BR102013032150B1 - starter impeller - Google Patents

Abstract

starting impeller. The present invention relates to a starter impeller (100) for torque transmission coupling between a drive shaft and a driven shaft of a motor comprising a clutch spring (6); a driven shaft (8) having a coupling end (81) with the clutch spring and a body (82) on which an output pinion (13) is coupled with torque transmission; a clutch spring housing (5) with a drive shaft facing face to which a plurality of planetary gears (1) driven by the drive shaft are rotatably coupled, and a driven shaft facing face provided with securing means (51) of a clutch spring, the clutch spring (6) being fixed to the housing clutch spring fastening means and being frictionally couplable to the coupling end (81) of the driven shaft, for torque transmission of the clutch spring housing to the shaft triggered; and a crown (11) with a toothed internal profile into which the planetary gears (1) are engaged.

Description

Patent Descriptive Report for "DEPARTURE DRIVER". The present invention relates to a starter impeller intended to initiate the operation of an internal combustion engine which is compact in construction using a planetary gear system and a clutch spring and has a freewheel mechanism. Description of the State of the Art Starter impellers are employed as transmission elements disposed between a starter motor and an internal combustion engine to assist in the commencement of operation of the internal combustion engine in both vehicle and stationary engines. The most common configuration of vehicular starter impellers comprises a free-wheel bearing-supported system where the free-wheel system connects the shaft of an electric motor to a drive pinion that engages the crown. crankshaft of the internal combustion engine. Still commonly in the prior art, the starter impeller may have a solenoid actuator that allows the pinion to be moved from a position away from the crankshaft crown to a position engaged with the crankshaft crown. A return spring is commonly responsible for returning the motion made by the solenoid actuator. The freewheeling system is a safety element for the electric motor against overloads induced by high revs from the normal operation of the internal combustion engine. The freewheel system selectively transmits torque from the electric motor to the combustion engine, decoupling the two engines when the combustion engine is accelerating the electric motor. The prior art document US5399129 describes a clutch spring reducing mechanism for application to internal combustion engine starters, among other applications. In the described embodiment, the reducing mechanism comprises the combination of an input shaft; a driven shaft; a planetary gear assembly disposed in a planetary crown, with at least one planetary gear coupled to the output element; a clutch spring assembly arranged in frictional contact with an input hub and an output hub, the output hub coupled to the planetary crown, and the input hub coupled to the input shaft.

In the mechanism described in this document, each spin-conal element needs to be biased, whether it be an axis, hub or gear. This bearing allows the transfer of rotational motion and restricts other movements such as vibratory motions from engine operation and radial and axial motions due to the contact forces of the gears. The more moving elements, the greater the need for staining.

It should also be noted that this mechanism has planetary gears arranged just before its hub and its driven shaft, so that vibrations from the transmission and reduction mechanism itself cannot be absorbed by any bearing disposed inside. The present invention seeks to provide an impeller with a more compact and modular construction, and with a reduced number of components and inner bearing elements. This reduction in the number of elements is due to the geometry of their internal devices, which enables these devices to perform the function of two or more traditional machine elements. The configuration of the starter impeller also seeks to allow the insertion of internal elements to absorb axial, radial and torsional vibrations.

Brief Description of the Invention The objects of the invention are achieved by a torque impeller coupling starter impeller between a drive shaft and a driven shaft of a motor, the impeller comprising; a clutch spring; a driven shaft having a coupling end with the clutch spring, and a body on which an output pinion is coupled with torque transmission; a clutch spring housing facing the drive shaft side, to which a plurality of planetary gears driven by the drive shaft are rotatably coupled, and a driven shaft facing face provided with means for securing a clutch spring, a. clutch spring being clamped to the housing clutch spring fastening means and being frictionally coupled to the coupling end of the driven shaft, for torque transmission of the clutch spring housing to the driven shaft; and a crown with a toothed internal profile into which the planetary gears are engaged.

The housing clutch spring securing means may comprise a channel within which one end of the clutch spring is clamped by interference.

One side of the clutch spring may be clamped to an outer surface or an inner surface of the housing clutch spring fastening means, and the opposite side of the clutch spring is frictionally couplable to the driven shaft.

