EP2627600B1 - Capstan comprising means of assessing the tension of a line wrapped around it and means of automatically selecting at least one speed according to said tension - Google Patents

Description

1. Field of the invention

The field of the invention is that of the design and manufacture of nautical equipment.

More specifically, the invention relates to a capstan intended to be secured to a sailboat for tensioning an integral end of a sail. This type of capstan is commonly referred to as a "winch".

2. Prior Art

Winches are commonly used on sailboats to allow their crew to tension the ends connected to the sails.

A winch conventionally includes a frame housing a drive shaft, a gearbox. A doll, connected to said shaft via the gearbox, is rotatably mounted on the frame.

In order to stretch one end, it is wrapped around the doll, then the shaft is rotated by means of a crank so that the doll rotates around the building: the end then wraps around the doll and stretches.

There are essentially two types of winches: two-speed winches and three-speed winches.

The first gear is the one that allows to wrap the tip as quickly as possible. The higher speeds respectively allow to wind up the tip less quickly than in the previous speed but exerting less force on the crank so as to compensate for the fact that as the end is wrapped around the winch, its voltage increases.

In two-speed winches, shifting is achieved by a teammate by reversing the direction of rotation of the crank.

In the three-speed winches, the passage from the first to the second speed is obtained, by a teammate, by reversing the direction of rotation of the crank, then the passage from the second to the third speed is obtained by the crew member by acting, if necessary, on a push button provided for this purpose on the winch and reversing the direction of rotation of the crank.

The current winches are effective. They make it possible to tension one end while adapting the effort to be provided for this purpose by a team member given the implementation of a gearbox.

These winches nevertheless have some disadvantages.

3. Disadvantages of prior art

To engage the third gear, the winches of the prior art have the disadvantage of requiring to reverse the direction of rotation of the crank and to actuate a push-button provided on the winch. This tends to complicate the maneuvers of the crew, evolving in a difficult context (rough sea, crowded bridge).

In practice, the crew members do not generally wind up one end around the doll of a winch by operating the crank at the first speed, then at the second speed, then if necessary at the third speed. moving from the lower to the higher gear when their force no longer allows to wind the end to the lower gear. According to a different approach, after a certain tension is exerted on the end in first gear, they wind the end passing alternately from the first to the second speed then, when the winch offers a third gear alternately passing from the second to the third gear by rotating the crank in one direction and then in the other over a range of about 30 ° around a starting position. This action is commonly called "pumping" in the field of sailing. This reduces the angle of movement of an arm around the winch and the arm to exert a force on the winch in an angular range in which it is the most powerful.

In winches with three speeds, the passage of a pumping between the first and second speeds to a pumping between the second and third speeds requires to engage the third gear and therefore to actuate the push button provided for this purpose. This complicates the maneuver.

The European patent application bearing the number EP-A1-0 159 095 describes a three-speed winch in which the passage from one speed to another is obtained by reversing the direction of rotation of the crank without the need to act on a button to go from the second to third gear . According to the technique described, a rotation of the crank clockwise allows to operate the winch in first gear, a rotation of the crank counterclockwise allows to operate the winch in second gear, then a rotation of the crank again in clockwise allows to operate the winch in third gear.

The technique described in this document has the advantage of allowing to engage the third speed by simply reversing the direction of rotation of the crank without the need to operate in addition to a push button. This technique, however, has the disadvantage of not allowing the crew to pump between the first and second speeds and between the second and third speeds.

There is no winch that allows to pump between the first and second speeds then between the second and third gear by acting only on the direction of rotation of the crank.

The current winches also do not allow to adapt, the power of the arm of the team member in charge of the rotation of the crank of the winch, the passage of pumping between the first and second speeds pumping between the second and third speeds .

Assuming that there is still tension on one end, the winch designers of the prior art have always offered winches whose ratio of each speed was a ratio of reduction.

Gear transmissions can provide, depending on the manner in which they are implemented, reduction ratios or multiplication ratios. When the ratio of a transmission is a reduction ratio, the speed at the output of the transmission is lower than the input speed while the output torque is greater than the input torque. Conversely, when the ratio of a transmission is a ratio of multiplication the output speed is greater than the speed of entry.

In winches of the prior art, the torque generated on the doll for wrapping a tip is greater than the torque exerted by a team member on the crank for winding process, regardless of the speed engaged.

As a result, the winding speed of the tip at the first speed is slow while the tension in the tip is low (usually a crank turn corresponding to half a doll turn). Thus, in practice, the crew puts the end around the doll by hand by pulling on the free end thereof to accelerate the tensioning of the end.

The current winches therefore do not allow both to provide a rapid winding speed of the end and large winding torques.

The current winches do not allow to select automatically a speed according to the tension of the end wrapped around the winch The selection of speed is on the contrary systematically operated by a teammate by modifying the direction of rotation of the crank and if necessary by activating a pushbutton. This tends to complicate the maneuvers of the crew, evolving in a difficult context (rough sea, crowded bridge).

No winch can also adapt the speed ratio to the tension in the end.

4. Objectives of the invention

The invention particularly aims to overcome these disadvantages of the prior art.

More precisely, an object of the invention is to provide, in at least one embodiment of the invention, a capstan which makes it possible to adapt at least one speed to the tension in the end wrapped around.

Another objective of the invention is to provide, in at least one embodiment, such a capstan that allows a crew member to automatically switch from a pumping between a first and a second speed then between the second and a third gear only by reversing the direction of rotation of the crank.

Another object of the invention is to provide, in at least one embodiment, such a capstan in which it is possible to adapt to the strength of the crew member the passage of a pumping between the first and the second speed. then between the second and the third gear.

Another objective of the invention is to implement, in at least one embodiment, such a capstan in which the selection of at least one speed is obtained automatically taking into account the tension of the end wrapped around.

An object of the invention is to provide, in at least one embodiment, a capstan in which the passage from one speed to another is obtained only by acting on the crank without the need to actuate other control means such as a push button.

The invention also aims to provide, in at least one embodiment, such a compact capstan.

Another object of the invention is to propose, in at least one embodiment, such a capstan which is ergonomic.

Yet another object of the invention is to provide, in at least one embodiment, such a capstan which is inexpensive.

5. Presentation of the invention

• un bâti fixe logeant un arbre et une boîte de vitesses ;
• une poupée autour de laquelle peut être enroulé ledit bout, ladite poupée étant montée mobile en rotation en sens unique autour dudit bâti et reliée audit arbre via ladite boîte, la mise en rotation dudit arbre s'accompagnant d'une mise en rotation de ladite poupée autour dudit bâti.

These objectives, as well as others that will appear thereafter, are achieved by means of a capstan intended to be secured to a sailboat to tension a fixed end of a sail, said capstan comprising:

• a fixed frame housing a shaft and a gearbox;
• a doll around which can be wound said end, said doll being rotatably mounted in one-way around said frame and connected to said shaft via said box, the rotation of said shaft accompanied by a rotation of said doll around said frame.

According to the invention, such a capstan comprises means for evaluating the said tip and means for selecting at least one speed when said voltage becomes greater than a predetermined threshold, said gearbox comprising an inner ring, said ring being rotatably mounted inside said doll against the effect of means exerting a friction force and / or elastic return on said ring so that it can rotate relative to said doll when said voltage is greater than said threshold.

The invention thus provides an original capstan in which at least one of the speeds is selected automatically according to the tension in the end wrapped around the doll. This makes it possible to adapt the effort to be provided by a team member putting a tension on one end to his physical condition.

The technique of the invention thus facilitates maneuvers crew members of a sailboat.

Thus, when the torque exerted on the doll by the end becomes greater than the torque exerted on the crown by the crew member via the drive means and the gearbox and the friction force and / or return between the crown and the doll, the crown turns inside the doll, that is to say that the crown and the doll turn relative to each other. This rotation then gives an indication of the level of tension in the tip.

In this case, said selection means are preferably movable between at least one rest position and a selection position of at least one speed, said ring acting on said automatic selection means to place them in one or the other. of their positions.

The rotation of the crown relative to the doll, which means that the tension in the end has reached a certain value, makes it possible to act on the selection means so that one or more adapted speeds, for example a third speed, are engaged.

A capstan according to the invention preferably comprises means for transforming a displacement of said ring relative to said doll in a movement of said means for selecting from one to the other of their positions.

This ensures accurate and efficient selection in a simple way.

A capstan according to the invention advantageously comprises means for adjusting said threshold value.

It is thus possible to adapt the capstan to the strength of its user by modifying the value of the threshold voltage in the end from which the tripping occurs.

