US20140291079A1 - Device for preventing a shaft rotation - Google Patents
Device for preventing a shaft rotation Download PDFInfo
- Publication number
- US20140291079A1 US20140291079A1 US14/127,587 US201114127587A US2014291079A1 US 20140291079 A1 US20140291079 A1 US 20140291079A1 US 201114127587 A US201114127587 A US 201114127587A US 2014291079 A1 US2014291079 A1 US 2014291079A1
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- US
- United States
- Prior art keywords
- shaft
- moving element
- fixed element
- moving
- movement
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
- B63H—MARINE PROPULSION OR STEERING
- B63H23/00—Transmitting power from propulsion power plant to propulsive elements
- B63H23/32—Other parts
- B63H23/34—Propeller shafts; Paddle-wheel shafts; Attachment of propellers on shafts
- B63H23/35—Shaft braking or locking, i.e. means to slow or stop the rotation of the propeller shaft or to prevent the shaft from initial rotation
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
- B63H—MARINE PROPULSION OR STEERING
- B63H3/00—Propeller-blade pitch changing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D49/00—Brakes with a braking member co-operating with the periphery of a drum, wheel-rim, or the like
- F16D49/16—Brakes with two brake-blocks
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D65/00—Parts or details
- F16D65/02—Braking members; Mounting thereof
- F16D2065/024—Braking members; Mounting thereof the braking surface being inclined with respect to the rotor's axis of rotation at an angle other than 90 degrees, e.g. comprising a conical rotor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2127/00—Auxiliary mechanisms
- F16D2127/001—Auxiliary mechanisms for automatic or self-acting brake operation
- F16D2127/002—Auxiliary mechanisms for automatic or self-acting brake operation speed-responsive
Abstract
A device for preventing and/or stopping rotation of a shaft coupled to a motor, of the type having a first fixed element with respect to this shaft, and a moving element, and means to constrain the moving element to the shaft in such a manner as to rotate integrally with this shaft and at the same time be able to move between a position of friction contact with the fixed element, to allow stopping of the shaft, and a position of disengagement from this fixed element, to allow release of the shaft is disclosed. The device advantageously provides that the means to constrain the moving element to the shaft include a link for movement of the moving element along a direction having a radial component with respect to the shaft.
Description
- The present invention relates to a device for preventing or stopping rotation of a shaft coupled to a motor, i.e. of a shaft that transfers a torque between two or more members connected thereto, when the motor is not operating and/or substantially is not transmitting torques to the shaft.
- In other words, the device according to the present invention is suitable to exert mechanical braking actions, i.e. resisting forces and/or torques, capable of preventing or stopping the rotational motion of the shaft on which the device acts when the motor is not operating.
- In particular, the device according to the present invention can be fitted to the motor of a watercraft, in such a manner as to prevent and/or stop rotation of a transmission shaft to which a motor and a propeller are coupled.
- When the motor is switched off and no longer transmits torque to the propeller through the shaft to which the two members are coupled, the propeller is free to move due to the inertia and due to the flow of fluid that strikes it, thus continuing its rotational motion. This effect is particularly felt in sailing boats equipped with a motor for auxiliary propulsion activated during manoeuvres or in the case of need, coupled to a propeller through a transmission of hydraulic type.
- In fact, when the motor is switched off and the watercraft proceeds using sailing (wind) propulsion, the motor does not transmit any torque to the propeller, which therefore continues its rotational motion due to inertia and to the flow of the current that strikes it during forward motion of the watercraft. In the case in which the transmission of motion from the motor to the propeller is of hydraulic type, or in the case in which an endothermic motor activates at least one pump of a hydraulic circuit responsible for rotation of the motor shaft of the propeller, when the motor is stopped and is no longer operating, this hydraulic transmission is not able to develop resisting actions capable of preventing, or at least of reducing, rotation of the shaft, which is therefore substantially free to rotate.
- It must also be noted that propellers of the variable pitch type are currently used, with the possibility of automatically arranging the blades in a “feathered” position when there is no driving torque, i.e. in the position in which the blades offer the least fluid dynamic resistance possible when the motor is not operating. This position, which is obtained through controlled rotation of the blades about their axis, can only be reached if the motor shaft not moving and therefore if the rotational motion of the propeller is stopped.
- The fact that the propeller continues its rotational motion even after the motor has been switched off, due to inertia and to the flow of fluid that strikes it, prevents the blades from reaching the feathered position which, as stated, requires the propeller to be stopped.
- For this reason, the propeller continues its rotational motion causing problems of noise, resistance to motion and consequent mechanical wear during sailing, until the watercraft stops moving or the motor is switched on again.
- In particular, the fact that the propeller continues to turn in an undesirable manner, besides causing increased resistance to the forward motion of the watercraft, can also cause damage to the propeller itself, to the transmission, and to the motor, given that this undesirable rotation increases the number of working hours that must be taken into account correctly for maintenance operations and for changing parts subject to wear.
- To deal with this problem, and to stop motion of the shaft, and therefore allow the blades of the propeller to reach the “feathered” position, it is necessary to try to stop the rotational motion of the shaft, for example by acting directly thereon through clamps, or similar tools available on board.
- Naturally, these operations are very difficult to carry out, and in fact often the shaft is not easily accessible, for example due to the limited spaces in which it is installed, and are also very dangerous for the safety of the person who attempts to stop the rotational motion of the shaft.
- Other solutions have been proposed for preventing shaft rotation through devices capable of blocking its rotation when the motor to which it is coupled is not operating.
- For example, the document U.S. Pat. No. 4,464,127 describes a device to immobilize a transmission shaft comprising two portions that are activated hydraulically to come into contact with the outer surface of the shaft causing locking thereof by friction contact. More in detail, the two portions are actuated by means of hydraulic cylinders connected to a power supply circuit that causes movement of the two portions in a position of contact with the shaft. In this manner, the friction generated between the two portions, and in particular by the friction means with which these portions are equipped, with the outer surface of the shaft, causes locking of this latter because of friction generated by contact between the surfaces.
- The device described above has some disadvantages mainly due to the presence of the hydraulic actuation. In fact, the device for immobilizing a motion transmission shaft described above requires to be connected to a suitable hydraulic distribution circuit, which causes a certain difficulty for installation and above all costly maintenance, also due to the noteworthy dimensions of this device.
- Moreover, as a system of hydraulic type is present, the device is not very reliable. Given that locking of the shaft is closely related to the pressure of the fluid that drives the hydraulic cylinders, any loss of load of the fluid inside this circuit, for example in the case of breakage or malfunction, means that it is not possible to reach the pressure required to generate sufficient friction to cause locking of the shaft.
