor runs backwards. After reaching a predetermined reverse speed, which can be monitored via a speed sensor, the controller can turn on a braking resistor, which limits the Rückdrehdrehzahl characterized in that now the engine is running as an engine brake. This electrical braking resistor does not need to be designed too large, since the reversing function is usually limited to a slight release.

This is also advantageous for other types of motor winches, new Fiuer device by an independent of the operating switch for fetching button. But it can also be used other control devices, such as a joystick. After the cable has been released and the return switch has been released, the control device for re-engaging the winch drum freewheel can drive the engine back to the home direction until the winch drum has almost reached standstill or even runs slightly in the direction of travel, thus avoiding the release of the pawls click too hard.

If the cable is running in the opposite direction to the wood direction, it could happen that it runs out of the self-tailing device. Therefore, a resilient retaining lever is preferably provided on the Selbstholeinrichtung, behind which the rope is placed and the considerable circumferential distance from the guide, i. the guide finger, which lifts the rope from the winch drum in the Selftail groove is arranged. Thus, the rope is guided on both sides of the Selftail groove and it is effective in both directions. This novel retention lever is also advantageous for other winches with return function.

The rope adheres to the winch on the outer surface of the winch drum by friction with self-reinforcing, ie the applied by the Selbstholeinrichtung initial cable is amplified over several turns of the rope on the winch drum respectively. Conventional winch drums are roughened or knurled on the outside to increase the friction factor. This is not very rope-friendly and damages its surface. It has also become known to provide the winch drum with numerous uniform distributed over the circumference longitudinal ribs. It has now been found within the scope of the invention that in winches of all kinds, a particularly good ratio between holding power and rope protection can be achieved if longitudinal ribs are provided in pairs with relaively large circumferential distance from each other, with a few closely spaced ribs alternate with large circumferential distances, for example, at the periphery of four groups of relatively two closely spaced ribs are present. As a result, the rope is brought into a relatively clear polygonal shape, of course, with rounded sides, which ensures good power transmission with less rope stress.

These and other features will become apparent from the claims and from the description and drawings, wherein the individual features each alone or more in the form of sub-combinations in one embodiment of the invention and in other fields be realized and advantageous and protectable Represent embodiments for which protection is claimed here. The subdivision of the application into individual sections as well as intermediate headings does not restrict the general validity of the statements made thereunder.

Brief description of the drawings

Fig. 1

eine perspektivische Darstellung einer winsch nach der Erfindung verbunden mit einem elek-trischen Schaltbild,

Fig. 2

einen schematischen Längsschnitt durch die Winsch,

Fig. 3 bis 6

schematische Querschnitte nach den Schnittlinien III-III-VI-VI in Fig. 2,

Fig. 7 und 8

durch ein Detail im Kreis VII-VIII in Fig. 2,

Fig. 9 und 10

elektrische Schaltbilder,

Fig. 11 bis 14, 15 bis 18 und 19 bis 22

jeweils drei Varianten einer Schaltmechanik für manuellen Betrieb und

Fig. 23

eine Draufsicht auf den Winschkopf.

Embodiments of the invention are illustrated in the drawings and will be explained in more detail below. In the drawings show:

Fig. 1

a perspective view of a winsch according to the invention connected to an electric circuit diagram,

Fig. 2

a schematic longitudinal section through the winch,

Fig. 3 to 6

schematic cross sections along the section lines III-III-VI-VI in Fig. 2,

FIGS. 7 and 8

by a detail in the circle VII-VIII in Fig. 2,

FIGS. 9 and 10

electrical diagrams,

11 to 14, 15 to 18 and 19 to 22nd

each three variants of a switching mechanism for manual operation and

Fig. 23

a top view of the winch head.

Detailed description of preferred embodiments

Figure 1 shows a winch 11, which is intended for the fetching and enforcement of ropes, such as pods or traps of sailboats. It is attached to a mast with a winch foot or base 12 on the deck 13, cockpit shroud or, usually by means of a console.