According to an advantageous characteristic, said ring comprises a contact surface having a ramp, and in that said means exerting a frictional force on said doll comprise a finger secured to said doll and bearing against said contact surface under the effect said elastic return means.

Thus, when the torque exerted for the end on the doll becomes greater than the friction force of the finger on the ramp, the ring rotates inside the doll.

Said adjustment means preferably comprise a screw having a foot and a head, said biasing means being interposed between said finger and said foot, said head being accessible from outside said doll.

It is thus possible to easily adjust the threshold value by acting from outside the capstan on the screw provided for this purpose without the need to disassemble the capstan. A capstan according to the invention therefore has the advantage of being ergonomic.

In the example of a three-speed winch, if the user is strong, the threshold voltage value will be important so that he can pump between the first and second speeds longer. If the user is weaker, the threshold voltage value will be decreased so that the passage of pumping between the first and second speeds pumping between the second and third speeds occurs faster to relieve the user. This principle is applicable to winches with more than three speeds.

According to an advantageous embodiment, said crown comprises a hollow housing, and in that said means exerting a frictional force on said doll comprises an elastic finger integral with said doll and whose end is adapted to be housed in said hollow housing.

This embodiment has the advantage of being simpler to implement than that in which the crown comprises a ramp on which a finger acts.

According to an advantageous embodiment, said box is a three-speed gearbox, said automatic selection means being means for selecting the third gear, and in that the rotation of said shaft in one direction or the other s accompanied by a rotation of said doll around said frame at a speed or another.

The invention therefore proposes an original three-speed capstan in which the passage from one to the other of the speeds is obtained by modifying the direction of rotation of the driving means, for example a crank, without being necessary to act in addition to a push button. In addition, the third gear engages automatically as soon as the tension in the end reaches a certain value. The invention thus provides a three-speed capstan in which the passage of a pumping between the first and second speeds to a pumping between the second and third speeds is obtained by acting only on the direction of rotation of the drive means.

Preferably, the first speed of said box at a multiplication ratio, the second and third speeds having reduction ratios.

In a completely novel way, a capstan according to the invention has a first speed, also called boarding speed, whose ratio is greater than one. In other words, when the capstan is actuated at first speed, the number of turns made by the doll is greater than the number of turns made by the drive means for a given number of turns of the actuating means. A capstan according to the invention therefore makes it possible to wind more quickly one end around the doll that the capstans of the prior art, each speed has a ratio less than one.

In advantageous embodiments, said selection means are means for selecting third and fourth speeds.

When the tension in the tip is low, the doll can be rotated in one direction according to a first and a second speed. When the tension in the end becomes significant, the doll can be rotated in one direction according to a third and a fourth speed. It will then be possible to switch from a pumping between the first and second speeds to a pumping between the third and fourth speeds.

In an advantageous embodiment, said shaft comprises a first shaft portion and a second shaft portion, said second shaft portion being connected to said ring by a plurality of gears so that a rotation of said second shaft portion shaft portion in one direction or the other causes a rotation of said doll in a direction in two different transmission ratio, said first shaft portion being connected to at least one gear train, said selection means setting in direct engagement with said first shaft portion and said second shaft portion when they occupy one of their position, said selection means engaging said first shaft portion and said second shaft portion via one of said first shaft portions; 'gears when they occupy another of their position.

When the tension in the tip is low, the doll can be rotated in one direction according to a first and a second speed. When the tension in the end becomes significant, the doll can be rotated in this direction according to at least two other speeds. It will then be possible to switch from a pumping between the first and second speeds to a pumping between the third and fourth speeds. In variants, the system could be multiplied to pass if necessary pumping between the third and fourth speeds to a pumping between a fifth and sixth speeds, etc.

In an advantageous embodiment, said shaft is connected to said ring by a plurality of gears so that a rotation of said shaft in one direction or the other causes a rotation of said doll in a direction in two transmission ratios. different, said shaft being further connected to the input of a multiplier gear train whose output is connected to the input of the plurality of gears by a one-way clutch, said selection means engaging the output of said multiplier gear train with the input of the plurality of gears when in their rest position, said selecting means not engaging the output of said multiplier gear train with the input of the plurality of gears; gears when they occupy their other position.

Thus, a simple way of rotating the doll at a first speed by the rotation of the shaft in one direction, a rotation of the doll according to a second speed by the rotation of the shaft in the other direction, a rotation of the doll according to a third speed by the rotation of the tree in the first sense.

According to an advantageous characteristic, said shaft comprises a first end to which drive means can be connected, said gearbox comprising a first pinion connected by means of a first unidirectional clutch to a second end of said shaft, said first pinion meshing a second gear rotatably mounted on a first axis integral with said frame, said second gear meshing with an inner ring integral with said headstock, a third gear being secured to said second end of said shaft, said third gear meshing with a fourth gear rotatably mounted around a second axis secured to said frame, said fourth pinion meshing with a fifth gear connected to said first axis by means of a second one-way clutch, said capstan further comprising a multiplier having an input connected to said shaft and an output connected to said first gear by means n of a third unidirectional clutch, said automatic selection means being able to assume a holding position of said third unidirectional clutch in the disengaged position when said voltage is greater than said threshold, the first, second and third unidirectional clutches being configured so that a rotation in a first direction of said shaft enables it to transmit a torque to said ring via said multiplier, said third unidirectional clutch, said first and second pinion, a rotation of said shaft in another direction allows it to transmit a torque to said ring via the first and second gears, a rotation in said first direction of said shaft while said voltage is greater than said threshold allows it to transmit torque to said ring via the third, fourth and fifth gears.

In this case, said ring is preferably mounted to rotate between two extreme positions inside said doll against the effect of said elastic return means, said ring acting on said automatic selection means so that the passage of the one to the other of said extreme positions of the ring against the effect of said return means is accompanied by the passage of said selection means in said holding position.

According to an advantageous characteristic, said multiplier, said third unidirectional clutch and said automatic selection means are removable.

Disassembly of these elements provides a conventional two-speed winch. A winch according to the invention therefore has a modular design that reduces the cost of manufacturing.

According to an advantageous characteristic, a capstan according to the invention comprises means for actuating said shaft, said actuating means comprising a coffee grinder or a crank whose one end is complementary to said first end of said shaft

It is thus possible to provide a capstan according to the invention with a crank and to place it in a position in which its shaft extends essentially vertically so that it constitutes a winch. It is still possible to equip it with a coffee grinder and place it in a position in which tree extends essentially horizontally in such a way that it constitutes a coffee grinder or a pedestal.

6. List of figures

• la figure 1 présente une vue de face d'un cabestan selon l'invention ;
• la figure 2 illustre une vue en coupe longitudinale du cabestan illustré à la figure 1 ;
• la figure 3 illustre une vue en coupe selon l'axe C-C du cabestan illustré à la figure 2 ;
• la figure 4 illustre une vue en coupe selon l'axe D-D du cabestan illustré à la figure 2 ;
• la figure 5 illustre une vue en coupe selon l'axe E-E du cabestan illustré à la figure 2 ;
• la figure 6 illustre une vue en coupe selon l'axe F-F du cabestan illustré à la figure 2 ;
• la figure 7 illustre une vue en coupe selon l'axe H-H du cabestan illustré à la figure 2 ;
• les figures 8 et 9 illustrent des vues en perspective du cabestan illustré à la figure 2 dans lesquelles la poupée n'est représentée qu'en partie ;
• les figures 10 et 11 illustre deux vues en coupe longitudinale d'un deuxième mode de réalisation d'un winch selon l'invention;
• la figure 12 illustre une vue en coupe selon l'axe F-F du winch illustré à la figure 10 ;
• la figure 13 illustre une vue en coupe selon l'axe G-G du winch illustré à la figure 11 ;
• la figure 14 illustre une vue en perspective d'un deuxième élément d'embrayage d'un winch selon le deuxième mode de réalisation ;
• la figure 15 illustre une vue en coupe selon l'axe C-C du winch illustré à la figure 10 ;
• la figure 16 illustre une vue en coupe selon l'axe D-D du winch illustré à la figure 10 ;
• la figure 17 illustre une vue en coupe selon l'axe E-E du winch illustré à la figure 11 ;
• la figure 18 illustre une vue en perspective d'un deuxième portion d'arbre d'un winch selon le deuxième mode de réalisation ;
• la figure 19 illustre une vue de face d'un winch selon un troisième mode de réalisation de l'invention ;
• les figures 20 et 21 illustrent deux vues en coupe selon l'axe A-A du winch illustré à la figure 19 ;
• la figure 22 illustre une vue en coupe selon l'axe E-E du winch illustré à la figure 19 ;
• la figure 23 illustre une vue en coupe selon l'axe B-B du winch illustré à la figure 19 ;
• la figure 24 illustre une vue en coupe selon l'axe C-C du winch illustré à la figure 20 ;
• la figure 25 illustre une vue en coupe selon l'axe F-F du winch illustré à la figure 20.