- The object of the present invention is to overcome the problems of the prior art and to provide a device for preventing rotation of a motion transmission shaft, and consequently to cause stopping thereof, when the motor constrained thereto is not operating, which is simple to produce and which can be easily installed on and removed from the shaft, for example when wishing to carry out maintenance operations.
- Moreover, a further object of the present invention is to provide a device for preventing rotation of a motor shaft of small dimensions, in such a manner that it can be easily installed on and adapted to different watercraft, and in particular to sailing craft, and which simultaneously offers high reliability in the locking of the shaft.
- Furthermore, an object of the present invention is to provide a device for preventing rotation when the motor is not operating, which can be used in sailing boats equipped with hydraulic transmission between motor and propeller, which allows locking of the shaft and therefore stops undesirable shaft rotation in order to reach the “feathered” position of the blades.
- Not least, an object of the present invention is to provide a device for preventing shaft rotation of “automatic” type, i.e. which does not require external controls and/or actuation by a user.
- These and other objects are achieved by means of a device for preventing and/or stopping the rotation of a motion transmission shaft connected kinematically to at least one motor according to
claim 1, of the type comprising at least a first element fixed with respect to the motion transmission shaft, and at least a moving element, and means to constrain said at least one moving element to the transmission shaft jointly in such a manner as to rotate integrally with the shaft and in such a manner as to move between a position of friction contact with said at least one fixed element, to allow stopping of the shaft, and a position of disengagement from said fixed element, to allow release of the shaft. Advantageously, the device provides that said means to constrain said at least one moving element to the shaft comprise at least one link for movement of said at least one moving element along a direction having at least a radial component with respect to the shaft. - According to a possible embodiment of the present invention, the moving elements are free to move between the position of friction contact with the fixed element, to stop the shaft, toward the position of disengagement therefrom in which the shaft is free to rotate, and vice versa.
- In this manner, when a predefined threshold angular velocity of the shaft is exceeded, this causes movement of the moving elements to the position of disengagement from the fixed element, while when the rotation speed decreases, the moving elements return, under the effect of their weight, to the position of friction contact with the fixed element.
- The friction contact between the moving element and the fixed element preferably takes place by means of the contact of inclined surfaces produced in a mating (correspondent) manner on the moving element and on the fixed element.
- Moreover, according to a possible embodiment, the means to constrain said at least one moving element to the shaft also comprise at least one contrast member to counter in a controlled manner the movement of said at least one moving element, at least along this direction having at least a radial component, toward the aforesaid position of disengagement from said at least one fixed element.
- This solution, as will be apparent to those skilled in the art, allows the moving element of the device to be caused to move with respect to the transmission shaft along this radial direction by the centrifugal force acting on the same moving element—when the shaft is made to rotate—even if this motion is countered in a controlled manner, i.e. only for certain rotation values of the motor shaft, by the contrast member, which can preferably be constituted by one or more springs.
- In this manner, the moving element can reach the aforesaid position of disengagement from the corresponding fixed element, starting from its position of friction contact with this latter, only when it is able to overcome the resistance to radial translation thereof exerted by the contrast member (for example a spring), i.e. only when the motor shaft has reached an angular velocity at which the centrifugal force, to which the moving element is subjected, exceeds the aforesaid countering radial force exerted by the spring.
- In practice, as shall be apparent also from the description below, the constraining means described above and claimed allow temporary movement of said at least one moving element in the position of disengagement from the fixed element, only when a predefined angular velocity of the motion transmission shaft is exceeded.
- It is clear that the device according to the present invention acts automatically without the need to control movement of the moving element from the position of friction contact with the fixed element in order to stop the shaft, to the position of disengagement from this fixed element to release the shaft, and vice versa.
- This means that, when a driving force produced by a motor connected to this transmission shaft no longer acts thereon, the decrease, due to friction, of the rotation speed of this transmission shaft causes a corresponding decrease of the centrifugal face and consequently causes operation of the contrast member, which counters radial movement of the moving element and return of this latter toward the position of friction contact with the corresponding fixed element, so as to brake rotation of the transmission shaft.
- It must be noted that the aforesaid moving elements can be constrained directly or indirectly to the shaft, provided that they are rotatable integrally therewith and at the same time movable, at least radially, with respect to said shaft.
- In the case in which, according to a preferred embodiment of the present invention, the contrast member also acts as return member of said at least one moving element toward its position of friction contact with the related fixed element, and for example this member is constituted by at least one return spring, or other equivalent elastic element, when the centrifugal force acting on the moving element decreases, this return spring causes the moving element to promptly take its position of friction contact with the fixed element, so as to brake and rapidly stop rotation of the motion transmission shaft.
- According to some preferred embodiments of the present invention, the constraint (link) for movement of said at least one moving element along a direction having at least a radial component with respect to the transmission shaft can be a link of the sliding type, to allow translation of the moving element with respect to the shaft along this direction having at least a radial component, or can be a pivot link, in which the pivot axis is orthogonal to the rotation axis of the transmission shaft. Preferably, the device according to the present invention allows prevention of shaft rotation in sailing craft when the motor is not operating and is not transmitting torques to the propeller. In fact, the device has been designed so that the return force exerted by the suitable contrast members with which it is equipped, and in particular springs, allows the moving elements to be retained in a position of contact with the fixed element and consequently locking of the shaft when the engine is not operating and the propeller continues its rotational motion due to inertia and to the flow of fluids that strikes it.