A cord 15 shown in broken lines is guided in several turns from bottom to top around a winch drum 14. The winch drum consists of a substantially cylindrical or slightly conical winch drum surface 16, on the circumferentially at greater distances from one another groups of two substantially vertical ribs 17 are pronounced outwards. These may also be slightly inclined, in accordance with the inlet and cable guidance properties.

To the winch drum surface 16 is closed down a bell-shaped winch drum base 18, which has a substantially larger diameter than the winch drum 16 and the obliquely downward connecting surface between a lower cylindrical portion 19 and the winch drum surface 16 forms an inlet guide surface 20 for the cable 15 , The cylindrical portion 19 engages over there offset upper portion of the winch base 12 and together with this forms a cylindrical body.

The upper free end of the winch is formed by a winch head 21, which includes a Selbsthol- (Selftail) device 22. This is formed by a circumferential gripping groove 23, which, as is apparent in particular from FIGS. 7 and 8, is variable in its groove width. The two nutbegrenzenden gripping bodies are on the one hand formed by a flange 24 at the upper end of the winch drum and on the other hand by an annular disc 25 which guided by means of guide pins 26 in the direction of the winch axis 28 and pressed by compression springs 27 in the position shown in Figure 7 with the smallest gripping groove 23 becomes.

From Figure 1 it can be seen that the cable 15 after its last turn to the winch drum 16 via a mounted on one of the top of the winch covering the winch cover 29 guide finger, which forms a guide 30 for the rope, and then into the gripping groove 23rd is inserted, which adjusts itself according to the respective rope thickness against the force of the compression spring (27) and the rope engages under this pressure force. Since the smallest diameter of the circumferential gripping groove is slightly larger than the diameter of the winch drum, so exerts the rope during rotation of the winch drum in Holrichtung (clockwise) a pulling force on the rope, whereby the guided around the winch drum cable turns tightly pulled around this and be taken by her. They tighten with increasing load more tightly around the drum and are thereby, possibly supported by a slight taper, also pressed against each other and against the inlet guide surface 20. The winch can therefore transmit large rope forces gently.

In the winch cover 29 is offset from the eccentric Winch axis 28, a Winchkurbelnuß 32 provided in a conventional winch handle for manual operation can be inserted. While normally the rope in the gripping groove rotates almost a complete revolution until shortly before the guide 30, where it is deflected out of the groove by an ejector 33, in a later described embodiment with reference to FIGS. 10 to 23 a retaining device 34 with a retaining lever 35 is provided appropriate. This is, as shown in FIG. 23, pivotally mounted in the winch cover about an axis parallel to the winch axis 28 formed by one of the cap screws 45 and resiliently supported by a spring 125 and has a hook 15 extending under the gripping groove cross-hook shape. A retaining lug 36 holds the rope in the gripping groove, while it is peeled off from the gripping groove by the hook opening 37 and the adjoining hook shank 38. This retainer ensures that in later described manner, the rope when firing, ie at a winch drum rotation in Fierrichtung 39 (counterclockwise), is not thrown out of the gripping groove.

Fig. 2 shows the internal structure of the winch with its gear 84 in conjunction with Figures 3 to 6, which represent individual transmission levels and levels. The winch base 12 is formed of two superimposed transmission plates 50, 51 which form a closed and sealed to the outside and compared to the rest of the winch interior, two-part gear chamber 40 which receives an oil bath, which provides for the lubrication of the transmission.

Arranged over the blanks is a winch support body which is in the form of a thin-walled tube having a cylindrical portion 41, a slightly enlarged space 43 for the third gear stage, and a flange 144. At the upper free end, an inner flange is provided in the screws 45 protrude that hold the winch head 29 and end cap.