Other characteristics and advantages of the invention will appear more clearly on reading the following description of a preferred embodiment, given as a simple illustrative and nonlimiting example, and the appended drawings, among which:

• the figure 1 has a front view of a capstan according to the invention;
• the figure 2 illustrates a longitudinal sectional view of the capstan shown in FIG. figure 1 ;
• the figure 3 illustrates a sectional view along the axis CC of the capstan illustrated in FIG. figure 2 ;
• the figure 4 illustrates a sectional view along the axis DD of the capstan illustrated in FIG. figure 2 ;
• the figure 5 illustrates a sectional view along the axis EE of the capstan illustrated in FIG. figure 2 ;
• the figure 6 illustrates a sectional view along the FF axis of the capstan shown in FIG. figure 2 ;
• the figure 7 illustrates a sectional view along the axis HH of the capstan illustrated in FIG. figure 2 ;
• the figures 8 and 9 illustrate perspective views of the capstan shown in figure 2 in which the doll is only partially represented;
• the Figures 10 and 11 illustrates two views in longitudinal section of a second embodiment of a winch according to the invention;
• the figure 12 illustrates a sectional view along the FF axis of the winch illustrated in FIG. figure 10 ;
• the figure 13 illustrates a sectional view along the axis GG of the winch illustrated in FIG. figure 11 ;
• the figure 14 illustrates a perspective view of a second clutch member of a winch according to the second embodiment;
• the figure 15 illustrates a sectional view along the axis CC of the winch illustrated in FIG. figure 10 ;
• the figure 16 illustrates a sectional view along the axis DD of the winch illustrated in FIG. figure 10 ;
• the figure 17 illustrates a sectional view along the EE axis of the winch illustrated in FIG. figure 11 ;
• the figure 18 illustrates a perspective view of a second shaft portion of a winch according to the second embodiment;
• the figure 19 illustrates a front view of a winch according to a third embodiment of the invention;
• the figures 20 and 21 illustrate two cross-sectional views along the AA axis of the winch illustrated in figure 19 ;
• the figure 22 illustrates a sectional view along the EE axis of the winch illustrated in FIG. figure 19 ;
• the figure 23 illustrates a sectional view along the BB axis of the winch illustrated in FIG. figure 19 ;
• the figure 24 illustrates a sectional view along the axis CC of the winch illustrated in FIG. figure 20 ;
• the figure 25 illustrates a sectional view along the FF axis of the winch illustrated in FIG. figure 20 .

7. Description of an embodiment of the invention 7.1. Recall of the principle of invention

The general principle of the invention is based on the implementation of a multi-speed capstan intended to be secured to a sailboat for tensioning an integral end of a sail, and which comprises means for evaluating the tension one end wound around and means for selecting at least one speed when the voltage becomes greater than a predetermined threshold.

The invention thus provides an original capstan in which at least one of the speeds is automatically selected as a function of the voltage in the end wrapped around the doll. This makes it possible to adapt the effort to be provided by a team member putting a tension on one end to his physical condition.

The technique of the invention thus facilitates maneuvers crew members of a sailboat.

7.2. Example of a first embodiment of a capstan according to the invention 7.2.1. Architecture

The figure 1 illustrates a front view of a capstan 10 according to the invention. Such a capstan 10 comprises a frame 11 on which is mounted rotatably a doll 12. The frame 11 is intended to be secured for example on the deck of a sailboat. A tip whose end is connected to a sail of the sailboat can be wrapped around the doll 12. This capstan 10 conventionally comprises a reversible imprisonment device 13 with one end of the end to be wrapped around the doll 12.

The figure 2 is a sectional view of the capstan 10 shown in FIG. figure 1 .

As it appears on this figure 2 , the doll 12 comprises an upper doll element 121 and a lower doll element 122.

The capstan comprises a shaft 14 rotatably mounted in the frame 11. The shaft 14 comprises an upper end 141. This upper end 141 is secured to the inlet 15 of the capstan. The inlet 15 has a grooved portion 151 provided to cooperate with means for actuating the capstan. These actuating means may comprise a crank. In a variant, they may include "a coffee grinder". The drive means may also be motorized.

The input 15 constitutes the satellite carrier of a first epicyclic gear train 16 (cf. figure 3 ). This first epicyclic gear train 16 comprises six satellites 161, 162, 163, 164, 165, 166, a fixed ring gear 167 and a sun gear 168. This first epicyclic gear train 16 performs the function of an inverter as will be explained in more detail below. .

The sun gear 168 is secured to the satellite door 170 of a second train epicyclic 17 (cf. figure 4 ). This second epicyclic gear train 17 comprises three satellites 171, 172, 173, a fixed ring gear 174 and a sun gear 175. This second epicyclic gear train 17 provides the multiplier function as will be explained in more detail below.

The sun gear 175 is integral with a first element 181 of a one-way clutch 18. This unidirectional clutch 18 comprises a second element 182. The first element carries pawls 183 movable between a gripping position in which they cooperate with the second element 182. such that the first 181 and second 182 elements are rotatably connected, and a release position in which the first 181 and second 182 elements are not rotationally connected.

The second element 182 and secured to a first pinion 19.

The shaft 14 has a lower end 142. The first pinion 19 is secured to the lower end 141 of the shaft 14 by means of another unidirectional clutch 20.

The first pinion 19 meshes with a second pinion 21 rotatably mounted on an axis 22 secured to the frame 11.

The second pinion 21 meshes with an inner ring 23 secured to the inside of the upper doll element 121.

A third pinion 24 is secured under the first pinion 19 at the lower end 142 of the shaft 14. This third pinion 24 meshes with a fourth pinion 25 mounted to rotate about an axis 251 integral with the frame 11. This fourth pinion 25 engages a fifth gear 26 which is rotatably mounted on the axis 22. The fifth gear 26 is connected to the second gear 21 by means of another unidirectional clutch 27.

• une première position, illustrée aux figures 6 et 8, dans laquelle le ressort de compression 30 est relâché en sorte que le pion 28 vient en butée contre une extrémité 291 de la cavité 29 ;
• une deuxième position, illustrée à la figure 9, dans laquelle le ressort de compression 30 est comprimé entre le pion 28 et une autre extrémité 292 de la cavité 29 sous l'effet de la rotation de la couronne 23 à l'intérieur de l'élément de poupée supérieur 121.

The ring 23 is rotatably mounted inside the upper doll element 121. The ring 23 comprises a pin 28 projecting from its periphery. This pin 28 is extended in a recess 29 in the form of a circular arc formed in the lower doll element 122. This cavity 29 houses a compression spring 30. The crown 23 is thus rotatable within the upper doll element 121 between two extreme positions:

• a first position, illustrated in figures 6 and 8 wherein the compression spring 30 is released so that the pin 28 abuts against an end 291 of the cavity 29;
• a second position, illustrated in figure 9 in which the compression spring 30 is compressed between the pin 28 and another end 292 of the cavity 29 under the effect of the rotation of the ring 23 within the upper doll element 121.

The ring 23 comprises a contact surface 31 having a ramp 310.

The upper doll element 121 has a cavity 32. The crown 23 also has a cavity 33 whose bottom is formed by the contact surface 31. The cavities 32 and 33 house a finger 46 which is mounted therein to move in translation according to a axis parallel to the axis of the shaft 14. This finger 46 has a ramp of complementary shape of the ramp 310 of the contact surface 31. It is held in abutment against the contact surface 31 by means of a spring of compression 34, which is interposed between the finger 46 and the foot 351 of a screw 35 which is housed in a tapping 36 formed in the upper head member 121. The head 352 of this screw 35 is accessible from outside the the doll.

An elevator 37 is housed in a housing of complementary shape formed in the ring 23 so that the elevator 37 and the ring 23 are rotatably connected.

The elevator 37 comprises a cylindrical portion 371 which extends above the ring 23. Three lights 372 are arranged and distributed uniformly in the cylindrical portion 371. These lights 372 are inclined so that they constitute ramps 373.

Three grooves 38 are arranged and uniformly distributed inside the upper doll element 121. They extend parallel to the axis of the shaft 14.

Three elevator pins 39 extend inside the grooves 38 and 372. They are integral with a transition ring 40 mounted to move in translation inside the cylindrical portion 371 along the axis of the shaft 14.