Alternatively, the coupling end of the driven shaft has a larger diameter than the body and is provided with an open cavity to the side of the clutch spring housing, the cavity having an inner surface and an outer surface, and the clutch spring being couplable. by friction with the inner surface or the outer surface of said cavity. The clutch spring housing is at least partially housed within the shaft of the shaft coupling end and an intermediate bushing is disposed between the inner surface of the driven shaft cavity and a part of the clutch spring housing housed within the cavity.

Alternatively, the clutch spring housing is provided with three equidistant planetary gear pins to which three planetary gears are coupled, and the clutch spring housing further comprises means for coupling a drive shaft, provided with a drive shaft bushing.

Preferably, inside the crown are planetary gears, at least a portion of the clutch spring and at least a portion of the clutch spring housing, the crown further comprising means for attachment to a motor housing. The starter impeller may further comprise a cap coupled externally to the clutch spring housing and at least partially internally to the crown, and a cap bushing disposed between the impeller cap and the crown, wherein the clutch spring and coupling end of the driven shaft are housed inside the cover. An intermediate bushing is arranged between the inner surface of the cover and the coupling end of the driven shaft.

Alternatively, the driven shaft comprises a damping element mounted by interference on its coupling end, and a torsion-proof shaft raceway piece mounted on the damping element, wherein the clutch spring is frictionally coupled to the outer surface of the part. The damping element consists of one of elastomeric material and a torsion spring.

Alternatively, the driven shaft has splines for coupling with a splined inner profile of the output pinion, the pinion comprising a circular profile outer portion and a toothed outer portion. At least two washers may be mounted on the outer circular profile portion of the output pinion. A damping spring and fork housing are mounted on the outer circular profile portion of the output pinion, the damping spring disposed compressed between the fork housing and the toothed outer portion of the output pinion. Alternatively, the starter impeller comprises a fork housing mounted on the driven shaft between the output pinion and the clutch spring coupling end, a disposed damping spring compressed between the fork housing and the output pinion; cap coupled to one end of the driven shaft opposite the coupling end of the clutch spring, a return spring arranged compressed between the output pinion and cap. Alternatively, the output pinion comprises a recess in the inner surface of each of its ends forming spaces between it and the driven shaft, the fork housing comprises a recess in the inner surface of its end facing the output pinion, forming a In the space between it and the driven shaft, the damping spring has one end engaged in the recess of the fork housing and the other end engaged in one recess of the output pinion, the return spring has one end engaged in the other recess of the output pinion. . Alternatively, the fork housing has splined inner profile for splined coupling in the driven shaft body, the groove in the inner surface of the pinion facing the fork housing has a slot for securing one end of the damping spring, the groove in the The inner surface of the fork housing has a slot for securing the other end of the damping spring, a locking ring is disposed in the recess of the fork housing, securing one end of the damping spring, and a locking ring is disposed in the recess of the pinion. the other end of the damping spring.

The objects of the invention are also achieved by a starting impeller for torque transmission coupling between a drive shaft and an output pinion, comprising a clutch spring; an output pinion gear; a drag piece provided with torsion-proof coupling means with a drive shaft; a torsion-coupled clutch spring housing with the drag piece; the clutch spring being torsionally clamped to the clutch spring housing and frictionally coupling to the output pinion, for torque transmission from the clutch spring housing to the output pinion. The starter impeller may further comprise at least one torsion-mounted radial damping member between the drag portion and the clutch spring housing. The at least one radial damping member may be a plurality of radially distributed elastomer segments along an inner surface of the drag piece and in contact with the clutch spring housing. The impeller may further comprise an axial damping element provided between the clutch spring housing and the drag piece. The axial damping element may be a plate spring.

BRIEF DESCRIPTION OF THE DRAWINGS The present invention will hereinafter be described in more detail based on an exemplary embodiment shown in the drawings. The figures show: Figure 1 is a schematic cross-sectional view of a starter impeller embodiment of the present invention.

Figure 2 is an exploded view showing the internal elements of the starter mode shown in Figure 1.

Figure 3 is a perspective view of the starter clutch spring housing shown in Figure 1.

Figure 4 is a perspective view of the starter impeller clutch spring shown in Figure 1.

Figures 5 to 8 are schematic cross-sectional views showing details of the freewheel system of other embodiments of the starter impeller of the present invention.

Figures 9 and 10 are exploded views showing the internal elements of the driven shaft of the starter mode shown in Figure 8.

Figures 11 to 13 are schematic cross-sectional views showing details of alternative embodiments of the starter impeller advancement system of the present invention.