On the cylindrical portion 41 of the support body 44, the winch drum 14 is mounted by means of needle bearings 46, in its upper and lower portion. This results in a very good power transmission with low material costs. A plastic friction washer 48 receives the pulling forces of the rope acting down on the winch drum. Through the flange 43 of the support body 44 and the two gear plates 50 and 51 reaching screws 49 are used to attach the winch on deck 13th

The tubular cylindrical portion 41 of the support body 44 surrounds a likewise cylindrical engine compartment 47, which extends from the upper transmission plate 51 to the winch head 21. In this room, an electric geared motor 52 is arranged. He has an elongated shape and is in the engine compartment 47 with the winch axis 28 parallel motor axis 53, slightly off-center offset, arranged, flanged onto the upper transmission plate 51.

The motor 52 is a shunt DC motor that reaches very high speeds of up to 14,000 rpm at idle and this by an internal planetary gear 54 to about 4,000 rev / min. decreases. Under load, the speed goes down under torque increase. This is desirable because both when using as a fall and as a Schotwinsch after initially pulling through the lots, the final Dichtholen should not go too fast.

The motor shaft 55 projects through the third gear stage 42 and the upper gear plate 51 into the lower gear board 50 and is stored there and rotatably connected to a drive pinion 56 which engages in a gear 57 of considerable larger diameter (Fig. 3). In the drawings, the gears are indicated only by their dashed circles drawn partial circles. The gear wheel 57 is non-rotatably mounted on the shaft 58, which protrudes from the first gear plane (board 50) into the second gear plane (board 51), which also forms the second gear stage (FIG. 4). There it is rotatably connected to a pinion 59, which in turn drives a gear 60 with a larger diameter. The gear 60 has a toothed outer rim 61 and a hub 62 which is rotatably connected to a shaft 63.

Between outer ring 61 and hub 62, a pawl freewheel 64 is provided. Three spring-loaded pawls 65 arranged in the vicinity of the circumference of the hub and obliquely projecting beyond the circumference thereof engage in reverse sawtooth-like recesses 66 on the inner periphery of the outer rim 61.

The shaft 63 projects through the upper surface of the circuit board 67 of the transmission plate 51 sealed and carries there rotatably a pinion 68 which drives an intermediate gear 69 which is mounted on a shaft 70. It engages in an internal ring gear 71 on the inner circumference of the winch drum and drives it (FIG. 5).

Fig. 6 shows that on the inner circumference of the winch drum also a sawtooth-like negative toothing 72 is provided, engage in the pawls 73 of the same type as previously described. They are mounted on the support body 44 and thus form a pawl freewheel 75 for the winch drum, which locks them against reverse rotation.

In the first gear stage (FIG. 3), a gear 77 driven by a pinion 76 is also mounted. The pinion 76 is rotatably provided with a drive shaft 98 for mechanical actuation, which is connected via a square adapter 99 (FIG. 2) with the winch crank nut 32. The shaft 98 is parallel, but eccentric to the winch axis 28 through the engine compartment 47, close to the Tragkörperwandung 41, so that in the engine compartment 47 sufficient space for the engine remains.

The gear 77 also includes a pawl freewheel 78 and is constructed in the same manner as the freewheel 64 of outer rim 79, hub 80, pawls 81 and inner helical teeth 82. The hub sits on the shaft 70 and also drives the idler gear 69.

The electrical connection of the winch is shown schematically in FIG. 9: Positive and negative supply lines 87, 88 coming from an on-board battery 86, possibly via main switches and fuses, lead to a control unit 89 which contains a contactor 90 and an overcurrent switch 91 in the positive line , The relay 90 is, optionally via an auxiliary relay, driven by a low power circuit 92 in which a control switch 93 is located for the winch. The control dial 89 may be located below a suitable location and the control switch 93 is preferably a robust and protected against moisture and possibly by a lid against accidental operation button, which is mounted in the vicinity of the winch on deck.

The winch operates as follows: The cable 15 is in the manner shown in Fig. 1 around the winch drum and is introduced via the guide nose into the gripping groove 23. By Pulling on the rope end 85, the rope can be ridden through, for example, to quickly catch up with a sheet after a turning maneuver. The winch drum can rotate freely in the direction of travel 31, because the pawl freewheel 75 (FIG. 6) runs freely in this direction without the transmission having to follow it.