- These and other advantages of the present invention will be more apparent from the following description and from the drawings, attached by way of non-limiting example, wherein:
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FIG. 1 shows, in a partially sectional view according to a plane passing through the rotation axis of the shaft, a possible embodiment of the device for preventing shaft rotation according to the present invention; -
FIG. 1A shows a schematic view according to a plane perpendicular to the rotation axis of the shaft of a possible embodiment of the moving elements of the device; -
FIGS. 1B and 1C show according to a plane perpendicular to the rotation axis of the shaft a further possible embodiment of the moving elements of the device respectively in the position disengaged from the shaft and in the position to stop the shaft. -
FIG. 2 shows, in a partially sectional view according to a plane passing through the rotation axis of the shaft, a further possible embodiment of the device for preventing shaft rotation according to the present invention; -
FIG. 3 shows, in a partially sectional view according to a plane passing through the rotation axis of the shaft, a further possible embodiment of the device for preventing shaft rotation according to the present invention equipped with means for regulation of the contrast member, -
FIG. 4 shows, in a partially sectional view according to a plane passing through the rotation axis of the shaft, a further possible embodiment of the device for preventing shaft rotation according to the present invention equipped with guides of the moving elements passing through the device; -
FIG. 5 is a sectional view according to a plane perpendicular to the rotation axis of the shaft of the device according toFIG. 4 ; -
FIG. 6 shows in detail the member to counter movement of the moving element used in the device according toFIGS. 4 and 5 . - With reference in general to the accompanying figures, some preferred embodiments of the
device 1 for preventing and/or stopping rotation of a motion transmission shaft according to the present invention will be described. In the accompanying figures, the same numerical reference will be assigned to those components of thedevice 1 that exercise, albeit with dissimilar forms, an identical function. - As can be seen in the figures, the
device 1 of the present invention is mounted on amotion transmission shaft 10 in order to exert resisting actions which prevent and/or stop rotation thereof when the motor to which theshaft 10 is connected is not operating. - Naturally, the
shaft 10 can be any type among those known in the art, and is adapted to transfer torque from a motor, not shown in the accompanying figures, to one or more further members constrained to the shaft, and vice versa. - In particular, as already stated, the device according to the present invention can prevent or stop rotation of a
shaft 10 of a watercraft, adapted to transmit torque between a motor and a propeller, and vice versa, above all in the case in which a transmission of hydraulic type is present between motor and propeller, and the propeller is of the variable pitch type, capable of adopting a “feathered” position when there is no driving torque, i.e. capable of adopted a configuration such as to offer the least possible fluid dynamic resistance, when no torque is transmitted to this propeller. - Generally, the
device 1 according to the present invention comprises at least onefixed element 2 which is constrained to one or more points of the structure inside which themotor shaft 10 is mounted in a rotatable manner. Thisfixed element 2 can be configured in such a manner as to constitute the external part of thedevice 1 and can house therein all the other components, so as to produce a compact and easily installable and removable device. - Naturally, an external casing, not shown in the accompanying figures, can be provided to protect the device according to the present invention.
- In the case in which the
device 1 is installed on a watercraft, the fixedelement 2 can preferably be constrained to the hull of the watercraft or to parts of the related propulsion that do not rotate together with themotion transmission shaft 10; for this purpose, as shown, for example, in the embodiment ofFIGS. 2 , 3 and 4, arod 50 secured to a fixed part with respect to the shaft is constrained to the fixedelement 2 for preventing rotation thereof. - The
device 1 according to the invention also comprises one or moremoving elements 5, constrained directly or indirectly to theshaft 10 through specific constrainingmeans element 2, for preventing or stopping rotation of thisshaft 10, and a position of disengagement from said fixedelement 2, to allow release of theshaft 10. Advantageously, according to the present invention, these constraining means comprise aspecific link elements 5 to move along a direction having at least a radial component with respect to the rotation axis A of theshaft 10. - As will be apparent to those skilled in the art, when the moving
elements 5 are in contact with the fixedelement 2, the friction generated between the surfaces allows prevention of rotation of theshaft 10 to which the moving elements are constrained, while when these movingelements 5 are not in contact with the fixedelement 2, and are therefore in the position to release theshaft 10, this latter is free to rotate as thedevice 1 does not exert any resisting actions thereon. - The friction contact between the moving
element 5 and the fixedelement 2 preferably takes place by means of contact ofinclined surfaces element 5 and on the fixedelement 2. - As shown in the accompanying figures, the
inclined surfaces element 5 and of the fixedelement 2 have a “wedge” configuration, in such a manner as to cause friction contact therebetween to cause stopping of theshaft 10. Therefore, the movingelements 5 act like the blocks of a brake. - More in detail, movement from the position of friction contact of the moving
elements 5 with the corresponding fixedelement 2, due to thelinks elements 5 to move along a direction having at least a radial component with respect to theshaft 10, takes place due to the centrifugal force Fc produced by rotation of thisshaft 10 on which the movingelements 5 are constrained, which in fact rotate integrally therewith. - In fact, for a given value of centrifugal force Fc, during rotation of the
shaft 10 the movingelements 5 tend to move away from the position of friction contact with the fixedelement 2 of thedevice 1, in which stopping of theshaft 10 is caused, moving toward the position of disengagement from the fixedelement 2, in which the movingelements 5 are not in contact therewith, and therefore theshaft 10 is able to rotate freely. - According to an embodiment of the present invention, the moving
elements 5 are free to move between the position of friction contact with the fixedelement 2, to stop theshaft 10, toward the position of disengagement therefrom in which the shaft is free to rotate, and vice versa. - In this manner, after exceeding a predefined threshold angular velocity of the
shaft 10, movement of the movingelements 5 in the position of disengagement from the fixedelement 2 is caused, while when the rotation speed decreases the movingelements 5 return, under the effect of their weight, to their position of friction contact with the fixedelement 2. - It is clear that, in the embodiment described above, in which the moving
elements 5 can move freely, the weight of these movingelements 5 must be suitably dimensioned during the design phase, so that for a desired number of revolutions of theshaft 10 and of the corresponding action of the centrifugal force generated, they are made to move away from the position of friction contact with the fixedelement 2 for release of the shaft. At the same time, it must be taken into account that the weight of the movingelement 5 must be such as to generate a braking force of an intensity such as to cause the shaft to stop following friction contact with the fixedelement 2. - In particular, in the case in which stopping of the shaft is caused through friction contact of the