The transition ring 40 is connected by pins 41 to an elevation ring 42. The shafts 41 pass through slots provided for this purpose in the frame 11 and which extend along an axis parallel to the axis of the tree 14.

A pusher element 43 is slidably mounted along the second element 182. A compression spring 44 is interposed between the elevation ring 42 and the pusher element 43.

The pusher element 43 has in the upper part a flange 431 designed to cooperate with the ends 184 of the pawls 183 of the one-way clutch 18.

A ball bearing 45 is interposed between the frame 11 and the upper doll element 121 so as to ensure the rotational guidance of the doll 12 relative to the frame 11.

7.2.2. Operation

A fluted portion of actuating means, such as a crank or a coffee grinder, is introduced into the fluted portion 151 of the capstan inlet 15.

A teammate can then wrap one end around the doll 12 at three different speeds by rotating the drive means.

A. First gear

When the drive means cooperating with the ribbed portion 151 is rotated clockwise, the shaft 14 rotates clockwise. The sun gear 168 is rotated via the satellites 161, 162, 163, 164, 165, 166 in the counterclockwise direction. The satellite gate 170 then rotates counterclockwise. The sun gear 175 is driven via the satellites 171, 172, 173 in the counterclockwise direction at a speed greater than the rotational speed of the shaft 14.

The first element 181 unidirectional clutch 18, which is secured of the sun gear 175, also turns counterclockwise. The pawls 183 cooperate with the second unidirectional clutch element 182 so that the latter rotates in the counterclockwise direction. The first pinion 19, which is secured to the second element 182 of unidirectional clutch 18, is then rotated in the opposite direction of clockwise. The second gear 21 rotates clockwise and drives the crown 23 in this direction. The doll 12 then rotates around the frame 11 in the direction of clockwise. In this case, the unidirectional clutches 20 and 27 respectively linking the first pinion 19 to the shaft 14, and the second pinion 21 to the fifth pinion 26 rotate in a vacuum.

When the effort to be applied by a team member on the drive means to continue the winding of the end around the doll becomes too important given the tension of the end, a second speed can be used.

B. Second speed

The passage from the first to the second speed is obtained by reversing the direction of rotation of the activation means.

The inlet 15 of the capstan and the shaft 14 then turn counterclockwise. The sun gear 168 is rotated via the satellites 161, 162, 163, 164, 165, 166 in a clockwise direction. The satellite gate 170 then rotates clockwise. The sun gear 175 is driven via the satellites 171, 172, 173 in a clockwise direction at a speed greater than the rotational speed of the shaft 14.

The first element 181 of unidirectional clutch 18, which is integral with the sun gear 175, also rotates in the direction of clockwise. The pawls 183 no longer cooperate with the second unidirectional clutch element 182 so that it is not linked to rotation with the first unidirectional clutch element 181. The first pinion 19 is then rotated anti-clockwise via the one-way clutch 19. The second gear 21 rotates clockwise and drives the crown 23 in this direction. The doll 12 then rotates around the frame 11 in the direction of clockwise. In this case, the unidirectional clutch 27 linking the second gear 21 to the fifth gear 26 rotates in a vacuum.

When the effort to be applied by a team member on the drive means to continue the winding of the end around the doll becomes too important given the tension of the end, a third gear can be used.

C. Third gear C.1 / Selection

When the force applied to the doll 12 by the end wrapped around becomes greater than the sum of the force applied to the doll 12 by the team member via the actuating means and the various gears by which they are connected to the crown 23 and the friction force exerted by the finger 46 via the compression spring 34 on the contact surface 31 of the ring 23, the ring 23 rotates inside the upper doll element 121 against the effect compression spring 30 to reach its second end position in which the pin 28 fully compresses the spring 30 against the end 292 of the cavity 29. The ring 23 passes from its first extreme position illustrated in FIG. figure 8 at its second extreme position illustrated at the figure 9 .

During its clockwise rotation relative to the upper doll member 121, the crown 23 rotates the elevator 37. The elevator pins 39 then move within the lights 372. and up in the grooves 38. The transition ring 40, integral with the lifting pins 39, follows the same movement, as is the lifting ring 42. The lifting ring 42 acts on the pusher element 43 via the spring The flange 431 then acts on the ends 184 of the pawls 183 of the one-way clutch 18. These pawls 183 are then maintained in their position in which they do not cooperate with the second element 182 of unidirectional clutch 18. The first 181 and second 182 clutch elements unidirectional 18 are not connected in rotation.

The third gear is thus selected. However, as the crew continues to rotate the actuating means in the opposite direction of clockwise, the capstan will be implemented at the second speed, the third speed being preselected.

C.2 / Engagement

When the crew member considers that the effort he must provide in the second gear to wind the end becomes too great, he gets the engagement of the third gear by reversing again the direction of rotation of the activation means.

The inlet 15 of the capstan then rotates in a clockwise direction Since the first 181 and second 182 unidirectional clutch elements 18 are not rotationally connected, the shaft 14 rotates the third gear 24 in a clockwise direction. The fourth gear 25 then rotates counterclockwise while the fifth gear 26 rotates clockwise. The fifth pinion 26 rotates in the clockwise direction of the second pinion 21 via the unidirectional clutch 27. The ring gear 23 rotates in this direction. The doll 12 then rotates around the frame 11 in the direction of clockwise In this case, the one-way clutch 20 linking the first pinion 19 to the second pinion 21 rotates in a vacuum.

C.3 / Setting third gear selection

The value of the force applied by the end on the doll which makes it possible to select the third speed can be set. This adjustment is obtained by more or less screwing the screw 35 in the tapping 36 of the doll 12. The more the screw 35 is tightened in the tapping 36, the greater the tension of the tip must be important for the third speed to be cut . Conversely, the less the screw 35 is tightened in the tapping 36, the less the tension force of the tip will be important for the third gear to be selected.

The tension in the end from which the third gear will be selected can therefore be adjusted according to the physical capabilities of the crew member to handle the capstan.

If the crew member has a moderate physical condition, the adjustment can be made so that the effort it will have to provide to wind the end to the second speed before the third gear is selected is average. If the teammate has a better physical condition, the adjustment can be made so that the effort it must provide to wind the end to the second speed before the third gear is selected is more important.

C.4 / Deselection

When the tip is released, the ring 23 returns to its first extreme position under the effect of the compression spring 30 and the pusher member 43 resumes its initial position so that when the drive means are driven in the direction of the squeezes of a watch, the capstan will turn at first speed.

7.2.3. Use in pumping mode

The capstan 10 can be used in pumping mode by a crew member. In this case, the crew rotates the crank in one direction and then the other to move the crank about thirty degrees on either side of an initial position. He then puts the end in tension by pumping between the first and the second speed.

As soon as the tension in the tip is such that the third gear is selected, the crew puts the end into tension by pumping between the second and the third gear.

• d'une vitesse à l'autre, et
• du pompage entre la première et deuxième vitesse à un pompage entre la deuxième et troisième vitesse,

en modifiant uniquement le sens de rotation de la manivelle.The capstan according to the invention therefore makes it possible to pass:

• from one speed to another, and
• pumping between the first and second speeds to pumping between the second and third speeds,

by only changing the direction of rotation of the crank.

The fact of being able to adjust the threshold voltage value from which the third gear engages allows to adapt to the strength of a crew member the effort from which the capstan will switch from pumping between the first and second gear to a pumping between the second and third gear.

In this first embodiment, the box is a three-speed gearbox, and said automatic selection means are means for selecting the third gear, the rotation of said shaft in one direction or the other accompanied by rotating said doll around said frame at one speed or another.

The invention therefore proposes an original three-speed capstan in which the passage from one to the other of the speeds is obtained by modifying the direction of rotation of the drive means, for example a crank, without it being necessary. to act as a complement on a push-button.

In addition, the third gear engages automatically as soon as the tension in the end reaches a certain value. The invention thus provides a three-speed capstan in which the passage of a pumping between the first and second speeds to a pumping between the second and third speeds is obtained by acting solely on the direction of rotation of the drive means.

7.3. Example of a Second Embodiment of a Capstan According to the Invention 7.3.1. Architecture

The Figures 10 and 11 illustrate two views in longitudinal section of a capstan according to a second embodiment.

Such a capstan 10 comprises a frame 11 on which is mounted rotatably a doll 12. The frame 11 is intended to be secured for example on the deck of a sailboat. A tip whose end is connected to a sail of the sailboat can be wrapped around the doll 12. This capstan 10 conventionally comprises a reversible imprisonment device 13 with one end of the end to be wrapped around the doll 12.

The doll 12 includes an upper doll element 121 and an element lower doll 122.

