Roller synchro mechanism

Abstract: A retainer (13a) retaining a plurality of rollers (12a) therein for slight movement in a radial direction is disposed between cam grooves (10a₁) in the outer periphery of an inner cam (10a) secured to a rotary shaft (1) and a roller abutment surface (3a₂) around an inner periphery of a gear (3a) relatively rotatably carried on the rotary shaft (1). A dowel-admission groove (13a₂) is defined in a side of the retainer (13a), so that a dowel (8a) of a sleeve (8) can enter the dowel-admission groove (13a₂). The dowel admission groove (13a₂) is defined between the adjacent rollers (12a) retained in the retainer (13a), or at least portions of the inner cam (10a), the rollers (12a) and the retainer (12a) are disposed in a recess made in the gear, thereby permitting a reduction in axial dimension of a roller synchro mechanism.

Description: The field of the present invention is synchro mechanisms for use in a multi-stage type transmission, and more particularly, synchro mechanisms designed to permit an outer member such as a gear relatively rotatably carried on an input or output shaft to be brought into engagement with an inner member which rotates in unison with the shaft. There is a conventionally known roller synchro mechanism described in U.S. Patent No.4,817,451. This roller synchro mechanism has a structure in which a plurality of rollers are disposed between a roller abutment surface formed at the inner periphery of a gear relatively rotatably carried on a rotary shaft and cam grooves provided on the outer periphery of an inner cam secured to the rotary shaft, and a dowel formed on a sleeve is adapted to be engaged into and disengaged from a dowel-admission groove made in a side of a retainer which retains the rollers while permitting their slight movement in a radial direction. In a state of the dowel of the sleeve being in engagement in the dowel-admission groove in the retainer, the rollers are fitted into the cam grooves and moved radially inwardly away from the roller abutment surface formed on the gear, thereby releasing engagement between the rotary shaft and the gear. On the other hand, in a state of the dowel of the sleeve being removed from the dowel-admission groove in the retainer, the rollers are urged radially outwardly by the cam grooves to bear against the roller abutment surface, thereby causing the rotary shaft and the gear to be brought into integral engagement with each other. However, the above prior art roller synchro mechanism has a disadvantage of an increased thickness of the retainer, resulting in an increased axial dimension of the entire roller synchro mechanism, because the dowel-admission grooves in the retainer and the roller-retaining holes are juxtaposed axially. In addition, the inner cam, the rollers and the retainer are contained in a projection formed on a side of the gear, resulting in an increased thickness of the gear. This also causes an increase in axial dimension of the entire roller synchro mechanism. The retainer used in the above prior art roller synchro mechanism is held merely in a loosely fitted manner on the roller abutment surface of the gear and for this reason, there is a possibility that when the dowel of the sleeve is removed from the dowel-admission groove in the retainer to effect the engagement between the gear and the rotary shaft, the gear and the retainer may be slipped to cause a time lag until the engagement is achieved. Further, roller-retaining grooves in a retainer require an extremely high accuracy in machining, but the retainer in the above prior art roller synchro mechanism is comprised of a single component and hence, has a disadvantage that machining of the roller-retaining grooves having a non-circular section is difficult and requires a high cost DE-A-1946140, DE-C-576907, US-A-3426874 and GB-923987 all disclose examples of differential drive mechanisms which have inner and outer members which can be selectively driven in synchronisation. Rollers are provided between the inner and outer members which, depending on the relative positions of these members, allow the synchronised rotation to be achieved. According to the present invention, there is provided a roller synchro mechanism comprising: an outer member relatively rotatably carried on a rotary shaft; an inner member which rotates in unison with the rotary shaft; a plurality of cam grooves formed on one of an inner peripheral surface of the outer member and an outer peripheral surface of the inner member; a roller abutment surface formed around the other of the inner peripheral surface of the outer member and the outer peripheral surface of the inner member; a plurality of rollers disposed between the cam grooves and the roller abutment surface; a retainer for retaining the rollers so as to permit a slight movement thereof in a radial direction and having a dowel-admission groove provided in a side surface of the retainer; and a sleeve relatively unrotably and axially movably carried on said rotary shaft and having a dowel engageable into and disengageable from said dowel-admission groove, wherein by removing the dowel of the sleeve from the dowel-admission groove, the rollers are radially urged by the cam