Figure 14 is a schematic cross-sectional view of another alternative embodiment of the starter impeller of the present invention.

Figure 15 is an exploded view showing the internal elements of the starter impeller shown in figure 14.

Detailed Description of the Figures Figure 1 is a cross-sectional view of one embodiment of the starter impeller of the present invention, the starter being provided with a freewheel system A and a forward system B. The wheel system Free A consists essentially of a clutch spring housing 5 coupled to a driven shaft 8 by means of a clutch spring 6 which torque transmits between the housing 5 and the driven shaft in a single direction of rotation. Feed system B essentially consists of an output pinion 13 to which the driven shaft torque 8 is transmitted, and the output pinion is coupled directly over the driven shaft body 82. Figure 2 individually illustrates each element of this embodiment of the invention. The starter impeller has a planetary speed reduction mechanism consisting of a plurality of planetary gears 1 which are driven by a drive shaft (not shown) belonging, for example, to a starter motor, with the drive shaft operating. as solar gear of the reducing mechanism.

In the embodiments of the invention illustrated herein, three planetary gears 1 rotationally coupled to the drive shaft are used. Planetary gears 1 are rotatably coupled to a clutch spring housing 5, which has a disc-shaped face facing the drive shaft and a face facing a drive shaft 8. In this embodiment of the invention, three pins 3 are fixed equidistant from each other on the face of the clutch spring housing 5 facing the drive shaft, and on each of these pins 3 a bushing 2 is mounted. On each of these pin 2 and bushing 3 a planetary gear 1 is mounted so that each gear is biased and positioned by said pins and bushings. The radially uniform distribution of the planetary gears gives this mechanism a known advantageous balance in transmission forces. The clutch spring housing 5 further comprises means for coupling a drive shaft 53, which, in this embodiment of the invention, consist of a hole in the disc-shaped face provided with a bushing 4 for rolling the drive shaft. This hole can extend in the form of a cylinder towards the driven shaft 8 for better bearing, as best seen in figure 3.

On the face facing a driven shaft, the clutch spring housing 5 is provided with means for securing the clutch spring 51 to which the clutch spring 6 is secured by interference. In this embodiment of the invention, the means for securing the clutch spring 51 consists of a channel into which one end of the clutch spring 6 is interference clamped, as shown in Figures 3 and 4. One end of the clutch spring 6 is bent into shape. "L", compatible with the shape of the channel in the clutch spring housing 5, and is inserted into said channel. The clutch spring 6 is further frictionally couplable to a clutch spring end 81 of the driven shaft 8 by transmitting the torque of the clutch spring housing 5 provided by the planetary gears to the driven shaft 8. That end of the driven shaft 8 is facing the side of the clutch spring housing 5.

According to preferred embodiments of the invention, said coupling end 81 of driven shaft 8 has a larger diameter portion relative to its body 82, which is provided with an open cavity for the side of the clutch spring housing 5, forming an inner surface and an outer surface of said coupling end 81. The clutch spring 6 may be frictionally coupled to the inner surface or the outer surface of said cavity.

As can be seen from figures 1 and 5 to 8, at least a portion of the clutch spring housing 5 is housed within the coupling end cavity 81 of the shaft. In the embodiments of the invention shown in FIGS. 1 and 5, an intermediate bushing 7 is disposed between the inner surface of the driven shaft 8 and the portion of the clutch spring housing 5 disposed within the cavity, bearing the driven shaft 8 over the housing. 5. The coupling end geometry 81 of the driven shaft 8 resembles a hub, so that the shaft can be supported internally and externally on sliding bearings, such as the intermediate bushing 7. Thus, it is It is possible to reduce the number of internal elements of the impeller and, consequently, the number of bearings. This reduction in the number of mechanical elements saves internal space on the device, enabling the insertion of vibration damping elements, as will be discussed in the following embodiments.

In the embodiment of the invention shown in figures 1, 2, 9, 10, and 13, the driven shaft 8 further has helical splines in its body 82 for coupling the output pinion 13 or other part to which its torque is transmitted.