If it is to be fetched then motor, the operation switch 93 is pressed. The contactor 90 is activated via the control circuit 92. This attracts and via the overcurrent switch 91, the motor 52 is set in motion. It drives the shaft 55 (FIG. 2) via the planetary gear 54 and thus the pinion 56 in the first, lower gear stage 50 (FIG. 3). The directions of rotation of the gear wheels in the horizontal direction 31 are indicated by arrows. Via the gear 57, which forms with the pinion 56, the first winch gear stage, the shaft 58 and the pinion 59 in the second gear stage (board 51 in Fig. 4), the gear 60 is driven. From the direction of rotation arrow (counterclockwise) can be seen that while the freewheel 64 locks and accordingly the hub 62 and the shaft 63 are taken. Thus, in the third gear stage (FIG. 5), the shaft 63 drives the pinion 68 and thus the idler gear 69, so that the winch drum 14 is rotated in the home direction 31 (clockwise).

In the manner described above, the rope is held taut by the Selbstholeinrichtung 22 at its expiring end, so that it lays firmly around the winch drum and the rope is obtained with considerable tensile forces. The size of this force depends on the one hand, how often the rope is placed around the winch drum and on the other hand limited by the pulling force of the engine. However, this can be so great because of the engine characteristics that a risk to the Rope or tightly fetched good (sail) could exist if the control button is not released in time. In this case, even in the case of complete blockage, but the motor takes on such a high current that the overcurrent switch 91 triggers and stops the engine. The tension of the rope is maintained. In the case of a permanent engine overload, a thermal motor protection in the form of a bimetallic switch is provided in the motor 52.

After switching off the engine, the pawls 73 of the winch drum freewheel 75 again engage in the toothing 72 formed by pawl segments and thus lock the winch drum mechanically against reverse rotation. Engine and gear train are relieved.

During engine operation, the gear train was automatically turned off for manual operation. Although the shaft 70 (Figure 3) rotated in a clockwise direction, the free wheel 78 caused the gear 79 to not rotate. Correspondingly, the pinion 76 and the drive shaft 98 stood. An accidentally plugged onto the Winchkurbelnuss 32 winch crank so does not rotate, which could otherwise have led to the risk of accidents.

On the other hand, when the winch crank is operated (counterclockwise), the gear 79 is rotated clockwise (see dashed direction arrows in Fig. 3). Thus, the freewheel 78 locks again and the shaft 70 is clockwise, i. in collection direction 31, taken away. The winch drum 14 can thus be rotated manually with a reduction corresponding to the gears 76 and 79.

The motor gear train does not need to be rotated, since with stationary or slower rotating engine Freewheel 64 when driving the hub 62 in the counterclockwise direction, the gear 60 free run.

Due to this automatic "transfer" between the two drive types, it is even possible to "help" with the winch crank during engine operation, without any mechanical damage or risk of accidents being feared.

It can be seen that by the exclusive use of spur gears and their arrangement in an oil bath, the transmission efficiency is very good. Together with the use of a high-revving engine and the strong gear reduction, large tractive forces can be generated with a small engine. Also contributes to the reduction, that the internal gear ring 71 transmitting the rotational force to the winch drum is close to the largest diameter of the winch drum, while the effective winch drum surface 16 has a smaller diameter.

In this embodiment, if the rope is to be completely loosened, it is led out of the gripping groove 23 and the end left loose, so that the windings on the winch drum relax and release the rope. The same is also to be done, if the rope is only slightly solved or the rope tension is to be reduced a little. In this case, the operator must give the end of the rope very carefully and then tighten again immediately and put it into the gripping groove of the self-tapping device 22 so as not to let down too much.

An explained with reference to Figures 10 to 23 advanced embodiment of the nut screw according to the invention makes it possible to make even the fieren or chopping the rope by motor.

This embodiment is the same in the winch area as the previously described embodiment, but with the following additions:

The yawing or squirming, during which the rope under tension can be loosened or released, must be controlled. A jerky, uncontrolled easing is e.g. not to use for trimming the sails. Therefore, in this embodiment, the motor is used as a brake. Accordingly, it is likewise driven in the opposite direction during a reverse rotation of the winch drum 14 in the direction of the fins 39 (FIG. 1). The freewheel 64 allows this reverse rotation, since it remains engaged.