grooves and press-contacted with the roller abutment surface to integrally engage the inner and outer members with each other, characterised in that said retainer comprises a body portion and a separate cover plate attached to said body portion, said body portion being provided with roller-retaining grooves each for retaining one of the end faces and opposite sides of a peripheral surface of each of said rollers, the other end face of each roller being retained by said separate cover plate, in that said body portion is also provided with a slide contact portion which is tightly fitted to the roller abutment surface of said other member, and in that the roller-retaining grooves each have an arcuate surface, each roller has a cylindrical shape and the arcuate surface of the roller-retaining grooves has a radius of curvature larger than a radius of the peripheral surface of each roller, such that the rollers are prevented from falling therefrom during assembly of said mechanism. The slide contact portion may be formed at the outer periphery of the retainer and tightly fitted to the roller abutment surface of the outer member and therefore, when the dowel of the sleeve is removed from the dowel-admission groove in the retainer for providing engagement between the rotary shaft and the outer member, the retainer can be dragged by the outer member under a frictional force acting between the roller abutment surface and the slide contact portion. This ensures that the retainer dragged by the outer member and the inner member provided on the rotary shaft can be rotated relative to each other without any time lag, and the rollers can be urged radially outwardly by the inner member, thereby bringing the rotary shaft and the outer member promptly to engagement with each other. In addition, since the retainer comprises two components: the body portion having the roller-retaining grooves; and the cover plate coupled to the body portion to cover the openings on one side of each of the roller-retaining grooves, machining of the grooves is facilitated, which enables an improvement in machining accuracy and a reduction in manufacturing cost. Preferably the dowel-admission groove is defined between the adjacent rollers retained in the retainer. With the above construction, the dowel-admission groove in the retainer is provided between the adjacent rollers retained in the retainer and therefore, even the retainer is formed to have a minimum thickness required only to retain the rollers, the dowel-admission groove can still be formed within a range of the thickness. This ensures that the thickness of the retainer can be smaller than that in the prior art, leading to a reduction in axial dimension of the roller synchro mechanism. In a preferred embodiment at least part of the inner member, the rollers and the retainer are disposed in a recess made in the outer member. With the above construction, at least part of the inner member, the rollers and the retainer are disposed in the recess made in the outer member and therefore, it is not necessary to form a projection on a side of the gear for containing the inner member, the rollers and the retainer. Consequently, it is possible to make the thickness of the outer member smaller than that in the prior art, leading to a reduction in axial dimension of the roller synchro mechanism. Accordingly, embodiments of the present invention may provide a roller synchro mechanism which is compact in axial dimension and shows a higher responsiveness when the outer member such as a gear relatively rotatably carried on the rotary shaft and the inner member which rotates in unison with the rotary shaft are brought into engagement with each other, and which enables use of a retainer which is easily fabricated with accuracy. The above and other objects, features and advantages of the invention will become apparent from reading of the following description of a preferred embodiment, taken in conjunction with the accompanying drawings. Figures 1 to 4 illustrate a first roller synchro mechanism which is not an embodiment of the invention, but is included by way of background, wherein Figure 1 is a sectional view of the roller synchro mechanism, taken along a line I-I in Figure 2; Figure 2 is a sectional view taken along a line II-II in Figure 1; Figure 3 is a sectional view taken along a line III-III in Figure 1; and Figure 4 is a perspective view of a retainer; Figure 5 is a sectional view similar to Figure 1, but illustrating a further roller synchro mechanism which is also included by way of background; Figures 6 to 8 illustrate an embodiment of the present invention, wherein Figure 6 is a sectional view similar to Figure 1; Figure 7 is a sectional view taken along a line VII-VII in Figure 6; and Fig.8 is an exploded perspective view of a retainer; and Fig.9 is a sectional view similar to Fig.3, but illustrating prior art. The background to the present invention will now be described with reference to Figures 1 to 4. Referring to Fig.1, a first shift-stage gear 3a as an outer member is relatively rotatably carried through a needle bearing 2a on a rotary shaft 1 constituting an input shaft of a mutli-stage type transmission, and a second shift-stage gear 3b as