inclined surfaces element 5 and of the fixedelement 2, the braking force generated following contact is equal to the weight of the moving element multiplied by the friction coefficient of the contact surfaces and divided by the sine of the angle of inclination of the inclined surfaces in contact, according to a relation well known in mechanics. - Preferably, the angle of inclination of the
surfaces - According to an alternative embodiment, movement of the moving elements (5) is suitably regulated and controlled, and the constraining
means contrast member 30, having the purpose of obstructing, in a controlled manner, i.e. only when predefined load conditions occur, movement of the movingelements 5, at least along said radial component thereof, toward their position of disengagement from the related fixedelement 2. - In particular, according to the present invention, this
contrast member 30 is configured to allow temporary movement of the movingelements 5 in the position of disengagement from the fixedelement 2, only after exceeding a predefined angular velocity of thisshaft 10. - It must be noted that while in the embodiments illustrated in the accompanying figures the device is equipped with at least one
contrast member 30, this element may be omitted, as described above, in such a manner that the movement of the movingelements 5 between the stop position and the position disengaged therefrom, and its return to the stop position (because of friction contact with the fixed element 2) as a result of the weight of the movingelements 5 themselves, remains free. - The
contrast member 30 of thedevice 1 is such as to counter, at least for certain values thereof, the centrifugal force Fc which, during rotation of theshaft 10, tends to move the movingelements 5 away from the position of friction contact with the fixedelement 2 of thedevice 1, in which theshaft 10 is locked, toward the position of disengagement from this fixed element, in which the movingelements 5 are not in contact with the fixedelement 2, and therefore theshaft 10 is able to rotate freely. - According to a preferred aspect of the present invention, said member to contrast (counter) movement, at least along the related radial component, of the moving
elements 5 toward their position of disengagement from the corresponding fixedelement 2, can be constituted by one ormore springs 30, or other similar elastic means, which also have the function of returning the movingelements 5 toward their position of friction contact with the fixedelement 2. - A
similar contrast member 30 is therefore configured to allow temporary movement of the movingelements 5 to the position of disengagement from the fixedelement 2 only after exceeding a predefined threshold angular velocity of the shaft 10 (i.e. when the centrifugal force Fc reaches greater intensity with respect to the return force exerted on the movingelements 5 by these members 30), and to return these movingelements 5 to their position of friction contact with the fixedelement 2, when the angular velocity of theshaft 10 drops below the aforesaid threshold value. - In the case in which springs 30 are used as contrast member, a suitable choice of the elastic constant of these
springs 30, together with the choice of any preload conditions and of the masses of the movingelements 5, allows these movingelements 5 to move toward their position of disengagement from the related fixedelement 2, toward which they are retained by thesprings 30, overcoming the related elastic force, only when the centrifugal force Fc acting thereon exceeds a threshold value defined during the design phase, i.e. only when the angular velocity of theshaft 10 exceeds a certain predefined value. - In this manner, when the
shaft 10 is rotating at low speed, for example because the related motor has been switched off, the elastic force exerted by thespring 30 tends to counter movement of the movingelements 5, preventing them from abandoning the position of contact with the fixedelement 2 due to the centrifugal force caused by rotation. - However, when the rotation speed of the
shaft 10 is sufficiently high, the centrifugal force generated will reach an intensity such as to overcome the elastic force exerted by thespring 30 on the movingelements 5 and consequently will allow these latter to disengage from the related fixedelement 2, thus leaving theshaft 10 free to rotate. - It must be noted that, although in the preferred embodiments of the present invention illustrated here, this
contrast member 30 has the form of cylindrical helical spring, or springs, any other type of spring, and/or any other means known in the art capable of countering, in a temporary or controlled manner, movement of the movingelements 5 toward their position of disengagement from the fixedelement 2, such as fluid dampers, or suitable elastically deformable elements, can be used alternatively, without departing from the scope of protection requested here. - It must also be noted that the term “controlled contrast members” is intended as any contrast member that is configured and calibrated to counter movement of the moving
elements 5 as a function of the force acting on these movingelements 5, without permanently preventing movement thereof, but only obstructing this movement. For example, this controlled contrast member can perform the function of preventing motion of the movingelements 5 only until a certain driving force (in this case constituted by the centrifugal force) acting on the movingelements 5 is reached, beyond which the contrast member is not longer able to immobilize these elements. According to a possible embodiment, the device is equipped withmeans 40 for regulation of thecontrast members 30, which are capable of determining any modifications of the return force exerted thereby. In this manner, it is possible to modify the threshold angular velocity of theshaft 10 at which thecontrast members 30 allow temporary movement of the movingelements 5 to the position of disengagement from the fixedelement 2 and at the same time to return these movingelements 5 to their position of friction contact with the fixedelement 2 when the angular velocity of theshaft 10 drops below said threshold value. - More in detail, in the embodiment illustrated in
FIG. 3 , in which the contrast members employed aresprings 30, said regulation means 40 comprise ascrew 41, operable from the outside, which allows modification of the preload of thespring 30 by means of controlled compression thereof depending on whether thescrew 41 is screwed or unscrewed. As a result, the related elastic force exerted by thespring 30 is modified causing variation of the conditions for which the movingelements 5 can move toward their position of disengagement from the related fixedelement 2, toward which they are retained by thesprings 30. In fact, it is apparent that for a different value of elastic force (force countering movement of the moving elements) exerted by the springs, the intensity of the centrifugal force Fc acting thereon necessary to allow movement thereof will vary, thus causing a modification of the threshold value of the angular velocity of theshaft 10 which allows actuation of the device according to the present invention. - It must also be noted that the device according to the present invention can be produced in two or more parts, preferably two mutually separable half-parts, in such a manner as to be easily constrained on the shaft whose rotation is to be controlled. More in detail, in the case of installation of the device on a watercraft, locking of the device formed by the two mutually separable half-parts that are subsequently constrained through means known for this use, such as a plurality of screws (see for example
FIGS. 1 and 3 ), is considerably simplified as it is not necessary to remove the propeller shaft from the watercraft. - It must also be noted that, in order to make the device safer, according to another possible embodiment, the parts of which it is composed are mutually constrained by means of a system of interlocks, preferably with cooperating parts arranged at 90° from one another, which are thus locked to one another. This method of constraint prevents the parts of which the device is composed, subject to rotation and therefore to centrifugal force, from becoming dangerously loose, or even separating.