A crown 11 is coupled outside the gears 1 and clutch spring housing 5. This crown 11 has a toothed internal profile into which the planetary gears 1 are engaged. Thus, the planetary gears 1 are housed inside the crown 11, in its largest internal diameter part. In a smaller inner diameter portion of the crown 11, at least a portion of the clutch spring 6 and at least a portion of the clutch spring housing 5 are housed as shown in Figures 5, 6, 7 and 8. The crown 11 it further comprises, on its outer surface, means for attachment to an engine housing, such as pin or screw fittings, as this crown is responsible for the attachment and holding of the impeller in the housing of an engine.

An impeller cap 9 is fixed externally to the clutch spring housing 5 and at least partially internally to the crown 11, as can be seen from figures 5, 6, 7 and 8. That cap 9 is biased inside the crown 11 by a bushing of the lid 10 disposed between the crown and a portion of the lid 9 disposed therein. The output pinion 13 is mounted on the driven shaft 8 to transmit torque to a motor. In the embodiment of the invention shown in FIG. 12, the output pinion has helical splines in its internal profile compatible with the helical splines in the driven shaft body 82, enabling the fastening and torque transmission between the driven shaft 8 and the output pinion. 13. In the embodiments of the invention shown in figures 2, 11 and 13, a pinion bushing 14 is coupled between the driven shaft 8 and the pinion to bias the pinion onto the driven shaft. A driven shaft cover 15, shown in figures 1, 2, 11, 12 and 13, is attached to the free end of the driven shaft, keeping the entire assembly assembled.

In the embodiments shown in figures 1, 2 and 11, the output pinion 13 has a toothed outer portion 132 and a circular toothed outer portion 131 free of gear teeth. In the embodiment shown in figures 1 and 2, two circular washers 12 are mounted on the circular profile portion, making it possible to attach a fork of an engine advance system, not shown in the figures, which acts by shifting the output pinion 13 to a position engaged with a engine's gear crown during its start.

Fig. 5 is a schematic cross-sectional view of an alternative embodiment of the starter impeller freewheel system of the present invention. In this embodiment, the clutch spring housing 5 has an axial projection 52 extending toward the driven shaft 8, in which the clutch spring fastening means 51 are formed. The clutch spring 6 has no bends at its end and is mounted with interference of some of its turns on the clutch spring fastening means 51 in the form of axial projection. The other turns of the clutch spring 6 are frictionally coupled to the outer surface of the coupling end 81 of shaft 8. The number of turns of the clutch spring 6 overlapping with the securing means 51 of the clutch spring housing 5 is approximately the same. number of turns of the clutch spring 6 overlapping the driven shaft 8. A portion of the axial projection 52 of the clutch spring housing 5 is housed within the cavity formed in the coupling end 81 of the driven shaft 8, and the intermediate bushing 7 is disposed between the inner surface of the driven shaft cavity 8 and this axial projection 52 of the clutch spring housing 5.

Figure 6 shows a schematic cross-sectional view of another alternative embodiment of the starter impeller freewheel system of the present invention. In this embodiment, the axial projection 52 of the spring housing 5 fits within the cavity at the coupling end 81 of the shaft 8. The clutch spring 6 is engaged with the channel-shaped fastening means 51 formed in the clutch spring housing 5, as shown in figures 3 and 4, and frictionally engages the inner surface of the cavity at the coupling end 81 of the shaft 8. Thus, when the spring housing 5 rotates in the reverse direction to the winding of the spring turns If expanded, frictional coupling of spring 6 with driven shaft 8 occurs. In this embodiment, the intermediate bushing 7 is disposed between the outer surface of the driven shaft 8 and the inner surface of the impeller cap 9, bearing the driven shaft over the shaft. impeller cover 9.

Figure 7 is a schematic cross-sectional view of another alternative embodiment of the starter impeller freewheel system of the present invention. In this embodiment, the clutch spring clamping means 51 of the clutch spring housing 5 are constituted by an axial projection forming a circular channel of internal diameter compatible for interference clutch mounting 6. In such an arrangement, the outside diameter of the clutch spring 6 is in contact with the inside diameter of the circular channel of the clutch spring housing 5. The clutch spring 6 is frictionally coupled to the inner surface of the driven shaft cavity 8. The number of turns of clutch spring 6 coupled by interference with the clutch spring housing 5 is approximately the same number of clutch spring turns 6 a-copied by friction to the driven shaft 8. The intermediate bushing 7, in this case, is disposed between the outer surface of the driven shaft 8 and the inner surface of the cover 9 of the impeller 9 by biasing the driven shaft over the impeller cap 9.