However, in order to preclude unwanted rotation of a winch crank plugged onto the winch crank nut, the gear design is changed as shown in FIGS. 11 to 22.

They show three different versions of a connection mechanism 100 for the mechanical drive. Common to these versions, that instead of the freewheel 78, a manually operated rocker switch 101 is provided, which is mounted pivotably about the manual drive axle 98. The seated on this shaft pinion 102 drives an intermediate pinion 103 which is freely rotatably mounted on the rocker switch. The rocker is in the form of a fork lever (see Figures 11, 15 and 19). Between the two fork legs, the pinions 102, 103 run.

The rocker switch 101 may be engaged by an operating handle 104 (Figs. 13, 17 and 21) or disengaged (Figs. 14, 18 and 22) with the idler gear 69 which drives the winch drum. It can not only be the Freewheel 78, but also the gear 79 omitted. To ensure that the engine operation of the winch (in both directions) is only possible when the mechanical drive is off, a microswitch 105 is provided which is located in the control circuit and only closes the control circuit when the mechanical drive is off and thus enables the electrical winch functions.

In that regard, the functions in all three embodiments according to the Figurne 11 to 14, 15 to 18 and 19 to 22 are the same. Different is the type of mechanical operating handle 104 and its arrangement.

In the embodiment of Figures 11 to 14 of the operating handle is formed as a spring plate 104a, which protrudes from the winch base through a cutout 106a and is pivotable between the positions shown in Figures 13 and 14. He snaps into upper detent recesses under his spring force, which set the two end positions. To operate the spring plate is pressed down and can then be pivoted. On the spring plate, an operating knob can be placed.

The embodiment according to FIGS. 15 to 18 has, for pivoting the rocker 101, a separate, teardrop-shaped actuating lever 104b, which is mounted so as to be pivotable about an axis 107 within a segment cutout 106b by approximately 180 °. A driving pin 108 runs in a fork groove 109 on the rocker 101 and pivots the rocker between the positions shown in Figures 17 and 18. This design provides a large translation for the operation, ensures that the actual operating lever 104b is indeed accessible through the cutout 106b, but does not protrude beyond the scope of the winch and at the same time ensures a Locking in the end positions, because in particular when the operating handle is slightly rotated over 180 °, which is possible in the arrangement in the segment-shaped groove, a self-assurance occurs.

The embodiment according to FIGS. 19 to 22 has an operating handle 104c in the form of an actuating button, which in the unactuated state (manual drive switched off) is recessed in a segment-shaped cutout 106c (FIG. 22) but can be gripped and pulled out so that an oblique surface 110 on the operating handle 104 together with a pin on the rocker 101 this releases for engagement in the gear 69. The pivoting of the rocker can be effected by a spring 130. Further, in all versions, an additional contact force between the gears 103 and 69 is made by bringing the reaction forces acting on the gears together themselves.

The engine winch with filler device works with the following procedure: Under engine operation, the winch works to fetch as described previously. If the winch is to be operated manually, which is provided only in the direction Holer, the manual gear train is turned on the described with reference to Figures 11 to 22 Zuschaltmechanismus 100 and by turning the winch handle in a clockwise direction, the shaft 98, the pinion 102 and 103 and over Intermediate gear 69 turned the winch drum. In this state, the microswitch 105 is open and therefore an engine operation is excluded. Because of the freewheel 64, the engine is not rotated.

The Rückhol- or Fierfunktion is controlled by means of an electronic flow and control control via a logic module (Eprom). This is in a control device 112 integrated, which is shown schematically in Fig. 10 and is located in the control unit 89. For this function, in addition to the circuit components shown in Fig. 9, the following are still present: An operating switch 113 for the Fierfunktion belonging to the control circuit, the already described micro switch 105 on the mechanical actuation mechanism and an electromechanical turn-off device for the winch drum freewheel 75th This consists, as indicated by dashed lines in Fig. 6, from the control circuit controllable electromagnets or servomotors, which can retrieve the pawls 79 of the winch drum freewheel against its spring force and thus release the winch drum 14 for rotation in both directions. The control 116 takes place via control lines 117.