- As will be described in more detail with reference to the embodiment illustrated in
FIGS. 4 and 5 , theguides 22 of the movingelements 5 passing through the body of the device cooperate in retaining in assembled position the parts of the device which are coupled to one another with this system of interlocks. - With reference now to the embodiment of the
device 1 according to the invention illustrated inFIGS. 1 and 1A , this comprises a plurality of movingelements 5, or blocks, which are constrained in such a manner as to rotate integrally with theshaft 10, by means of interposing of aframe 3, integral with theshaft 10, and of guides, or pins 20, projecting integrally from theframe 3 in radial direction with respect to theshaft 10, and configured to act as a link of the sliding type for each of the movingelements 5. - More in detail, the
frame 3 is substantially annular in shape and has a central portion, in the form of a sleeve, having an internal diameter such as to allow fitting thereof on theshaft 10, and a peripheral portion, also annular, which extends in a manner coaxial to theshaft 10, and which acts as support for theguides 20 of theblocks 5. - The
frame 3 can be secured to theshaft 10 according to known means, such as by interference fit of parts or using constraining means such as screws, pins, bolts and the like, just as theguides 20 can also be secured to theframe 3 by known means (such as interlocking, or screwing of threaded parts, etc.). - In the embodiment illustrated in
FIG. 1 , thedevice 1 is equipped with two moving elements, or blocks, 5, each of which is substantially in the shape of an annular sector, when viewed on a plane perpendicular to the rotation axis of the shaft 10 (seeFIG. 1A ). Theblocks 5 have dimensions substantially equal to half of an annular sector. However, other embodiments are possible, for example in which the device is equipped with four moving elements, or blocks, 5, each having dimensions substantially equal to a quarter of annular sector. -
FIGS. 1B and 1C show a further possible embodiment of the movingelements 5, illustrated schematically respectively in position of disengagement from the shaft and in the position to stop the shaft. - In the same manner as illustrated in
FIG. 1A ,FIGS. 1B and 1C show two movingelements 5, each having a shape substantially equal to a half of annular sector, viewed in a plane perpendicular to the rotation axis of theshaft 10, and which are equipped with at least one raised surface portion 5.1. - More in detail, the moving
element 5 is provided on the lateral surface thereof with a raised portion 5.1 with respect to the other portions 5.2. of its lateral surface. As will be more apparent below, the raised surface portion 5.1, which is preferably produced in the central portion of its half of annular sector shape, is destined to come into friction contact with the fixedelement 2 to cause locking of the shaft. Moreover, the Applicant has verified that the presence of a portion 5.1, even if only slightly raised (one or a few millimetres of thickness) with respect to the other portions 5.2 of the surface, greatly facilitates movement of the moving element from the position to stop the shaft to the position of disengagement therefrom, and vice versa, without heat and rotational motion being in any manner able to obstruct this movement of the moving element required for correct operation of the device. - The
blocks 5 are constrained to theframe 3 in such a manner that as a whole, when viewed in a plane perpendicular to the axis of theshaft 10, they substantially define a circular ring around theshaft 10. - It must be noted that although in the embodiments illustrated the
blocks 5 have this annular sector shape, other embodiments of the movingelements 5 can be used without departing from the scope of protection of the present invention. - As stated, each moving
element 5 is constrained to theframe 3, and in particular to the annular peripheral portion thereof, by means of a pair of guides, or pins 20, or similar means, projecting from theframe 3 toward theshaft 10, along a radial direction with respect to thisshaft 10. - While specific reference has been made to
guides 20 arranged radially with respect to theshaft 10, other embodiments are possible, in which theguides 20 lie in a plane passing through the rotation axis A of theshaft 10, but are not directed radially with respect thereto, although allowing translation of theblocks 5 along a direction with a radial component with respect to the axis A, or, theguides 22 lie in a plane parallel to a plane passing through the rotation axis A of theshaft 10 and are preferably perpendicular to this shaft 10 (consequently leaving theblocks 5 free to translate along a direction with a radial component), as in the embodiment illustrated inFIGS. 4 and 5 . These guides 20 are configured to act as link of the sliding type in relation to theblocks 5, i.e. to constrain theblocks 5 to theframe 3, and therefore to theshaft 10, in such a manner as to allow radial movement thereof with respect to the rotation axis A of theshaft 10—movement caused by the centrifugal force, as already described—and at the same time make theseblocks 5 rotate integrally with theframe 3 and therefore with thisshaft 10. - In other words, in the embodiment of this invention illustrated herein in
FIG. 1 , the two moving elements, or blocks, 5, are constrained in a translatable manner on theframe 3, integral with theshaft 10, in such a manner as to be free to move along a radial direction and at the same time be constrained to rotate integrally with thisshaft 10. - In the embodiment illustrated in
FIG. 1 , thedevice 1 also comprises a fixedelement 2 which, as stated, can be constrained, for example, to parts of a watercraft or of a propulsion fixed with respect to theshaft 10, and which comprises a portion destined to come into friction contact with the moving elements, or blocks, 5. - This friction contact with the fixed
element 2 by theblocks 5 is generated, according to the embodiment described here, by means ofinclined portions 6 produced on the lateral surface of each movingelement 5, which are configured to come into contact with correspondinginclined surfaces 6′ arranged on the fixedelement 2. - As already stated, the friction generated by the contact of the
inclined portions elements 5 and of the fixedelement 2, and therefore the braking force exerted by thedevice 1 on theshaft 10, will depend on the inclination of thesurfaces - This
portion 6′ of the fixedelement 2 is configured to intercept theblocks 5 during their radial movement, only in a position that theseblocks 5 reach when they are not stressed by the centrifugal force Fc to which they are subjected due to rotation of theshaft 10. - In this manner, due to the
guides 20, theblocks 5 can translate in a radial direction between a position of disengagement from the fixed element 2 (upward inFIG. 1 ) and a position of friction contact with this fixed element 2 (downward inFIG. 1 ), as a function of the rotation speed reached by theshaft 10. - Moreover, as can be seen in
FIG. 1 , each moving element, or block, 5, is also connected along a radial direction with a cylindricalhelical spring 30, for example acting in extension or in compression, which constitutes part of the corresponding controlled contrast members of the radial movement of theblocks 5 toward their position of disengagement from the fixedelement 2. These cylindricalhelical springs 30 also act as means for the return of theseblocks 5 toward said position of disengagement from the fixedelement 2. - The elastic force exerted by each
spring 30 is calibrated in such a manner as to cause each movingelement 5 to remain in the position of friction contact with the fixedelement 2, at least until the centrifugal force Fc acting on theblocks 5, generated by rotation of theshaft 10, is insufficient to overcome the return force of thesesprings 30. When the centrifugal force Fc acting on theblocks 5 is sufficiently intense to overcome the return force of thesprings 30, this centrifugal force Fc causes the blocks to move radially along theguides 20, toward said position of disengagement from the fixedelement 2. - It must be noted that, during the design phase of the