Figure 8 is a schematic cross-sectional view of another alternative embodiment of the starter impeller freewheel system of the present invention. In this embodiment, the clutch spring fastening means 51 of the clutch spring housing 5 are also formed in an axial projection 52 of the compatible outside diameter clutch housing for mounting with interference to the inside diameter in spring 6. This spring 6 engages by interference with the outer surface of coupling end 81 of shaft 8, which in this case consists of separate parts e2, e3 provided with their own damping, as will be described later in more detail. The number of clutch spring turns 6 overlapping the clutch spring housing retaining means 5 is approximately the same number of clutch spring turns 6 overlapping the driven shaft 8. Intermediate bushing 7 is disposed between the surface of the cavity at the coupling end 81 of the driven shaft 8 and an axial projection 52 of the clutch spring housing 5 housing within the shaft cavity 8.

9 and 10 show the driven shaft shown in the assembly of figure 8. Shaft 8 comprises an interference damping element e2 on its coupling end 81, and a torsion-mounted shaft raceway e1 on the damping element e2. In this case, the clutch spring 6 is frictionally coupled to the outer surface of the axle track part e1. In the embodiment shown in Figure 9, the damping element e2 is comprised of an elastomeric material ring mounted between shaft raceway part e1 and shaft body 82. The shaft end has radial locks compatible with the internal geometry of damping element e2. and the damping element e2 has radial locks compatible with the internal geometry of the axle track piece e1. In figure 10, the damping element e2 'consists of a torsion spring having a bent end in the outer radial direction. The damping element e2 'is mounted between the eT shaft track piece and the shaft end 81. The shaft end 81 is integrally mounted to the damping element e21 by frictional interference, while the shaft track piece e1 * has an axial groove for engaging and securing the bent spring end of the damping element e2 ‘. In the embodiments of figures 9 and 10, the incision of such damping element e2, e2 'provides radial damping of the impeller located within the freewheel system.

11 illustrates one embodiment of the axial damping output pinion drive system 13. In this embodiment, a damping spring 18 and a part acting as a fork housing 16 are mounted on the outer circular profile portion of the output pinion 13. This fork housing 16 consists of a cylindrical part provided with a perforation compatible with a coupling. the shaft, and with a channel formed in its outer race, to which a feed system fork may be attached, not shown in the figures. The damping spring 18 is compressed in the assembly between the fork housing 16 and the toothed outer portion 132 of the output pinion 13 so that it is arranged slightly compressed between these two pieces for better axial damping. The fork housing 16 is fixed to the pinion by a retaining ring 17 positioned in a channel of the outer circular profile portion of the output pinion 13 and a compatible channel on the inner surface of the fork housing 16. The damping spring 18 has the function of absorbing impacts generated during output pinion gear 13 for smooth coupling with the crankshaft crown of the engine on which the impeller is installed.

Figure 12 illustrates another embodiment of the output pinion drive system 13g with radial damping mechanism in addition to axial damping. Radial damping is responsible for absorbing impacts generated by motor acyclism in the geared phase as well as gaps between gear teeth. In this embodiment, the output pinion 13g has its entire toothed profile outer surface 132. A fork housing 16, the damping spring 18, the pinion are mounted on the driven shaft in sequence from its coupling end 81 in sequence. 13g, a return spring 19 and driven shaft cover 15, which holds all elements on the shaft. Pinion 13g has internal helical splines that engage the helicoidal splines of the driven shaft, receiving torque from the starter impeller. The output pinion 13g comprises a recess in the inner surface of each end, forming two spaces between it and the driven shaft. The fork housing 16 also comprises a recess in the inner surface of its end facing the output pinion, forming a space between it and the driven shaft S. The damping spring 18 is disposed with an end engaged in the recess of the fork housing 16 and the other end engaged in a recess of the output pinion 13g. Return spring 19 is disposed with one end engaged with the other recess of output pinion 13g. Thus, after the feed system fork moves the pinion 13g, the pinion is returned to the original position by return spring 19.