The capstan comprises a first shaft portion 200 rotatably mounted in the frame 11. The first shaft portion 200 comprises an upper end 201. This upper end 201 is secured to the inlet 15 of the capstan. The inlet 15 has a grooved portion 151 provided to cooperate with means for actuating the capstan. These actuating means may comprise a crank. In a variant, they may include "a coffee grinder". The drive means may also be motorized.

The first shaft portion 200 carries a pinion which constitutes the sun gear 202 of an epicyclic gear train. The sun gear 202 meshes with three satellites 203 which are mounted on a planet carrier 204 rotatably mounted on the first shaft portion 200. The satellites 203 meshing with an internal gear 205. The epicyclic gear is here a gear. In a variant, it may be a multiplier.

In a variant in which the epicyclic gear is a multiplier, when the capstan is actuated in first gear, the number of turns made by the doll is greater than the number of turns made by the drive means for a given number of turn means actuating. A capstan according to the invention therefore makes it possible to wind up a tip around the doll more quickly than the capstans of the prior art, each speed of which has a ratio of less than one. This capstan is particularly well suited to winches listening to spinnaker, genoa and mainsail. It authorizes the maneuvers of tacking without ever having to apprehend listening by hand for boarding.

In a variant in which the epicyclic gear train is a gearbox, when the epicyclic gear train is a gearbox, the third and fourth gear have reduction ratios 50% higher than the reduction ratios of speeds one and two. A capstan according to the invention therefore makes it possible to wind with a factor of two times less effort around the doll than the capstans of the prior art, each speed of which has a reduction ratio of 50% less. This winch is particularly well adapted to the halyard winch with which the sails are hoisted at the masthead. The forces to be applied on the drive means are particularly important at the end of hoisting, in particular because of the weight of the mainsail and the friction of the mainsail rails. It is then often necessary to implement electrical drive means winches. The implementation of a gearbox offers an alternative to the electric winch.

The toothed wheel 205 is integral with a first clutch element 206 rotatably mounted on the first shaft portion 200.

The first clutch element 206 comprises a cylindrical lower extension 207. Four housings 208 are formed longitudinally on the peripheral surface of the extension 207. They are distributed uniformly.

The first shaft portion 200 comprises a lower portion 209. A clutch ring 210 is secured in a fixed manner to the lower end of the lower portion 209 by means of grooves 211 of complementary shape formed in the first shaft portion 200 and in the clutch ring 210. Four housings 212 are formed longitudinally on the peripheral surface of the clutch ring 210. They are distributed uniformly.

The capstan comprises a second shaft portion 213. This second shaft portion 213 is rotatably mounted in the frame 11 and extends in the extension of the first shaft portion 200.

The second shaft portion 213 comprises at its upper end a portion forming a bell 214. The bell 214 defines an inner housing 215 inside which are housed the cylindrical lower extension 207 and the clutch ring 210.

The peripheral surface of the bell 214 is traversed by four series of two bores 216. The series are distributed uniformly around the bell 214. The bores 216 of each series extend along an axis parallel to the axis longitudinal section of the second shaft portion 213. There are thus two rows of holes 216.

A first pinion 19 is mounted at the lower end of the second shaft portion 213 by means of a one-way clutch 20.

The first pinion 19 meshes with a second pinion 21 rotatably mounted on an axis 22 secured to the frame 11.

The second pinion 21 meshes with an inner ring 23 secured to the inside of the upper doll element 121.

A third pinion 24 is secured under the first pinion 19 at the lower end of the second shaft portion 213. This third pinion 24 meshes with a fourth pinion 25 mounted to rotate about an axis 251 secured to the frame 11. This fourth gear 25 meshes a fifth gear 26 which is rotatably mounted on the axis 22. The fifth gear 26 is connected to the second gear 21 by means of another unidirectional clutch 27.

• une première position, illustrée aux figures 6 et 8, dans laquelle le ressort de compression 30 est relâché en sorte que le pion 28 vient en butée contre une extrémité 291 de la cavité 29 ;
• une deuxième position, illustrée à la figure 9, dans laquelle le ressort de compression 30 est comprimé entre le pion 28 et une autre extrémité 292 de la cavité 29 sous l'effet de la rotation de la couronne 23 à l'intérieur de l'élément de poupée supérieur 121.

In the same way as in the first embodiment, the ring 23 is rotatably mounted inside the element, upper doll 121. The ring 23 comprises a pin 28 protruding from its periphery. This pin 28 is extended in a cavity 29 in an arc formed in the lower doll element 122. This cavity 29 houses a compression spring 30. The ring 23 is rotatable inside the element of upper doll 121 between two extreme positions:

• a first position, illustrated in figures 6 and 8 wherein the compression spring 30 is released so that the pin 28 abuts against an end 291 of the cavity 29;
• a second position, illustrated in figure 9 in which the compression spring 30 is compressed between the pin 28 and another end 292 of the cavity 29 under the effect of the rotation of the ring 23 within the upper doll element 121.

The ring 23 comprises a contact surface 31 having a ramp 310.

The upper doll element 121 has a cavity 32. The crown 23 also has a cavity 33 whose bottom is constituted by the surface of The cavities 32 and 33 house a finger 46 which is mounted to move in translation along an axis parallel to the axis of the first shaft portion 200. This finger 46 has a ramp of complementary shape to the ramp 310 of FIG. the contact surface 31. It is held in abutment against the contact surface 31 by means of a compression spring 34, which is interposed between the finger 46 and the foot 351 of a screw 35 which is housed in a tapping 36 arranged in the upper doll element 121. The head 352 of this screw 35 is accessible from the outside of the doll.

An elevator 37 is housed in a housing of complementary shape formed in the ring 23 so that the elevator 37 and the ring 23 are rotatably connected.

The elevator 37 comprises a cylindrical portion 371 which extends above the ring 23. Three lights 372 are arranged and distributed uniformly in the cylindrical portion 371. These lights 372 are inclined so that they constitute ramps 373.

Three grooves 38 are formed and uniformly distributed inside the upper doll element 121. They extend parallel to the axis of the first shaft portion 200.

Three lifting pins 39 extend inside the grooves 38 and the slots 372. They are integral with a transition ring 40 mounted to move in translation inside the cylindrical portion 371 along the axis of the first portion 200.

The transition ring 40 is connected by pins 41 to an elevating ring 42. The shafts 41 pass through slots provided for this purpose in the frame 11 and which extend along an axis parallel to the axis of the first portion of tree 200.

A second clutch member 217 is slidably mounted along the second shaft portion 213.

The second clutch element 217 has in the upper part a bell-forming portion 218. The bell 218 defines an inner housing 219 intended to house the bell 214 of the second shaft portion 213.

The inner surface of the bell 218 of the second clutch element 217 has two ramps 220, 221 of inverted inclination and joined by a flat surface 222 parallel to the axis of the first shaft portion 200. The ramps 220, 221 as well as the flat surface 222 define a protruding member 223 inside the bell 218.

The bell 218 is extended by a hollow cylindrical lower portion 224 whose contour is traversed by three oblong slots 225. The oblong slots 225 are uniformly distributed and extend along axes parallel to the axis of the second shaft portion 213 .

A compression spring 44 is mounted between the second clutch element 217 and the lifting ring 42.

The shafts 41 can slide inside the oblong slots 225.

Each piercing 216 houses a ball 226.

• une première position dans laquelle l'élément formant saillie 223 agit sur la première rangée de billes 226, c'est-à-dire la rangée inférieure, en sorte que celles-ci soient logées dans les logements 212 de la bague d'embrayage 210 et que la première portion d'arbre 200 et la deuxième portion d'arbre 213 sont liées en rotation ;
• une deuxième position dans laquelle l'élément formant saillie 223 agit sur la deuxième rangée de bille 226, c'est-à-dire la rangée supérieure, en sorte que celles-ci soient logées dans les logements 208 de l'extension 207 et que l'extension 207 et la deuxième portion d'arbre 213 soient liées en rotation.

The second clutch element 217 is movable between two positions:

• a first position in which the protruding member 223 acts on the first row of balls 226, i.e. the lower row, so that they are housed in the housings 212 of the clutch ring 210 and that the first shaft portion 200 and the second shaft portion 213 are rotatably connected;
• a second position in which the protruding member 223 acts on the second row of balls 226, i.e. the upper row, so that they are accommodated in the housings 208 of the extension 207 and that the extension 207 and the second shaft portion 213 are rotatably connected.

In the first position, the projection member 223 does not act on the second row of balls. In the second position, the protruding element does not act on the first row of balls.