device 1, the mass of the movingelements 5, their distance from the rotation axis A of the shaft and the characteristics of thespring 30 are determined; therefore it is basically possible to establish the rotation speed of theshaft 10 at which thedevice 1, after installation on theshaft 10, will start to function, allowing temporary movement of the movingelements 5 from the position of friction contact with the fixedelement 2 to the position of disengagement in which theshaft 10 is free to rotate. Moreover, as shown inFIG. 3 , according to a possible embodiment, the elastic force exerted by eachspring 30 can be modified manually by the user acting on suitable regulation means 40, which comprise ascrew 41 adapted to modify the extension of thisspring 30, modifying the preload thereof. - As already stated, the device according to the present invention illustrated in
FIG. 1 can also function without contrast members, and in particular without thespring 30, in such a manner that movement of theblocks 5 from the position of friction contact with the fixedelement 2, and in its return to this position when the centrifugal force decreases (linked to the number of revolutions of the shaft 10) as a result of the weight of theblock 5, remains free. - With reference now to the embodiment of the present invention illustrated in
FIG. 2 , thedevice 1 illustrated provides that the movingelements 5 are constrained to aframe 3 integral with theshaft 10, in such a manner as to be able to rotate, at least partially, about ahinge 21, constrained to thisframe 3. - This
frame 3, in the same manner as the one described in relation toFIG. 1 , has a substantially annular extension and is fitted on theshaft 10 by means known in the art. Thehinge 21, constituted for example by a metal pin secured to theframe 3 and coupled in rotation to a movingelement 5, has a rotation axis which is substantially orthogonal to the rotation axis A of theshaft 10, in such a manner that the rotational motion R of each movingelement 5 about thishinge 21 has a component along a radial direction with respect to thisshaft 10, so that the centrifugal force acting on the moving elements during rotation of theshaft 10 causes rotation of the movingelements 5 about the related hinges 21. - The
device 1 is completed by a fixedelement 2, suitably constrained, for example, to the hull of a watercraft, and configured to temporarily engage with friction with the movingelements 5, and with the suitable return means of these elements. - According to this embodiment, each moving
element 5 is configured in such a manner as to comprise apart 5A of small dimensions equipped with at least oneinclined surface 6, adapted to come into contact with at least one correspondinginclined surface 6′ of the fixedelement 2, and apart 5B of larger dimensions. As thepart 5B is of larger dimensions with respect to thepart 5A, the centrifugal force Fc generated during rotation of the shaft will act prevalently thereon, causing rotation of the moving element about the point ofconstraint 21. - Also in the case of the
device 1 ofFIG. 2 , aspring 30, or similar elastic contrast and return means, acting on each movingelement 5, allows thepart 5A of each movingelement 5 to be retained in the position of friction contact with the fixedelement 2, until the centrifugal force acting on this moving element is eliminated or remains below a predefined threshold. - It must be observed that, also in the embodiment of the
device 1 ofFIG. 2 , thesprings 30 are configured to act radially on the moving elements, or blocks, 5, so that their line of action on theseblocks 5 is a straight line arranged radially with respect to theshaft 10. - Therefore, in the same manner as the device illustrated in
FIG. 1 , when rotation of theshaft 10 is such that the centrifugal force generated is of lesser intensity than the elastic return force of thespring 30, the movingelements 5 are retained in the position of friction contact with the fixedelement 2, thus causing the shaft to stop. - Instead, when rotation of the
shaft 10 reaches a value that allows the corresponding centrifugal force Fc generated on the movingelements 5 to overcome the intensity the elastic return force of thespring 30, the movingelements 5 which would tend to move radially toward the periphery of the device, due to the point ofconstraint 21, of hinge type, with theframe 3 are subjected to rotation thereabout in the direction indicated inFIG. 2 by the arrow R. - This rotation of the moving
elements 5 causes compression of thespring 30, through thepart 5B thereof, and consequently temporary movement of thepart 5A from the position of friction contact with the fixedelement 2, toward the related position of disengagement, in which theshaft 10 is free to rotate as the device does not exert resisting forces thereon. - It must be noted that, just as for the embodiment illustrated in
FIG. 1 , the term “temporary movement” from the position of contact has been used in the present description to indicated that in the moment in which rotation of theshaft 10 generates a centrifugal force Fc of lesser intensity than that of the return force exerted by thesprings 30, the movingelements 5 are returned to the position of contact with the fixedelement 2. - Also in this embodiment, the at least one
contrast member 30 of the device can be omitted, in such a manner that movement of the movingelements 5 remains free. - With reference now to the embodiment of the present invention illustrated in
FIGS. 4 and 5 , this comprises two movingelements 5, or blocks, which are constrained in such a manner as to be rotatable integrally with theshaft 10, through interposing of aframe 3, integral with theshaft 10, and ofguides 22 configured to act as a link of the sliding type for each of the movingelements 5. - More in detail, the device comprises four
guides 22, arranged in pairs laterally with respect to theshaft 10, and directed perpendicular to the rotation axis A of theshaft 10 and preferably lying in a plane parallel to a plane passing through this rotation axis A of theshaft 10. - As is visible in particular in
FIG. 5 , theguides 22 pass inside the device in such a manner as to act as a sliding link in relation to the two movingelements 5, guiding movement thereof between the position to stop the shaft and the position of disengagement therefrom, and vice versa. - In fact, the
guides 22 are configured to act as link of the sliding type in relation to theblocks 5, i.e. to constrain theblocks 5 to theframe 3, and consequently to theshaft 10, in such a manner as to allow radial movement thereof with respect to the rotation axis A of theshaft 10, movement caused by centrifugal force, and at the same time make theseblocks 5 rotate integrally with theframe 3 and therefore with thisshaft 10. - As already stated, the parts of the device can be mutually coupled by means of an interlocking constraint, and the
guides 22 passing inside the body of the device cooperate in maintaining the parts in assembled position. The applicant has verified that this method of interlocking constraint allows the total weight of the device to be limited, at the same time obtaining high reliability in the coupling of the parts by means of the action of theguides 22 which, as stated, cooperate in retaining the parts in assembled position, also providing rigidity to the device as a whole, preventing the centrifugal force to which it is subjected from causing loosening or even separation of the parts of which it is constituted. - In the same manner as the other embodiments described previously with reference to
FIGS. 1 and 2 , theframe 3 is substantially annular in shape and has a central portion, in the form of a sleeve, having an internal diameter such as to allow fitting thereof on theshaft 10, and a peripheral portion, also annular, which extends coaxially to theshaft 10, and acts as a support for theguides 22 which can be secured to the device, and in particular to theframe 3, by known means (such as interlocking, or screwing of threaded parts, etc.). - The
device 1 is equipped with two moving elements, or blocks, 5, each of which has substantially the shape of an annular sector and having dimensions equal to half of an annular sector, when viewed on a plane perpendicular to the rotation axis of theshaft 10. - In particular, in the embodiment illustrated in
FIGS. 4 and 5 , the movingelements 5 according toFIGS. 1B and 1C are preferably used, i.e. equipped with at least one portion of raised lateral surface 5.1. - Moreover, the
device 1 also comprises a fixedelement 2 which, as stated, can be constrained, for example, to parts of a watercraft or of a propulsion fixed with respect to theshaft 10, and which comprise a portion destined to come into friction contact with the moving elements, or blocks, 5. - This friction contact with the fixed