Figure 13 shows another embodiment of the output pinion drive system 13h, which is provided with axial and radial damping between the pinion and the shaft. In this embodiment, the output pinion 13h has its entire outer surface with toothed profile 132, but has no grooves in the internal profile. A fork housing 16, a damping spring 18, the output pinion 13h which is mounted on a pinion bushing 14 disposed between it and the shaft for bearing are mounted on the driven shaft from the coupling end 81; the return spring 19 and the driven shaft cover 15, the latter being responsible for retaining all the elements on the shaft. In this embodiment, the fork housing 16 has splined internal profile for coupling with driven shaft splines. The damping spring 18 has both ends bent in the outer radial direction. The output pinion 13h comprises a recess in the inner surface of each end. In the recess facing the fork housing 16 a groove for fixing the end bend of the damping spring 18 is formed. The fork housing 16 also comprises a recess in the inner surface of its end facing the output pinion 13h, provided with slot in which the other folded end of the damping spring 18 is fixed.

A locking ring 20 is disposed in the recess of the fork housing 16, attaching one end of the damping spring 18 to the twist-proof fork housing 16, and another locking ring 20 is disposed in the recess of the output pinion 13h of the fork. side facing the fork housing 16, securing the other end of the damping spring 18 to the torsion proof output pinion 13h.

Thereby, the torque is transmitted from the driven shaft 8 to the fork housing 16, and then transmitted to the damping spring 18, and then to the output pinion 13h. For this reason, the damping spring 18 promotes axial and radial damping.

In any of the embodiments described above, the spring 6 operates by being twisted in a first direction when the drive shaft is accelerating the output shaft 8, i.e. when starting the engine to which the impeller is coupled. This twist increases the interference pressure between output shaft 8 and clutch spring 6, ensuring impeller transmission. Spring 6 can be designed to completely lose coupling with driven shaft 8 at a certain torque value, thus acting as a safety mechanism that acts in the event of overloading the starter motor.

After starting the driven motor, the driven shaft 8 accelerates the drive shaft, and the clutch spring 6 is twisted in the opposite direction. This twist relieves the interference pressure between driven shaft 8 and clutch spring 6 when clutch spring 6 mates by friction of its inner surface with driven shaft 8.

In figure 14 an alternative embodiment of the starter impeller is shown. The starter impeller of this alternative embodiment is more compact and is not provided with a reduction mechanism. This impeller is also used for transmitting starting torque from an electric starter motor to a combustion engine. The drive shaft of the electric motor is torsion-proof mounted on one side of a drag piece C to transmit the torque to that part. The side of the drive piece C where the shaft is mounted has a smaller inside diameter and torsion-proof coupling means with the drive shaft, such as a thread or splines. The opposite side of drag piece C has a larger inside diameter. A washer 12i may be mounted on the outer surface of the drag piece at the coupling end with the drive shaft.

Within the larger inner diameter side of the drag piece C are engaged a plurality of radial damping elements in the form of radially distributed elastomer segments 21 along the inner surface of the drag piece C. The elastomer segments may be coupled by interference within small recesses 221 compatible with elastomer segments 21. Thus, the rotational torque of drag piece C is also transferred to elastomer segments 21. Alternatively, other radial damping elements may be used. performing this same function, such as a torsion spring mounted between the drag part C and clutch spring housing 5i.

Inside the drag piece C is mounted a clutch spring housing 5i. The coupling between the drag part C and clutch spring housing 5i enables torque transmission from the drag part C to the clutch spring housing 5i.

In the embodiment of the invention shown in FIGS. 14 and 15, the clutch spring housing 5i has a disc-shaped face that rests against the transition wall between the smallest diameter and the largest internal diameter portion of the drag piece C This disc-shaped face may be provided with recesses in the outer edges, where the elastomer segments 21 engage or contact, which assist in the torque transmission of the carrier C to the clutch spring housing 5i and absorb radial stresses on the transmission. However in alternative embodiments of the invention, the drag part C may transmit rotational torque directly to the clutch spring housing 5i. From the disc-shaped face extends a cylindrical portion 51i of the clutch spring housing 5i, provided with a central perforation. On the outer surface of the cylindrical portion is housed a clutch spring 6i which is torsionally secured to the clutch spring housing 5i. The spring 6i may be interference-coupled to this cylindrical portion and / or may be fixed in a channel formed on the disc-shaped face of the clutch spring housing 5i.