Ball bearings are interposed between the frame 11 and the upper doll element 121 so as to ensure the rotational guidance of the doll 12 relative to the frame 11.

7.3.2. Operation

A fluted portion of actuating means, such as a crank or a coffee grinder, is introduced into the fluted portion 151 of the capstan inlet 15.

A teammate can then wrap one end around the doll 12 at several different speeds by rotating the drive means:

A. First gear

At the beginning of the winding of one end around the doll, the tension exerted by the end on the doll is low so that the crown 23 occupies its first position and the second clutch element 217 occupies its first position.

When the drive means cooperating with the fluted portion 151 are rotated counterclockwise, the first shaft portion 200 rotates counterclockwise. The first clutch member 206 is rotated about the first shaft portion 200 in a clockwise direction via the sun gear 202, the satellites 203 and the inner gear 205.

Because the second clutch member 217 occupies its first position, the first clutch member 206 is not engaged with the second shaft portion 213.

The clutch ring 210 is engaged with the second shaft portion 213 because the second clutch element acts on the balls 226 of the first row so that they are housed in the corresponding housings 212 of the clutch ring 210. The second shaft portion 213 is thus rotated in the counterclockwise direction.

The first pinion 19 is rotated counterclockwise via the unidirectional clutch 20.

The second pinion 21 is rotated clockwise by the first pinion 19.

The inner ring 23 is driven in rotation in the direction of the needles by the second gear 21. The doll then rotates clockwise at a first speed. In this embodiment, the reduction ratio of the first speed is equal to 0.5. In variants, it could be different.

The third pinion 24 is rotated anti-clockwise by the second shaft portion 213. The fourth pinion 25 is rotated clockwise by the third pinion 24. The fifth pinion 26 is rotated counterclockwise by the fourth pinion 25. The rotational movements of the fifth pinion 26 and the second pinion 21 are loosened due to the implementation of the clutch. unidirectional 27.

B. Second speed

When the effort to be printed on the drive means becomes too great, the teammate can reverse the direction of rotation of the drive means to engage a second speed. The team then rotates the drive means in the direction of clockwise.

The first shaft portion 200 is rotated in a clockwise direction. With the second clutch member 217 still in its first position, the second shaft portion 213 is also rotated clockwise.

The third pinion 24 is rotated in a clockwise direction by the second shaft portion 213.

The fourth pinion 25 is driven counterclockwise by the third pinion 24.

The fifth pinion 26 is rotated in a clockwise direction by the fourth pinion 25.

The second pinion 22 is rotated clockwise via the fifth pinion 26 and the unidirectional clutch 27.

The doll then rotates clockwise at a second speed. In this embodiment, the reduction ratio of the second gear is equal to 0.167. In variants, it could be different.

The first pinion 19 is rotated counterclockwise by the second pinion 22. The rotational movements of the first pinion 19 and the first shaft portion 213 are loosened due to the implementation of the unidirectional clutch 20.

C. Selection

When the force applied to the doll 12 by the end wound around becomes greater than the sum of the force applied to the doll 12 by the crew member via the actuating means is the different gears by which they are connected to the crown 23 and the friction force exerted by the finger 46 via the compression spring 34 on the contact surface 31 of the ring 23, the ring 23 rotates inside the upper doll element 121 against the effect compression spring 30 to reach its second end position in which the pin 28 fully compresses the spring 30 against the end 292 of the cavity 29. The ring 23 passes from its first extreme position illustrated in FIG. figure 8 at its second extreme position illustrated at the figure 9 .

During its clockwise rotation relative to the upper doll member 121, the crown 23 rotates the elevator 37. The elevator pins 39 then move within the lights 372. and up in the grooves 38. The transition ring 40, integral with the lifting pins 39, follows the same movement, as well as the lifting ring 42. The axes 41 slide inside the lights 225 of the second element. Clutch 217. The lifting ring 42 acts on the second clutch element 217 via the compression spring 44. The second clutch element 217 then moves from its first position to its second position.

The second clutch element 217 then acts on the balls 226 of the second row so as to place it in the corresponding recesses 208 of the first clutch element 206. The balls 226 of the first row are then no longer housed in the housings 212 of the clutch ring 210. The first clutch element 206 is engaged with the second portion shaft 213 so that they are linked in rotation.

Third and fourth speeds are thus selected.

D. Third gear

When the second clutch member 217 moves from its first position to its second position, and the teammate reverses the direction of rotation of the drive means by driving the latter counterclockwise, the doll 12 rotates around the frame 11 according to a third gear.

The first shaft portion 200 is rotated counterclockwise. The planet 202 follows the same movement. The satellites 203 are rotated in the clockwise direction. They drive in the same direction the inner gear wheel 205 and the first clutch element 206.

With the first clutch element 206 engaged with the second shaft portion 213, the latter is rotated in a clockwise direction.

The third pinion 24 is rotated in a clockwise direction by the second shaft portion 213.

The fourth pinion 25 is driven counterclockwise by the third pinion 24.

The fifth pinion 26 is rotated in a clockwise direction by the fourth pinion 25.

The second pinion 22 is rotated clockwise via the fifth pinion 26 and the unidirectional clutch 27.

The doll then turns clockwise at a third speed. In this embodiment, the reduction ratio of the third speed is 0.083. In variants, it could be different.

The first pinion 19 is rotated counterclockwise by the second pinion 22. The rotational movements of the first pinion 19 and the second shaft portion 213 are loosened due to the implementation. of the unidirectional clutch 20.

E. Fourth speed

When the second clutch element 217 moves from its first position to its second position, and the team member rotates the drive means in a clockwise direction, the doll 12 rotates around the frame 11 according to a fourth gear.

The first shaft portion 200 is rotated in a clockwise direction. The planet 202 follows the same movement. The satellites 203 are rotated in the anti-clockwise direction. They drive in the same direction the inner gear wheel 205 and the first clutch element 206.

The second clutch element 206 being engaged with the second shaft portion 213, the latter is rotated in the counterclockwise direction.

The first pinion 19 is rotated counterclockwise via the unidirectional clutch 20.

The second pinion 21 is rotated clockwise by the first pinion 19.

The inner ring 23 is driven in rotation in the direction of the needles by the second pinion 21. The doll then rotates clockwise at a fourth speed. In this embodiment, the reduction ratio of the fourth speed is equal to 0.24. In variants, it could be different.

The third pinion 24 is rotated anti-clockwise by the second shaft portion 213. The fourth pinion 25 is rotated clockwise by the third pinion 24. The fifth pinion 26 is rotated counterclockwise by the fourth pinion 25. The rotational movements of the fifth pinion 26 and the second pinion 21 are loosened due to the implementation of the clutch. unidirectional 27.

F. Setting selection

The value of the force applied by the end on the headstock which makes it possible to select the third and fourth speeds by placing the toothed wheel 23 and the second clutch element 217 in their respective second position can be adjusted by screwing more or less the screw 35 in the tapping 36 of the doll 12 according to the principle explained in connection with the first embodiment.

G. Deselection

When the end is released, the ring 23 returns to its first extreme position under the effect of the compression spring 30 and the second clutch member 217 resumes its first position so that when the drive means are rotated in Either way, the capstan will turn at the first or second speed.

H. Pumping

When the tension exerted by the end on the doll is low enough so that the third and fourth speeds are not engaged, the teammate can drive the doll in rotation according to the first or second speed in the direction of rotation of the drive means . It can also alternately rotate the drive means on a reduced angular range in one direction and then in the other. He then gets a winding of the end by pumping between the first and the second speed.

When the tension exerted by the end on the doll is large enough so that the third and fourth speeds are engaged, the teammate can drive the doll in rotation according to the third or fourth speed in the direction of rotation of the drive means. It will also be able to pump between the third and fourth speeds.

When the third and fourth speeds are engaged, if the teammate continues to rotate the drive means in a clockwise direction, it will cause the doll to rotate at the fourth speed. If it reverses the direction of rotation, it will cause the doll in rotation according to the third speed.

Given the reduction ratios of different speeds, pumping between the first and the second speed is substantially symmetrical to the pumping between the third and the fourth speed. Thus, the amplitude of effort observed between the first and second speeds is substantially equal to the magnitude of effort between the third and fourth speeds. In other words, the contrast of the forces between the first and second speeds is equivalent to the contrast of the forces between the third and fourth speeds.

7.4. Example of a third embodiment of a capstan according to the invention 7.4.1. Architecture

We present in relation with the Figures 19 to 25 a capstan according to a third embodiment.