another outer member is also relatively rotatably carried likewise through a needle bearing 2b on a collar 4 fitted over the rotary shaft 1 at a location axially spaced from the gear 3a by a predetermined distance. Between the gears 3a and 3b, a sleeve 8 is axially slidably carried through a spline 7 around an outer periphery of a boss 6 which is connected to the rotary shaft 1 through spline 5, so that the axial movement of the sleeve 8 by a shift fork 9 causes the first shift-stage gear 3a or the second shift-stage gear 3b to be brought into integral engagement with the rotary shaft 1, thereby establishing a first or second shift stage. As can be seen from Figs.1 and 2, a ring-shaped inner cam 10a is secured to the rotary shaft 1 through a spline 11a between the first shift-stage gear 3a and the boss 6, and a large number of angle cam grooves 10a 1 are provided on the outer periphery of the inner cam 10a as an inner member. A plurality of rollers 12a are disposed between the cam grooves 10a 1 of the inner cam 10a and a roller-abutment surface 3a 2 formed on the inner periphery of a projection 3a 1 provided on one side surface of the gear 3a, respectively. It can be seen from reference to Figs.3 and 4 together with Figs.1 and 2 that a ring-shaped retainer 13a is fitted between the inner cam 10a and the projection 3a 1 of the gear 3a, with an outer periphery of the retainer 13a placed into slide contact with the roller-abutment surface 3a 2 of the gear 3a for permitting relatively rotating movement therebetween, and is prevented by a clip 15a through a control ring 14a from being slipped out. The retainer 13a is provided with a plurality of roller-supporting holes 13a 1 extending radially therethrough in correspondence with positions of the cam grooves 10a 1 , and the rollers 12a are retained within the roller-supporting holes 13a 1 so as to be permitted a slight movement in a radial direction. Three dowel-admission grooves 13a 2 are provided at the inner periphery of the retainer 13a at equal angles of 120° and opened to one side surface of the retainer 13a to extend axially. As best shown in Fig. 3, the dowel-admission grooves 13a 2 are made to lie centrally between adjacent roller-supporting holes 13a 1 , thereby ensuring that the axial thickness of the retainer 13a is of a minimum level required for retaining the rollers 12a. A dowel 8a is projectingly provided on one side of the sleeve 8, so that it is removed from the dowel-admission groove 13a 2 by the axial movement of the sleeve 8 through the spline 7. When the dowel 8a is in engagement with the dowel-admission groove 13a 2 , the inner cam 10a and the retainer 13a are positioned in the state shown in Fig.2, and each of the rollers 12a is fitted in the middle of the cam groove 10a 1 . A roller synchro mechanism for the second shift stage has a structure substantially symmetrical with and identical to a roller synchro mechanism for the first shift stage and hence, duplicated description thereof will be omitted by using reference numerals and characters with a suffix b attached thereto. Description will now be made of the operation of the first mechanism having the above-described construction. In a condition in which the sleeve 8 is in a neutral position shown in Fig.1 with the dowel 8a thereof fitted in the dowel-admission groove 13a 2 of the retainer 13a on the side of the gear 3a, the inner cam 10a and the retainer 13a are positioned in the state shown in Fig.2 through the spline 11a, the rotary shaft 1, the spline 5, the boss 6, the spline 7, the dowel 8a of the sleeve 8, and the dowel-admission groove 13a 2 . In this condition, the roller 12a retained in the retainer 13a at a position slightly moved radially inwardly within the roller-supporting hole 13a 1 away from the roller abutment surface 3a 2 of the gear 3a. In this state, the outer peripheral surface of the retainer 13a and the roller abutment surface 3a 2 slip relative to each other, so that the transmission of torque between the rotary shaft 1 and the gear 3a is cut off. At this time, the dowel 8a of the sleeve 8 is also fitted in the dowel-admission groove 13b 2 of the retainer 13b on the side of the gear 3b, so that the transmission of torque between the rotary shaft 1 and the gear 3b is also cut off. If the sleeve 8 is moved from this state in the direction of an arrow A, thereby removing the dowel 8a from the dowel-admission groove 13a 2 , the retainer 13a and the inner cam 10a can then be relatively rotated slightly by a torque applied from the rotary shaft 1 or the gear 3a. The rollers 12a are strongly urged radially outwardly within the roller-supporting holes 13a 1 by the cam grooves 10a 1 of the inner cam 10a to come into abutment against the roller abutment surface 3a 2 of the gear 3a. This causes the inner cam 10a and the gear 3a, and thus the rotary shaft 1 and the gear 3a to be brought into integral engagement with each other, thereby establishing the first shift stage. Conversely, if the sleeve 8 is moved in the direction of an arrow B, the rotary shaft 1 and the gear 3b are brought into integral engagement with each other by an action similar to that described above, thereby establishing the second shift stage. As apparent from