An axial damping element 22 may further be provided between the clutch spring housing 5i and the drag piece C, promoting absorption of axial stresses in the transmission. Such axial damping element 22 may be a disc spring, capable of absorbing high axial stresses caused by the movement of an output pinion, taking up very small space. The output pinion Pi has a larger outer and inner diameter portion with a cylindrical outer surface and a smaller outer and inner diameter portion with a toothed surface. The largest diameter portion of the output pinion Pi is coupled within the drag piece C and is disposed between the outer raceway of the clutch spring 6i and the inner surface of the drag piece C and may also be in contact with the elastomer elements. 21. When the impeller is driven by the drive shaft, the clutch spring 6i expands and frictionally engages with the inner surface of the output pinion, imparting rotational torque to it, performing the freewheeling function.

An Ei bushing is coupled within the smaller internal diameter portion of the pinion pin to bias the drive shaft. An intermediate bushing 7i is provided between the drag piece C and the outer surface of the larger diameter portion of the output pinion Pi, biasing the pinion over the drag piece C. An impeller cap 9i overlaps the intermediate bushing 7i and holds the assembly mounted.

Having described some examples of embodiment, it should be understood that the scope of the present invention encompasses other possible variations, being limited only by the content of the claims, including the possible equivalents thereof. Reference Numbers 1 - planetary gear 2 - planetary gear bushing 3 - planetary gear pin 4 - first shaft bushing 5, 5i - clutch spring housing 51 - means for securing a clutch spring 53 - means for coupling a shaft drive 6, 6i spring clutch 7, 7i - intermediate bushing 8 - driven shaft 81 - driven shaft coupling end 82 - driven shaft body e1, e1 '- driven shaft track piece e2, e2' - shaft damping driven 82 - shaft body driven 9, 9i - impeller cap 10 - cap bushing 11 - crown 12, 12i - washers 13, 13, 13g, 13h - output pinion 131 - outer circular portion of output pinion 132 - toothed outer portion of output pinion 14 - pinion bushing 15 - driven shaft cover 16 - fork housing 17 - retaining ring 18, - damping spring 19 - return spring 20 - locking rings 21 - damping element radial 22 - love element axial support 100 - starting thrust C - drag piece Ei - bushing Pi - output pinion.

Claims (23)