Such a capstan 10 comprises a frame 11 on which is mounted rotatably a doll 12. The frame 11 is intended to be secured for example on the deck of a sailboat. A tip whose end is connected to a sail of the sailboat can be wrapped around the doll 12. This capstan 10 conventionally comprises a reversible imprisonment device 13 with one end of the end to be wrapped around the doll 12.

The doll 12 comprises an upper doll member 121 and a lower doll member 122.

The capstan comprises a first shaft portion 200 rotatably mounted in the frame 11. The first shaft portion 200 comprises an upper end 201. This upper end 201 is secured to the inlet 15 of the capstan. The inlet 15 has a grooved portion 151 provided to cooperate with means for actuating the capstan. These actuating means may comprise a crank. In a variant, they may include "a coffee grinder". The drive means may also be motorized.

The first shaft portion 200 carries a pinion which constitutes the sun gear 202 of an epicyclic gear train. The sun gear 202 meshes with three satellites 203 which are mounted on a satellite gate comprising a satellite gate element upper 204 'and a lower stellite door member 204 rotatably mounted on the first shaft portion 200. The satellites 203 mesh with an inner gear wheel 205 fixedly mounted in the frame 11. The epicyclic gear is here a gear. In a variant, it may be a multiplier.

In a variant in which the epicyclic gear is a multiplier, when the capstan is actuated in first gear, the number of turns made by the doll is greater than the number of turns made by the drive means for a given number of turn means actuating. A capstan according to the invention therefore makes it possible to wind up a tip around the doll more quickly than the capstans of the prior art, each speed of which has a ratio of less than one. This capstan is particularly well suited to winches listening to spinnaker, genoa and mainsail. It authorizes the maneuvers of tacking without ever having to apprehend listening by hand for boarding.

In a variant in which the epicyclic gear train is a gearbox, when the epicyclic gear train is a gearbox, the third and fourth gear have reduction ratios 50% higher than the reduction ratios of speeds one and two. A capstan according to the invention therefore makes it possible to wind with a factor of two times less effort around the doll than the capstans of the prior art, each speed of which has a reduction ratio of 50% less. This winch is particularly well adapted to the winch of halyards with which the sails are hoisted at the masthead. The forces to be applied on the drive means are particularly important at the end of hoisting, in particular because of the weight of the mainsail and the friction of the mainsail rails. It is then often necessary to implement electrical drive means winches. The implementation of a gearbox offers an alternative to the electric winch.

The lower satellite gate element 204 comprises, in its lower part, complementary coupling elements of coupling elements formed on a transmission ring 300. The transmission ring 300 is thus rotationally connected to the transmission element. lower satellite door 204. Housing suitable for receiving balls 301 are provided in the lower part of the transmission ring 300.

The capstan comprises a second shaft portion 213. This second shaft portion 213 is rotatably mounted in the frame 11 and extends in the extension of the first shaft portion 200.

The second shaft portion 213 comprises at its upper end grooves complementary grooves formed inside a cylindrical pusher element 302 mounted on the second shaft portion 213 slidably movable along the axis of the second shaft portion 213. The pusher element 302 is thus rotatably connected to the second shaft portion 213.

The lower part of the winch according to this second embodiment is similar to the lower part of the winches according to the first and second embodiments.

A first pinion 19 is thus mounted at the lower end of the second shaft portion 213 by means of a unidirectional clutch 20.

The first pinion 19 meshes with a second pinion 21 rotatably mounted on an axis 22 secured to the frame 11.

The second pinion 21 meshes with an inner ring 23 secured to the inside of the upper doll element 121.

A third pinion 24 is secured under the first pinion 19 at the lower end of the second shaft portion 213. This third pinion 24 meshes with a fourth pinion 25 mounted to rotate about an axis 251 secured to the frame 11. This fourth gear 25 meshes a fifth gear 26 which is rotatably mounted on the axis 22. The fifth gear 26 is connected to the second gear 21 by means of another unidirectional clutch 27.

• une première position dans laquelle le ressort de compression 30 est relâché en sorte que le pion 28 vient en butée contre une extrémité 291 de la cavité 29 ;
• une deuxième position dans laquelle le ressort de compression 30 est comprimé entre le pion 28 et une autre extrémité 292 de la cavité 29 sous l'effet de la rotation de la couronne 23 à l'intérieur de l'élément de poupée supérieur 121.

The ring 23 is rotatably mounted inside the upper doll element 121. The ring 23 comprises a pin 28 projecting from its periphery. This pin 28 is extended in a cavity 29 in an arc formed in the lower doll element 122. This cavity 29 houses a compression spring 30. The ring 23 is rotatable inside the element of upper doll 121 between two extreme positions:

• a first position in which the compression spring 30 is released so that the pin 28 abuts against an end 291 of the cavity 29;
• a second position in which the compression spring 30 is compressed between the pin 28 and another end 292 of the cavity 29 under the effect of the rotation of the ring 23 inside the upper doll element 121.

The ring 23 comprises on its peripheral contour a hollow housing 303.

The lower doll element 122 comprises an elastic finger 304 whose end is housed in the hollow housing 303 of the crown when it occupies its first position.

An elevator 37 is housed in a housing of complementary shape formed in the ring 23 so that the elevator 37 and the ring 23 are rotatably connected.

The elevator 37 comprises a cylindrical portion 371 which extends above the ring 23. Three inclined ramps 373 are formed and distributed uniformly in the cylindrical portion 371.

Three grooves 38 are formed and uniformly distributed inside the upper doll element 121. They extend parallel to the axis of the first shaft portion 200.

Three lifting pins 39 extend inside the grooves 38 and the slots 372. They are integral with a transition ring 40 mounted to move in translation inside the cylindrical portion 371 along the axis of the first portion 200.

The transition ring 40 and connected by hook slats 305 to a first clutch member 306.

The first clutch member 306 is movably mounted in translation along the axis of the second shaft portion 213.

A second clutch element 309 is mounted in translation to inside the first clutch element 306 along the axis of the second shaft portion 213.

Compression springs 400 are interposed between the first 306 and second 309 clutch members.

The second clutch element 309 is integral with the pusher element 302 so that a translation of the second clutch element 309 along the second shaft portion 213 is accompanied by a translation of the pusher element. 302 along the axis of the second shaft portion 213.

The periphery of the upper part of the pusher element 302 is traversed by uniformly distributed bores defining housings 307 able to receive balls 301.

The first shaft portion 200 comprises a lower portion on which are formed in a uniform manner grooves 308 suitable for housing the balls 301.

• une première position, illustrée à la figure 20, dans laquelle il place les billes 301 dans les logements 308 de la partie inférieure de la première portion d'arbre 200 en sorte que la première portion d'arbre 200 et la deuxième portion d'arbre 213 sont liées à rotation ;
• une deuxième position, illustrée à la figure 21, dans laquelle il place les billes 301 dans les logements prévus à cet effet de la bague de transmission 300 en sorte que le porte satellites et la deuxième portion d'arbre 213 sont liées à rotation.

The pusher element 302 is movable between:

• a first position, illustrated in figure 20 wherein it places the balls 301 in the housings 308 of the lower portion of the first shaft portion 200 so that the first shaft portion 200 and the second shaft portion 213 are rotatably connected;
• a second position, illustrated in figure 21 , in which it places the balls 301 in the housings provided for this purpose of the transmission ring 300 so that the satellite carrier and the second shaft portion 213 are rotatably connected.

The passage of the pusher element 302 from its first to its second position is obtained during the passage of the ring 23 from its first position to its second position. During this movement of the ring 23, the ramps 373 act on the pins 39 at the output that the transition ring 40 rises along the axis of the second shaft portion 213. The transition ring 40 drives in the same movement the first clutch element 306 against the effect of compression springs 311 placed between the frame 11 and the first element The first clutch element 306 drives the second clutch element 309 via the compression springs 400 in one and the same movement. The second clutch element 309 drives the pusher element 302 in one and the same movement. 301 balls then leave the housing 308 of the first shaft portion 200 to be housed in the slots provided for this purpose of the transmission ring 300.

The passage of the pusher element 302 from its second position to its first position is obtained during the passage of the ring 23 from its second position to its first position. During this movement of the ring 23, the ramps 373 act on the pins 39 at the output that the transition ring 40 descends along the axis of the second shaft portion 213. The first clutch member 306 follows the same movement under the effect of the compression springs 311. The second clutch member 309 follows the same movement via the compression springs 400. The second clutch member 309 drives in the same movement the pusher element 302. The balls 301 then leave the slots provided for this purpose of the transmission ring 300 to be housed in the housing 308 of the first shaft portion 200.

Needle cages 312 are interposed between the ring 205 and the upper doll element 121 so as to ensure the rotational guidance of the doll 12 relative to the frame 11.