element 2 by theblocks 5 is generated, in the same manner as described with reference to the embodiment ofFIG. 1 , by means ofinclined portions 6 produced on the lateral surface of each movingelement 5, which are configured to come into contact with correspondinginclined surfaces 6′ arranged on the fixedelement 2. - As already stated, the friction generated by the contact of the
inclined portions elements 5 and of the fixedelement 2, and consequently the braking force exerted by thedevice 1 on theshaft 10, will depend on the inclination of thesurfaces - As will be apparent at this point of the description, due to the
guides 22, theblocks 5 can translate in a direction with a radial component between a position of disengagement from the fixed element 2 (upward inFIGS. 5 and 6 ) and a position of friction contact, with this fixed element 2 (downward inFIGS. 5 and 6 ), as a function of the rotation speed of theshaft 10. - Moreover, as can be seen in
FIG. 5 and more in detail inFIG. 6 , and in the same manner as the embodiment ofFIG. 1 , each moving element, or block, 5, is also connected to aspring 30, for example acting in extension or in compression, which constitutes part of the corresponding controlled contrast members of radial movement of theblocks 5 toward their position of disengagement from the fixedelement 2. These cylindricalhelical springs 30 also act as return means of theseblocks 5 toward said position of disengagement from the fixedelement 2. - Also in this embodiment, the elastic force exerted by each
spring 30 is calibrated in such a manner as to cause each movingelement 5 to remain in the position of friction contact with the fixedelement 2, at least until the centrifugal force Fc acting on theblocks 5, generated by rotation of theshaft 10, is insufficient to overcome the return force of thesesprings 30. When the centrifugal force Fc acting on theblocks 5 is sufficiently intense to overcome the return force of thesprings 30, theblocks 5 are caused to move radially by this centrifugal force Fc along theguides 22, toward the aforesaid position of disengagement from the fixedelement 2. - Also in this embodiment, the contrast members, and in particular the
springs 30, can be omitted in such a manner that movement of the movingelements 5 remains free. - Moreover, as can be seen in the detailed view of
FIG. 6 , and as already described in relation toFIG. 3 , according to a possible embodiment, the elastic force exerted by eachspring 30 can be modified manually by the user acting on suitable regulation means 40, which comprise ascrew 41 adapted to modify the extension of thisspring 30, modifying the preload thereof. - Moreover, as can be seen in
FIGS. 5 and 6 , the device comprises aspring guiding rod 31, adapted to prevent thespring 30, during compression or elastic return thereof to the non-deformed condition, from being subject to modifications in shape, mainly caused by the rotational motion to which the device, and consequently thespring 30, is subjected due to rotation of theshaft 10. Naturally, the spring-guiding rod can also be employed in the other embodiments of the device described previously with reference toFIGS. 1 , 2 and 3. - Operation of the
device 1 illustrated here, with reference to the three embodiments described above respectively with reference to theFIGS. 1 , 2 and 4, is as follows. - After having defined, during the design phase, the values of the masses of the moving
elements 5 and the elastic force that thesprings 30 must exert to counter movement of these movingelements 5, as a function of the angular velocity reached by theshaft 10 during operation thereof, thedevice 1 is assembled in such a manner that the fixedelement 2 is firmly integral with a fixed part with respect to theshaft 10, that theframe 3 is fitted on this latter and that the moving elements, or blocks, 5 are constrained to theframe 3 by the guides 20 (FIG. 1 ), by the pins 21 (FIG. 2 ) or by the guides 22 (FIGS. 4 and 5 ), with the same connection as the return springs, or contrast members, 30, also secured to theframe 3 and constrained to theblocks 5, in such a manner as to return them to a position of friction contact with saidfixed element 2. - When the
shaft 10, connected to a motor, is stopped, the return springs 30 retain theblocks 5 in friction contact with the fixedelement 2, so that theshaft 10 cannot rotate even in the case of external stresses. - During the motor start-up transient, for low angular velocities of the
shaft 10, even if thelinks blocks 5 to theframe 3 would allow theseblocks 5, stressed by the centrifugal force, to move from said position of friction contact with the fixedelement 2, the dimensions of theblocks 5 and of thesprings 30 are such that these latter efficiently counter the initial limited centrifugal force to which theblocks 5 are subjected. - When the rotation speed of the
shaft 10 increases, and consequently the centrifugal force Fc acting on theblocks 5 increases, these will start to move according to a direction, having in any case a radial component, defined by the type oflink springs 30. - In other words, the
blocks 5, stressed radially by the centrifugal force Fc and free to move at least in this radial direction due to thelinks element 2, disengaging therefrom, when the centrifugal force Fc, proportional to the angular velocity of theshaft 10, is sufficiently intense to overcome the elastic return force of the related springs 30. - When the motor coupled to the
motion transmission shaft 10 is switched off, or in any case the torque transmitted to thisshaft 10 is drastically decreased, if the rotation speed of theshaft 10, and consequently the centrifugal force Fc acting on theblocks 5, becomes less than the elastic return force of thespring 30, for example when theshaft 10 rotates through inertia, thesesprings 30 return theblocks 5 to their position of friction contact with the fixedelement 2 of thedevice 1, thereby causing theshaft 10 to stop immediately. - Although having made specific reference to the embodiments in which the device is equipped with
contrast members 30 of the movement of the movingelements 5, as will be apparent to those skilled in the art, operation of the device without thesecontrast members 30, wherein the movingelements 5 can move freely, is the same as described above. - In particular, from the condition of stopping of the
shaft 10 when the centrifugal force increases due to the increase in the number of revolutions, the braking force exerted by the friction contact between the movingelements 5 and the fixed element will decrease until being cancelled, causing movement of the movingelements 5 toward the position of disengagement from theshaft 10, in which this latter is free to rotate. When the centrifugal force decreases, for example in the case of stopping the motor connected to theshaft 10, the movingelements 5 will tend to return to the position to stop the shaft in the position of friction contact with the fixedelement 2 under the effect of their weight. - As stated, the
device 1 according to the present invention can advantageously be applied to the motion transmission shaft of a sailing craft, preferably equipped with a variable pitch propeller capable of adopting a “feathered” position when there is no driving torque, to promptly stop rotation of the motion transmission shaft of the propeller when the motor is not operating and does not transmit torques to the propeller. - In fact, the
device 1 according to the present invention allows the rotational motion of the shaft to be stopped when the motor is switched off and without thisdevice 1 the propeller, and consequently theshaft 10, would continue to rotate due to the inertia and to the flow of fluid caused by movement of the watercraft, thereby preventing automatic arrangement of the blades in their “feathered” position. - The
device 1 is designed in such a manner that the return force exerted by the contrast member (for example the springs 30) allows the movingelements 5 to be retained in position of contact with the fixedelement 2, and consequently locking of theshaft 10, when the engine is not operating and the propeller continues its rotational motion due to inertia and to the flow of fluids that strikes it. - In this manner, it is possible to promptly stop the
shaft 10 when no driving forces are acting thereon, in such a manner that the propeller can be arranged automatically in the position in which the blades are in “feathered” configuration and offer the least resistance to fluid. - Naturally, the force exerted by the
return members 30 is such as to allow movement of the movingelements 5 to the position of disengagement, releasing theshaft 10, when the engine is activated, thereby allowing normal operation of the propeller.