1. Starting impeller (100) for coupling with torque transmission between a drive shaft and a driven shaft of a motor, characterized in that it comprises a clutch spring (6); a driven shaft (8) having a coupling end (81) with the clutch spring, and a body (82) on which an output pinion (13) is coupled with torque transmission; a clutch spring housing (5) with a drive shaft-facing face to which a plurality of drive shaft driven planetary gears (1) are rotatably coupled, and a driven shaft-facing face provided with securing means (51) of a clutch spring, the clutch spring (6) being attached to the clutch spring retaining means (51) of the housing (5) and being frictionally couplable to the coupling end (81) of the driven shaft (8), for torque transmission from clutch spring housing (5) to driven shaft (8); and a crown (11) with a toothed internal profile into which the planetary gears (1) are engaged. Starting impeller (100) according to Claim 1, characterized in that the housing clutch spring securing means (51) comprises a channel into which one end of the clutch spring (6) is secured by interference. Starting impeller (100) according to Claim 1, characterized in that one side of the clutch spring (6) is fixed by interference with an outer surface or an inner surface of the spring clamping means (51). housing clutch (5), and the opposite side of the clutch spring is frictionally couplable to the driven shaft (8). Starting impeller (100) according to one of Claims 1 to 3, characterized in that the coupling end (81) of the driven shaft has a larger diameter than the body (82) and is provided with a open cavity to the side of the clutch spring housing (5), the cavity having an inner surface and an outer surface, and the clutch spring (6) being frictionally couplable to the inner surface or outer surface of said cavity. Starter impeller (100) according to Claim 4, characterized in that the clutch spring housing (5) is at least partially housed within the coupling end cavity (81) of the shaft (8). . Starting impeller (100) according to Claim 5, characterized in that an intermediate bushing (7) is arranged between the inner surface of the driven shaft cavity (8) and a part of the clutch spring housing ( 5) housed inside the cavity. Starting impeller (100) according to one of Claims 1 to 6, characterized in that the clutch spring housing (5) is fitted with three equidistant planetary gear pins (3) to which three gears are coupled. clutch spring housing (5) further comprises means for coupling a drive shaft (53), provided with a bushing (4) for biasing the drive shaft. Starter impeller (100) according to one of Claims 1 to 7, characterized in that the planetary gears (1), at least a portion of the clutch spring (6), are housed inside the crown (11). and at least a portion of the clutch spring housing (5), the crown (11) further comprising means for attachment to a motor housing. Starting impeller (100) according to one of Claims 1 to 8, characterized in that it further comprises a cap (9) coupled externally to the clutch spring housing (5) and at least partially internally to the crown (11). , and a cap bushing (10) disposed between the impeller cap (9) and the crown (11), with the clutch spring (6) and coupling end (81) of the driven shaft being housed within the cap (9). Starting impeller (100) according to Claim 9, characterized in that an intermediate bushing (7) is arranged between the inner surface of the cover (9) and the coupling end (81) of the driven shaft. Starting impeller (100) according to one of Claims 1 to 10, characterized in that the driven shaft (8) comprises a damping element (e2, e2 ') interference-mounted on its coupling end (81). ), and a torsion-proof raceway piece (e1, e1 ') mounted on the damping element (e2, e2'), the clutch spring (6) being frictionally coupled to the outer surface of the axis track (e1, eV). Starter impeller (100) according to Claim 11, characterized in that the damping element (e2, e2 ') consists of one of the elastomeric material and a torsion spring. Starter impeller (100) according to one of Claims 1 to 12, characterized in that the driven shaft (8) has coupling grooves with a splined inner profile of the output pinion (13), pinion shaft comprising a circular profile outer portion (131) and a toothed outer portion (132). Starter impeller (100) according to Claim 13, characterized in that at least two washers (12) are mounted on the outer circular profile portion of the output pinion (13). Starter impeller (100) according to Claim 13, characterized in that a damping spring (18) and a fork housing (16) are mounted on the outer circular profile portion of the output pinion ( 13), the damping spring (18) disposed compressed between the fork housing (16) and the toothed profile outer portion of the output pinion (13). Starting impeller according to any one of Claims 1 to 12, characterized in that it comprises a fork housing (16) mounted on the driven shaft (8) between the output pinion (13g) and the end of the coupling (81) with the clutch spring, a damping spring (18) disposed compressed between the fork housing (16) and the output pinion (13g), a cap (15) coupled to one end of the driven shaft opposite the end coupling spring (81) of the clutch spring, a return spring (19) arranged compressed between the output pinion (13g) and the cover (15). Starter impeller (100) according to Claim 16, characterized in that the output pinion (13g) comprises a recess in the inner surface of each of its ends, forming spaces between it and the driven shaft ( 8), the fork housing (16) comprises a recess in the inner surface of its end facing the output pinion (13g), forming a space between it and the driven shaft (8), the damping spring (18) has With one end engaged in the recess of the fork housing and the other end engaged in one recess of the output pinion, the return spring (19) has one end engaged in the other recess of the output pinion. Starter impeller according to Claim 17, characterized in that: the fork housing (16) has a splined inner profile for spline coupling on the driven shaft body (82), the recess on the inner surface of the pinion (13g) facing the fork housing (16) has a slot for fixing one end of the damping spring (18), the recess in the inner surface of the fork housing (16) has slot for fixing the other end of the damping damping spring (18), a locking ring (20) is disposed in the recess of the fork housing (16), securing one end of the damping spring (18), and a locking ring (20) is disposed in the recess of the fork housing. output pinion (13g) securing the other end of the damping spring (18). Starter impeller (100) for coupling with torque transmission between a drive shaft and an output pinion, characterized in that it comprises a clutch spring (6i); an output pinion (Pi) a drag piece (C) provided with a torsion-proof coupling means with a drive shaft, a torsion-coupled clutch spring housing (5i) with the drag piece (C) , the clutch spring (6) being torsionally secured to the clutch spring housing (5) and frictionally coupling to the output pinion (Pi) for torque transmission of the clutch spring housing (5) to the clutch sprocket. exit (Pi). Starter impeller according to claim 20, characterized in that it comprises at least one radial damping element (21) mounted torsion-proof between the drag part (C) and the clutch spring housing (5i) Starter impeller according to claim 21, characterized in that it comprises, as at least one radial damping element (21), a plurality of radially distributed elastomer segments along an inner surface of the carrier (C ) and in contact with the clutch spring housing (5i). Starting impeller according to one of Claims 19 to 22, characterized in that it further comprises an axial damping element (22) provided between the clutch spring housing (5i) and the drag part (C). . Starter impeller according to Claim 23, characterized in that the axial damping element (22) is a disc spring.