Abstract:
A pin for connecting a gear to a supporting member has a first and a second longitudinal end portion connectable to the supporting member; a first intermediate portion extending from the first end portion; and a second intermediate portion extending from the second end portion, and which differs in size from the first intermediate portion and has a flexural strength differing from that of the first intermediate portion.

Description:
The present invention relates to a pin for connecting gears to a supporting member. 
     More specifically, the present invention relates to a supporting pin which may be used to advantage, though not exclusively, in epicyclic gear trains for transmitting severe loads in general, and in epicyclic gear trains of aircraft transmissions in particular, to which the following description refers purely by way of example. 
     BACKGROUND OF THE INVENTION 
     Aircraft transmissions normally comprise an epicyclic gear train in turn comprising a sun gear, a ring gear, and a number of planet wheels interposed between the sun and ring gears and supported on a planet carrier. 
     In most applications, the planet carrier comprises two substantially platelike elements positioned facing each other on opposite axial sides of the planet wheels, and connected integrally to each other by a number of the gear train in relative motion. 
     To eliminate the above drawbacks, dedicated supporting pins are used, which have opposite elastic end portions of the same size, which deform elastically alongside deformation of the platelike elements and respective tenons to ensure the gears mesh correctly at all times. Also, between the carrier and the supporting body, provision is and must be made for a load balancing assembly, which comprises a number of axial arms connected integrally to the supporting body; and, for each arm, a respective connecting member lying in a plane perpendicular to the sun and ring gear axes and through the center lines of the planet wheels. 
     Known balancing assemblies of the above type are particularly complex, are extremely expensive to both produce and maintain, and, being highly stressed, are subject to frequent breakdowns and malfunctioning. 
     SUMMARY OF THE INVENTION 
     It is an object of the present invention to provide a supporting pin designed to solve the aforementioned problems in a straightforward, low-cost manner. 
     According to the present invention, there is provided a pin for connecting a gear to a supporting member; the pin having a respective axis, and comprising a first and a second longitudinal end portion connectable to said supporting member; a first intermediate portion extending from said first end portion; and a second intermediate portion extending from said second end angularly equally spaced cross members or tenons normally integral with both the platelike elements. Each of the planet wheels is connected to the carrier by a respective supporting pin, the opposite ends of which are each connected to a respective platelike element, and to which the respective planet wheel is in turn normally connected via the interposition of a bearing, normally a friction bearing. 
     During operation of the gear train, the carrier is stressed by forces which, in some cases, result in deformation of the carrier and, in particular, in displacement of the two platelike elements with respect to each other. 
     Displacement of the platelike elements in turn results in deformation of both the tenons and the supporting pins, the axes of which pass from an ideal work or rest condition parallel to the axes of the sun and ring gears, to a real or critical work condition in which they form, with the sun and ring gear axes, an angle of other than zero and which varies according to the intensity of the forces transmitted. 
     Deflection of the pin axes and, hence, of the respective planet wheel axes with respect to the ring and sun gear axes results in uneven distribution of the contact pressures between the planet wheel teeth and those of both the sun and ring gear, which in turn results, not only in general malfunctioning of the gear train, but also in rapid wear of the contacting parts of portion; characterized in that said first and said second intermediate portion differ from each other in size and in flexural strength. 
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS 
     A non-limiting embodiment of the invention will be described by way of example with reference to the accompanying drawings, in which: 
     FIG. 1 shows schematically, and with parts removed for clarity, an epicyclic transmission featuring a number of supporting pins in accordance with the present invention; 
     FIG. 2 shows a larger-scale section along line II—II in FIG. 1; 
     FIG. 3 shows a section of a detail in FIG.  2 . 
    
    
     DETAILED DESCRIPTION OF THE INVENTION 
     Number  1  in FIGS. 1 and 2 indicates as a whole an epicyclic transmission for an aircraft (not shown). Transmission  1  comprises a sun gear  2  rotating about a respective axis  3 ; a rotating ring gear  4  coaxial with axis  3 ; and a number of planet wheels  5 —in the example shown, five—meshing with ring gear  4  and sun gear  2 , and connected to a planet-carrier  6  so as to rotate about respective axes  7  parallel to one another and to axis  3 . 