7.4.2. Operation

The operation of the winch according to this third embodiment is substantially the same as the operation of the winch according to the second embodiment.

At the beginning of the winding of one end around the doll, the tension exerted by the end on the doll is low so that the crown 23 occupies its first position and the pusher element 302 occupies its first position.

When the drive means, which cooperate with the fluted portion 151, are rotated counterclockwise, the first shaft portion 200 rotates in the opposite direction of the needles of a watch. The second shaft portion 213 is engaged with the first shaft portion 200 via the balls 301 and the pusher member 302. The doll is then rotated clockwise at a first speed. .

A reversal of the direction of rotation of the drive means makes it possible to drive the doll in rotation in the direction of the clockwise according to a second speed.

When the force applied to the doll 12 by the end wound around becomes greater than the sum of the force applied to the doll 12 by the crew member via the actuating means is the different gears by which they are connected to the crown 23 and the friction force exerted by the elastic finger 304 on the ring 23, the ring 23 rotates inside the upper doll element 121 against the effect of the compression spring 30 to reach its second extreme position in which the pin 28 completely compresses the spring 30 against the end 292 of the cavity 29.

The crown 23 moves from its first extreme position illustrated to the figure 20 at its second extreme position illustrated at the figure 21 . The pusher member 302 moves from its first position to its second position.

The first shaft portion 200 and the second shaft portion 213 are no longer directly rotational. The transmission between the first shaft portion 200 and the second shaft portion 213 is provided by the epicyclic gear train, the planet carrier being connected to the second shaft portion 213 via the pusher element 302 and the balls 301.

Third and fourth speeds are thus selected.

When the drive means is rotated in a clockwise direction, the doll is rotated clockwise at a third speed

A reversal of the direction of rotation of the drive means makes it possible to drive the doll in rotation in the direction of clockwise according to a fourth speed.

The deselection of the third and fourth speeds is obtained automatically when the force exerted by the end on the doll decreases sufficiently.

The winch according to this third embodiment can operate in pumping mode.

Adjusting means may be provided to act on the stiffness of the elastic finger 304 so as to adjust the effort from which the third and fourth speed are selected. The elastic finger and the hollow housing of the crown could be replaced by a ramp and finger system like that of the previous embodiments.

Claims (16)

1. Winch (10) intended to be fixedly attached to a sailing boat in order to tension a line connected to a sail, said winch (10) comprising:

   - a fixed frame (11) housing a shaft (14) and a gearbox;

   - a drum (12) around which said line can be wound, said drum (12) being mounted so as to be mobile in rotation in only one direction around said frame (11) and connected to said shaft (14) via said gearbox, the putting of said shaft (14) into rotation being accompanied by a putting of said drum (12) into rotation around said frame (11).

   characterized in that it comprises means for evaluating the tension of said line and means for selecting automatically at least one gear speed when said tension becomes above a predetermined threshold, said gearbox comprising an inner ring gear (23), said ring gear (23) being mounted so as to be mobile in rotation inside said drum (12) against the effect of means exerting a frictional force and/or means for exerting an elastic return force on said ring gear (23) so that it can rotate relative to said drum (12) when said tension is above said threshold.
2. Winch according to claim 1, characterized in that said means for selecting automatically are mobile between at least one resting position and one position for selecting at least one gear speed, said ring gear (23) acting on said means for selecting automatically to place them in either one of their positions.
3. Winch according to claim 2, characterized in that it comprises means for converting a rotation shift of said ring gear (23) relative to said drum (12) into a movement of said means for selecting automatically either one of their positions.
4. Winch according to any one of the claims 1 to 3, characterized in that it comprises means for adjusting (35) said threshold value.
5. Winch according to claim 1 to 4, characterized in that said ring gear (23) has a contact surface (31) with a ramp (310) and in that said means exerting a frictional force on said drum (12) comprise a toe (46) interdependent with said drum (12) and return elastic means (34), said toe (46) taking support on said contact surface (31) under the effect of said elastic return means (34).
6. Winch according to claims 4 and 5, characterized in that said means for adjusting comprise a screw (35) having a base (351) and a head (352), said return means (34) being interposed between said toe (46) and said base (352), said head (351) being accessible from outside said drum (12).
7. Winch according to claim 1 to 4, characterized in that said ring gear (23) has a hollow housing (310) and in that said means exerting a frictional force on said drum (12) comprise an elastic toe (304) that is interdependent with said drum (12) and has its end capable of getting housed in said hollow housing (310).
8. Winch (10) according to any one of the claims 1 to 7, characterized in that said gearbox is a three-speed gearbox, said means for selecting automatically being means for selecting the third gear speed and in that the putting of said shaft (14) into rotation in one direction or the other is accompanied by the putting of said drum (12) into rotation around said frame (11) in one speed or another.
9. Winch according to claim 8, characterized in that the first gear speed of said gearbox has a multiplication ratio, the second and third gear speeds having reduction ratios.
10. Winch (10) according to any one of the claims 1 to 7, characterized in that said means for selecting automatically are means for selecting a third gear speed and a fourth gear speed.
11. Winch (10) according to any one of the claims 1 to 7, or 10, characterized in that said shaft comprises a first shaft portion (200) and a second shaft portion (213), said second shaft portion (213) being connected to said ring gear (23) by a plurality of gears so that a rotation of said second shaft portion (213) in one direction or in the other drives a rotation of said drum (12) in one direction at two different transmission ratios, said first shaft portion (200) being connected to at least one gear train, said means for selecting automatically interlocking directly said first shaft portion (200) with said second shaft portion (213) when they occupy one of their positions, said means for selecting automatically interlocking said first shaft portion (200) with said second shaft portion (213) via one of said gear trains when they occupy another of their positions.
12. Winch (10) according to any one of the claims 1 to 9, characterized in that said shaft (14) is connected to said ring gear (23) by a plurality of gears so that a rotation of said shaft (14) in one direction or the other drives a rotation of said drum (12) in one direction at two different transmission ratios, said shaft (14) being furthermore connected to the input of a multiplier gear train, the output of which being connected to the input of the plurality of gears by a one-way clutch, said means for selecting automatically interlocking the output of said multiplier gear train with the input of the plurality of gears when they occupy their resting position, said means for selecting automatically not interlocking the output of said multiplier gear train with the input of the plurality of gears when they occupy their other position.
13. Winch according to any one of the claims 1 to 9, or 12, characterized in that said shaft (14) has a first end (141) to which drive means can be connected, said gearbox having a first pinion (19) connected by means of a first one-way clutch (20) to a second end (142) of said shaft (14), said first pinion (19) meshing with a second pinion (21) mounted so as to be rotationally mobile on a first pin (22) interdependent with said frame (11), said second pinion (21) meshing with an inner ring gear (23) interdependent with said drum, a third pinion (24) being interdependent with said second end (141) of said shaft (14), said third pinion (24) meshing with a fourth pinion (25) mounted so as to be rotationally mobile around a second pin interdependent with said frame (11), said fourth pinion (25) meshing with a fifth pinion (26) connected to said first pin (22) by means of a second one-way clutch (27), said winch furthermore comprising a multiplier having an input connected to said shaft (14) and an output connected to the first pinion (19) by means of a third one-way clutch (18), said means for selecting automatically being capable of taking a position for holding said third one-way clutch (18) in disengaged position when said tension is above said threshold, the first (20), second (27) and third (18) one-way clutches being configured so that a rotation in a first direction of said shaft enables it to transmit a torque to said ring gear via said multiplier, said third one-way clutch (18), said first (19) and said second (21) pinions, so that a rotation of said shaft (14) in another direction enables it to transmit a torque to said ring gear (23) via the first (19) and second (23) pinions, and so that a rotation in said first direction of said shaft (14) while said tension is above said threshold enables it to transmit a torque to said ring gear (23) via the third (24), fourth (25) and fifth (26) pinions.
14. Winch according to claim 13, characterized in that said ring gear (23) is mounted so as to be mobile in rotation between two end positions inside said drum (12), countering the effect of said elastic return means (30), said ring gear (23) acting on said means for selecting automatically so that the passage from one of said end positions to the other of the ring gear (23), countering the effect of said return means (30), is accompanied by the passage of said means for selecting automatically into said holding position.
15. Winch according to any one of the claims 12 à 14, characterized in that said multiplier, said third one-way clutch (18) and said means for selecting automatically are detachable.
16. Winch according to any one of the claims 1 to 15, characterized in that it comprises means for actuating said shaft (14), said means for actuating comprising a pedestal or a crank, one end of which complements said first end (141) of said shaft (14).

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