Claims (18)
1. A device for preventing and/or stopping a shaft rotation coupled to at least a motor, of the type comprising at least a first fixed element with respect to said shaft, and at least one moving element, and means to constrain said at least one moving element to said shaft in such a manner as to rotate integrally with said shaft and also be able to move between a position of friction contact with said least one fixed element, for stopping of said shaft, and a position of disengagement from said at least one fixed element, for release of said shaft, wherein said means to constrain said at least one moving element to said shaft comprise at least one link for movement of said at least one moving element along a direction having at least a radial component with respect to said shaft.
2. The device according to claim 1 , wherein in said position of friction contact of said at least one moving element with said at least one fixed element, at least one inclined surface of said at least one moving element is in contact with at least one corresponding inclined surface of said at least one fixed element.
3. The device according to claim 1 , wherein said means to constrain said at least one moving element to said shaft comprise at least one contrast member to counter in a controlled manner said movement of said at least one moving element, at least along said direction having at least a radial component, toward said position of disengagement from said at least one fixed element.
4. The device according to claim 3 , wherein said least one contrast member allows temporary movement of said at least one moving element to said position of disengagement from said at least one fixed element, only after exceeding a predefined angular velocity of said shaft.
5. The device according to claim 3 , wherein said contrast member is configured to return said at least one moving element to said position of friction contact with said at least one fixed element.
6. The device according to claim 5 , wherein said at least one contrast member comprises at least one spring.
7. The device according to claim 5 , wherein said at least one spring is integral with said shaft and is also constrained to said at least one moving element.
8. The device according to claim 1 , wherein said at least one link for movement of said at least one moving element along a direction having at least a radial component with respect to said shaft is a link of sliding type for translation of said at least one moving element with respect to said shaft along said direction having at least a radial component.
9. The device according to claim 8 , wherein said link of sliding type for movement of said at least one moving element along a direction having at least a radial component with respect to said shaft comprises at least one guide arranged in radial direction with respect to said shaft and/or in a direction perpendicular to the shaft and lying in a plane parallel to a plane passing through the rotation axis of said shaft.
10. The device according to claim 1 , wherein said at least one link for movement of said at least one moving element along a direction having at least a radial component with respect to said shaft is a pivot link.
11. The device according to claim 1 , wherein said at least one moving element has a circular ring shape viewed in a plane perpendicular to the rotation axis (A) of the shaft.
12. The device according to claim 10 , wherein it comprises two moving elements having a shape substantially equal to half of an annular sector viewed in a plane perpendicular to the rotation axis (A) of the shaft.
13. The device according to claim 1 , wherein said constraining means comprise at least one frame integral with said shaft, rotatable with said shaft, said at least one moving element being constrained to said at least one frame integral with the shaft in a manner rotatable with said shaft.
14. The device according to claim 13 , wherein said at least one frame constrained to said shaft has a substantially annular shape and is constrained to the outer surface of said shaft.
15. The device according to claim 1 , wherein it comprises means for regulation of said least one contrast member to modify the action of controlled countering of movement of said at least one moving element.
16. A watercraft comprising at least one motion transmission shaft from a motor to a propeller, comprising at least one device according to claim 1 .
17. The watercraft according to claim 16 , wherein said at least one motion transmission shaft is coupled to said motor through a hydraulic transmission.
18. The watercraft according to claim 16 , wherein said propeller is of the type with adjustable blades.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/IB2011/001520 WO2013001324A1 (en) | 2011-06-29 | 2011-06-29 | A device for preventing a shaft rotation |
Publications (1)
Publication Number | Publication Date |
---|---|
US20140291079A1 true US20140291079A1 (en) | 2014-10-02 |
Family
ID=44512994
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US14/127,587 Abandoned US20140291079A1 (en) | 2011-06-29 | 2011-06-29 | Device for preventing a shaft rotation |
Country Status (3)
Country | Link |
---|---|
US (1) | US20140291079A1 (en) |
EP (1) | EP2726370A1 (en) |
WO (1) | WO2013001324A1 (en) |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN107380392A (en) * | 2017-07-21 | 2017-11-24 | 苏州飞驰环保科技股份有限公司 | The locking device of stern tube shaft after a kind of ship is stopped |
CN110562431A (en) * | 2019-09-16 | 2019-12-13 | 广州船舶及海洋工程设计研究院(中国船舶工业集团公司第六0五研究院) | Ship, propulsion system, braking device and braking method thereof |
CN112109872A (en) * | 2020-08-04 | 2020-12-22 | 沪东中华造船(集团)有限公司 | Hydraulic locking system for ship shafting and control method |
US20210190154A1 (en) * | 2017-11-30 | 2021-06-24 | C Series Aircraft Managing Gp Inc. | Brake for transmission line of aircraft control surfaces |
US11377188B2 (en) * | 2017-03-10 | 2022-07-05 | Zf Friedrichshafen Ag | Saildrive arrangement |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN103434630B (en) * | 2013-09-05 | 2016-04-20 | 熊碧波 | Propeller for vessels stern tube shaft acceleration device |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3036667A (en) * | 1959-02-09 | 1962-05-29 | Horton Mfg Co Inc | Friction brakes |
GB1502616A (en) * | 1974-10-26 | 1978-03-01 | Elliston Evans & Jackson Ltd | Electrically controlled brake |
US4464127A (en) | 1982-04-08 | 1984-08-07 | Boudreaux Mark J | Shaft immobilizer apparatus |
-
2011
- 2011-06-29 US US14/127,587 patent/US20140291079A1/en not_active Abandoned
- 2011-06-29 EP EP11748989.8A patent/EP2726370A1/en not_active Withdrawn
- 2011-06-29 WO PCT/IB2011/001520 patent/WO2013001324A1/en active Application Filing
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11377188B2 (en) * | 2017-03-10 | 2022-07-05 | Zf Friedrichshafen Ag | Saildrive arrangement |
CN107380392A (en) * | 2017-07-21 | 2017-11-24 | 苏州飞驰环保科技股份有限公司 | The locking device of stern tube shaft after a kind of ship is stopped |
US20210190154A1 (en) * | 2017-11-30 | 2021-06-24 | C Series Aircraft Managing Gp Inc. | Brake for transmission line of aircraft control surfaces |
US11668357B2 (en) * | 2017-11-30 | 2023-06-06 | Airbus Canada Managing Gp Inc. | Brake for transmission line of aircraft control surfaces |
CN110562431A (en) * | 2019-09-16 | 2019-12-13 | 广州船舶及海洋工程设计研究院(中国船舶工业集团公司第六0五研究院) | Ship, propulsion system, braking device and braking method thereof |
CN112109872A (en) * | 2020-08-04 | 2020-12-22 | 沪东中华造船(集团)有限公司 | Hydraulic locking system for ship shafting and control method |
Also Published As
Publication number | Publication date |
---|---|
EP2726370A1 (en) | 2014-05-07 |
WO2013001324A1 (en) | 2013-01-03 |
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