comparison of Fig.3 with Fig.9 (prior art), dowel-admission grooves 13a 2 ' and 13b 2 ' of retainers 13a' and 13b' in the prior art are provided on axes of rollers 12a' and 12b', respectively, at axial spacings therebetween whereas the dowel-admission grooves 13a 2 and 13b 2 in the first mechanism are provided between the circumferentially adjacent roller-supporting holes 13a 1 and 13b 1 , respectively. Therefore, it is possible to make the axial thickness of the retainers 13a and 13b minimum, resulting in a reduction in size of the roller synchro mechanism. In the above described mechanism, the roller abutment surfaces 3a 2 and 3b 2 are formed on the side of the gears 3a and 3b, whereas the cam grooves 10a 1 and 10b 1 are formed on the side of the inner cams 10a and 10b. However, it is possible to reverse this positional relationship. A second mechanism will now be described in connection with Fig.5. Gears 3a and 3b in this embodiment have annular recesses 3a 3 and 3b 3 made in opposed side surfaces thereof, respectively, and inner cams 10a and 10b and retainers 13a and 13b retaining rollers 12a and 12b are contained within the recesses 3a 3 and 3b 3 made in the gears 3a and 3b, respectively. In this case, the inner cams 10a and 10b are formed integrally with the boss 6, because they cannot be spline-connected directly to the rotary shaft 1. In this mechanism, the gear 3a or 3b of a first or second shift stage can be selectively brought into engagement with the rotary shaft 1 by moving the sleeve 8 axially to remove dowels 8a or 8b from dowel-admission grooves 13a 2 or 13b 2 of the retainers 13a and 13b, respectively. As apparent from comparison of Fig.1 with Fig.5, in this second mechanism, the inner cams 10a and 10b and the retainers 13a and 13b retaining the rollers 12a and 12b are contained in the recesses 3a 3 and 3b 3 made in the gears 3a and 3b, respectively and therefore, it is possible to substantially reduce the axial thickness of the gears 3a and 3b to further reduce the axial dimension of the roller synchro mechanism in cooperation with the disposition of the dowel-admission grooves 13a 2 , 13b 2 between the adjacent rollers 12a, 12b. An embodiment of the present invention will now be described in connection with Figs.6 to 8. Fig.6 is a sectional view similar to Fig.1; Fig.7 is a sectional view taken along a line VII-VII in Fig.6; and Fig.8 is an enlarged exploded view of a retainer. Referring to Fig.6, a first shift-stage gear 52 1 is relatively rotatably carried through a needle bearing 51 on a rotary shaft 70 which constitutes an output shaft of a continuously variable transmission, and a second shift-stage gear 52 2 is also relatively rotatably carried likewise through the needle bearing 51 on the rotary shaft 70 at a location axially spaced from the gear 52 1 by a predetermined distance. Between the two gears 52 1 and 52 2 , a sleeve 56 is axially slidably carried through a spline 55 around an outer periphery of a boss 54 which is connected to the rotary shaft 70 through spline 53, so that the axial movement of the sleeve 56 by a shift fork 57 causes the first shift-stage gear 52 1 or the second shift-stage gear 52 2 to be brought into integral engagement with the rotary shaft 70, thereby selectively establishing a first or second shift stage. It should be noted that the spline 55 and the sleeve 56 are engaged in a concave/convex fashion with each other, but this concave/convex engagement can be reversed. It can be seen from to Fig.7 together with Fig.6 that a recess is made in a side surface of the first shift-stage gear 52 1 , and a ring-shaped inner cam 58 is integrally formed on a side of the boss 54 to lie within the recess. A large number of triangular cam grooves 58a are provided on an outer periphery of the inner cam 58, and a large number of rollers 60 retained in a retainer 59 are disposed between the cam grooves 58a and a roller abutment surface 52a formed on the outer radially inwardly directed surface of the recess in the gear 52 1 , respectively. As can be seen from Fig.8 as well as from Figs.6 and 7, the retainer 59 is a ring-shaped member relatively rotatably fitted in the recess in the gear 52 1 and comprised of two components: a body portion 61 and a cover plate 62. The body portion 61 is provided with roller-retaining grooves 61b defined between a large number of connections 61a to retain the rollers 60 such that the rollers 60 are permitted slight movement in a radial direction. An inner surface of each of the roller-retaining grooves 61b, i.e., a surface opposed to the outer periphery of the roller 60 is formed into an arcuate surface having a radius of curvature larger than the radius of the roller 60, thereby making the angle of a corner defined between the roller abutment surface 52a and the roller-retaining groove 61b obtuse. A projection 61c is formed on a side of the connection 61a, and the body portion 61 and the cover plate 62 are integrally coupled to each other by fitting each of the projections 61c in a caulking manner into corresponding one of holes 62a provided in the cover plate 62. Four dowel-admission grooves 59a are provided on the inner periphery of the retainer 59 at equal angles of 90 ° and opened to a side