In the control unit 89 or outside of this, a braking resistor 118 is provided, which closes the motor circuit via a controllable by the controller 112 contactor or relay 119.

The sequence is now as follows: When the return operation switch 113 is actuated, the motor is briefly approached in the direction of travel by the control device 112 in order to release the previously loaded and thus jammed pawls 73 of the winch drum 14. The engine is started by means of preset speed pulses, controlled by a pulse generator on the motor. The pawls 73 of the winch drum freewheel 75 (FIG. 6) are disengaged via the switch-off devices 116 and held in this position.

The motor is switched off again. Under the train of the rope, the winch drum now begins to turn in Fierrichtung 39. The engine is powered by and turns in Counter direction to its normal direction of rotation until a preset Abwindungsdrehzahl is reached. This is monitored via the pulse generator 120 on the engine or in the gear train. Upon reaching the Abwindungsdrehzahl the relay 119 is closed, so that now the resistor 118 is charged by the motor acting as a generator and the engine thus acts as an engine brake. The winch drum thus rotates with a controlled speed braked backwards. Optionally, could be adjustable by a corresponding control or, for example, the choice of different resistances, the tailwind speed.

To end the FViervorganges the button of the control switch 113 is released. Thereafter, under the control of the control device 112, the motor is briefly turned on again until the reverse rotation is decelerated by the now forward-going motor and the direction of rotation of the winch drum is in the reversing process, i. goes to zero. This is also reported via the pulse generator to the control device and this causes the magnets or actuators of the switch-off device 116, the pawls 73 solve again so that they can come under their spring force in the toothing 72 of the drum and secure them again. This completes the downwinding process. The braking of the reverse rotation causes the process is not abruptly interrupted and the drum is not abruptly stopped from the reverse rotation by the pawls, which could lead to wear or damage.

As already mentioned with reference to FIG. 1, the retaining device 34 serves to retain the cable 15 even in the event of a reverse rotation in the gripping groove 23 of the self-tending device 22 and to prevent the rope end from becoming free and the loop around the winch drum solves. It is thus avoided that the cable suddenly collapses in Fieren and after Fiervorgang the rope is ready to fetch again.

It is thus created by the invention, a winch, which is particularly suitable as Sdhot- or fall winch for sailing yachts, etc. It has an integrated electric or hydraulic drive, whereby the engine is integrated into the winch so that it lies within the winch body and in particular within the winch drum. He causes via a lying in the winch base multi-stage gearbox, possibly supported by a present in the engine planetary gear, the rotation of the winch drum. A manual operation with a winch crank is possible by a winch crank nut in the winch head, wherein the manual drive shaft passes the slightly off-set motor.

It can be provided a Rückdreh- or Fierfunktion in which after switching off the Trommelgesperres the engine is braked back and at a controlled speed.

Claims (14)

1. Capstan for ropes (15), particularly for runners, such as falls and sheets on sailing vessels, having

   1.1 a capstan drum (14) rotatable at least in one hauling direction (31),

   1.2 a capstan foot fittable to a base part (13),

   1.3 a capstan gear (84),

   1.4 an engine (52), which is at least partly located in an engine compartment (47) surrounded by the capstan drum (14) and driving the capstan drum (14) via the gear,
   characterized in that

   1.5 the engine compartment (47) is located in a substantially tubular supporting body (44) on which the capstan drum (14) is mounted in rotary manner and