     Carrier  6  extends coaxially with axis  3 , is formed in one piece from metal material, and comprises two facing platelike bodies  8  and  9  (FIG.  2 ). In the particular example shown, body  8  is connected integrally in known manner—e.g. by means of a bracket  8   a  and screws or pins not shown—to a fixed body  10  (shown schematically) supporting carrier  6 . Carrier  6  also comprises a number of known tenons (not shown) extending axially between, and integral with, platelike bodies  8  and  9 . In a variation not shown, body  8  is connected integrally to an output shaft, and ring gear  4  is connected integrally to a fixed body. 
     Each planet wheel  5  has a central axial through hole  12 , and is connected to platelike bodies  8  and  9  of carrier  6  by a respective supporting device  13 . As shown in FIG. 2, device  13  extends through hole  12 , and comprises a supporting pin  14  having a respective axis  15 ; and a bushing  16  made of antifriction material and interposed between pin  14  and the relative planet wheel. 
     Pin  14  is asymmetrical with respect to a plane P (FIGS. 2 and 3) perpendicular to axis  15  and through the center line of pin  14 , and is defined laterally by a cylindrical supporting surface  18  coaxial with axis  15  and having a straight generating line. Pin  14  comprises two opposite tubular longitudinal end portions  19  and  20 , which, in the particular example shown, engage, with substantially no clearance, respective axial through holes formed in bodies  8  and  9 . Alternatively, in a variation not shown, portion  19  engages the respective hole and is therefore connected integrally to body  9 , while portion  20  simply rests against a support carried by body  8 , so that pin  14  acts in the same way as an ordinary rod restrained at one end and resting against a support at the opposite end. 
     As shown in FIGS. 2 and 3, pin  14  also comprises two tubular cylindrical intermediate portions  21  and  22  extending from portions  19  and  20  respectively, and having respective outside diameters and different respective cross sections measured in respective planes parallel to plane P. More specifically, portion  21  has an outside diameter and a cross section greater than those of portion  22 , and a much greater flexural strength than portion  22 , or at least such that, when pin  14  is stressed in use, portion  22  is the only one to undergo substantial elastic deformation. 
     As shown in FIGS. 2 and 3, pin  14  also comprises a further tubular portion  24 , which is defined externally by surface  18 , projects from intermediate portion  21 , and surrounds intermediate portion  22 . Tubular portion  24  is defined internally by a conical surface  25 , which extends facing an outer lateral surface  26  of intermediate portion  22  and has an inside diameter tapering towards end portion  19 . Surface  25  is spaced apart from lateral surface  26 , and defines, together with surface  26 , a cavity  27  in which portion  22  flexes in use. 
     As shown in FIG. 2, pin  14  houses a known lubricating device  28 , not described in detail, for supplying lubricating fluid between pin  14  and bushing  16 . 
     Each pin  14  acts in the same way as an ordinary variable-section rod restrained at least one end, and the different intermediate resisting sections of pin  14  are so sized that, when the loads transmitted by planet wheels  5  to carrier  6  are such as to deform platelike bodies  8  and  9  and the tenons (not shown) of carrier  6 , portion  22  flexes as shown by the dash line in FIG. 3, while both portions  21  and  24  remain substantially undeformed. In fact, by virtue of the particular connection of end portions  19  and  20  to platelike bodies  8  and  9 , and of the deformation of platelike bodies  8  and  9  themselves, the deflection of portion  22  generates a reaction on body  9  in opposition to the forces acting on relative planet wheel  5 , to enable surface  18  of pin  14  to move while remaining parallel to itself and, hence, planet wheel  5  to mesh correctly at all times with both sun gear  2  and ring gear  4 . Maintaining a substantially unchanged mesh condition between the planet wheels and the sun and ring gears alongside variations in the deformation of carrier  6  prevents the generation of undesired, unpredictable forces between the meshing teeth and local deformation of bushings  16 , which would obviously result in steady, rapid impairment not only of the epicyclic gear train but also of the transmission as a whole. 
     As compared with known solutions, the particular geometry of pins  14  also provides for greatly reducing both the manufacturing and running cost of transmission  1 . That is, the geometry of pins  14 , and in particular the fact that each comprises only one reaction portion which is elastically deformable when stressed, enables only one of the two platelike bodies—in the example shown, body  8 —to be connected directly to the carrier  6  supporting body, with no need, as in known solutions, for complex, high-cost load balancing devices. 
     Clearly, changes may be made to pins it as described herein without, however, departing from the scope of the present invention. In particular, the various portions of pins  14  may be formed differently from those described by way of example, or may be replaced by respective portions performing equivalent functions.