   1.6 the engine (52) is mounted thereon with an engine axis (53) parallel to the rotation axis (28) of the capstan drum (14).
2. Capstan according to claim 1, characterized in that it has an additional manual drive, which is preferably operable by means of a capstan crank by a lid-like capstan head (29) covering the capstan drum (14), a drive shaft (98) for the manual drive running past the engine (52) optionally eccentrically positioned in the engine compartment (47).
3. Capstan according to claim 1 or 2, characterized in that it has a self-hauling device (22) tightening the rope (15) running off the capstan drum (14) during hauling and which is positioned close to the free end of the capstan drum (14) and has a circumferential gripping groove (23) and said gripping groove (23) preferably has two spacing-variable gripping bodies (24, 25) axial to the capstan drum (14) and whereof in particular one is constructed as a flange of the capstan drum (14) and the other as a resiliently axially movable ring disk (25).
4. Capstan according to one of the preceding claims, characterized in that the engine is constructed as a geared electric engine (52) with an integrated engine gear serving as a gear driving stage and which reduces by three to five times the speed of the engine preferably constructed as a direct current shunt-wound engine, which has an idling speed of above 10,000 rpm, particularly approximately 14,000 rpm, prior to introduction into the capstan gear (84).
5. Capstan according to one of the preceding claims, characterized in that the capstan gear (84) and engine gear (54) are preferably constructed as non-self-locking spur gear sets, the capstan gear (84) more particularly running in a maintenance-free oil bath.
6. Capstan according to one of the preceding claims, characterized in that the capstan gear (84) is located in the capstan foot (12) and contains three gear planes, which in each case form a gear stage, and contains at least two, disk-like, superimposed stacked plates (50, 51) and optionally the third gear stage is contained in a compartment mounting the capstan drum (14) formed by the supporting body (44) surrounding the same.
7. Capstan according to one of the preceding claims, characterized in that it is operable by means of an electric, manually connectable control (89) having at least one contactor (90) and an overcurrent fuse (91) for limiting the maximum tensile force.
8. Capstan according to one of the claims 2 to 8, characterized in that it has at least two of the following freewheels:

   8.1 a capstan drum freewheel (75) allowing a rotation of the capstan drum (14) in the hauling direction (31), but prevents a rotating back counter to the hauling direction,

   8.2 a first gear freewheel (64) connecting in the gear run between the engine and the gear connection of the manual drive and uncoupling the engine (52) during manual operation,

   8.3 a second gear freewheel (78) provided in the manual drive run and uncoupling the same during engine operation.
9. Capstan according to one of the preceding claims, characterized in that it has a slackening device with an electric control device (112) enabling a tensioned rope (15) to be loosened or relaxed, the engine (52) being used as an optionally regulated brake.
10. Capstan according to one of the preceding claims, characterized in that a manual drive disconnects the capstan during engine operation and during manual operation connects it in by means of a manually operable connection mechanism (100).
11. Capstan according to claim 9 or 10, characterized in that the capstan drum freewheel (75) can be freely connected by control device (112) by means of electrical operation, so that the capstan drum (14) can be rotated in both rotation directions, the free connection in particular taking place through an electromagnetic or electromechanical raising of retaining pawls (73) of a ratchet wheel and pawl forming the freewheel (75) and in which optionally the free connection takes place after engine operation in the hauling direction (31) for releasing the retaining pawls (73).
12. Capstan according to claim 11, characterized in that the engine (52) can be rotated back by the capstan drum (14) rotated back under the tension of the rope (15) and the control device (112) contains a brake resistor (118), which is connected in by the control device (112) at a given return speed and the control device, optionally following manual disconnection of the slackening device, controls the engine in the hauling direction (31) until the capstan drum (14) is virtually stationary and it then connects in the freewheel (75) again.
13. Capstan according to one of the preceding claims, characterized in that the self-hauling device (22) contains a retaining device (34) which retains the rope (15) also in the case of slackening in the self-hauling device and preferably has a resilient retaining lever (35), which, in the rope running direction, is circumferentially spaced from a guiding device (30), which guides the rope from the capstan drum into the self-hauling device (22).
14. Capstan according to one of the preceding claims, characterized in that the capstan drum (14) on its outer surface (16) serving as a contact surface with respect to the rope has circumferentially spaced groups of preferably two roughly axially parallel ribs (17).

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