thereof closer to the cover plate 62 to extend axially. By forming the roller-retaining groove 61b to have an arcuate surface as described above, there is no possibility that rollers fitted in the roller-retaining grooves 61b may be fallen to the outside during assembly, and therefore, the assembling efficiency of the retainer 59 can be substantially improved. Moreover, because the roller-retaintng grooves 61b of the body portion 61 which require working accuracy most are opened to the surface joined to the cover plate 62, machining of the roller-retaining grooves 61b can be easily carried out with a higher accuracy. The retainer 59 is mounted between the roller abutment surface 52a of the recess in the gear 52 1 and the cam grooves 58a of the inner cam 58 and in this case, slide contact portions 61d are formed around the outer periphery of the body portion 61 of the retainer 59 and tightly fitted into the recess in the gear 52 1 in order to ensure that a proper frictional force is provided between the slide contact portions 61d and the recess in the gear 52 1 to cause the retainer 59a to be dragged by the gear 52 1 for integral rotation. In addition, lubricating grooves 61e are provided on the outer periphery of the body portion 61 of the retainer 59, and a locking portion 61f (See Fig 6) is formed on the body portion 61 to abut against the side surface of the inner cam 58 in order to restrain axial movement of the body portion 61. On the other hand, four dowe is 56a are projectingly provided on a side surface of the sleeve 56 at equal angles of 90° , so that an axial movement of the sleeve 56 through the spline 55 causes the dowel 56a to be brought into and out of engagement with the dowel-admission groove 59a. Thus, when the dowel 56a is in engagement with the dowel-admission groove 59a, the inner cam 58 and the retainer 59 are positioned in the state shown in Fig.7, with each roller 60 being centrally fitted in the cam groove 58a. According to the roller synchro mechanism of this embodiment, in a condition in which the sleeve 56 is in a neutral position shown in Fig.6 with the right dowel 56a thereof fitted in the dowel-admission groove 59a of the retainer 59 on the side of the gear 52 1 , the inner cam 58 and the retainer 59 are positioned in the states shown in Fig.7. Consequently, the rollers 60 retained in the retainer 59 assume the state capable of moving in the radial direction within the roller-retaining grooves 61b. In such condition, the outer peripheral surface of the retainer 59 and the roller abutment surface 52a of the gear 52 1 are slipped relative to each other, so that the transmission of a torque between the rotary shaft 1 and the gear 52 1 is cut off. In this state, the left dowel 56a of the sleeve 56 is also fitted in the dowel-admission groove 59a in the retainer 59 for the second shift-stage gear 52 2 , so that the transmission of torque between the rotary shaft 70 and the gear 52 2 is also cut off. If the sleeve 56 is moved from this condition in the direction of an arrow A by a shift fork 57 to remove the dowel 56a from the dowel-admission groove 59a of the gear 52 1 , the retainer 59 and the inner cam 58 for the gear 52 1 are relatively rotated slightly by torque applied from the rotary shaft 70 or the gear 52 1 , causing the rollers 60 to be strongly urged radially outwardly within the roller-retaining grooves 61b by the cam grooves 58a of the inner cam 58 to bear against the roller abutment surface 52a of the gear 52 1 . This causes an integral engagement between the inner cam 58 and the gear 52 1 and thus between the rotary shaft 70 and the gear 52 1 to establish a first shift stage. Conversely, if the sleeve 56 is moved in the direction of an arrow B, the rotary shaft 70 and the gear 52 2 are brought into integral engagement with each other by an action similar to that described above to establish a second shift stage. In order to provide an enhanced responsiveness in the operation of removing the dowel 56a of the sleeve 56 from the dowel-admission groove 59a of the retainer 59 to bring the gear 52 1 into engagement with the rotary shaft 70, it is necessary to rotate the retainer 59 relative to the inner cam 58 to promptly urge the rollers 60 radially outwardly by the cam grooves 58a of the inner cam 58. To this end, the slide contact portions 61d are provided in the body portion 61 of the retainer 59 to come into close contact with the recess in the gear 52 1 in order to allow for the dragging of the retainer 59 by the gear 52 1 due to frictional force acting on the portions 61d to provide a prompt engagement of the gear 52 1 with the rotary shaft 70. When inserting the dowel 56a of the sleeve 56 into the dowel-admission groove 59a of the retainer 59 to release the engagement of the gear 52 1 with the rotary shaft 70, it is not feared that the roller 60 may cut into a wedge-shaped corner formed by the roller-retaining groove 61b in the retainer 59 and the roller abutment surface 52a, because the roller-retaining groove 61b in the body portion 61 of the retainer 59 is formed to have an arcuate surface of a radius of curvature larger than the radius of the roller 60. Therefore, as soon as the dowel 56a is inserted, the rollers 60 become freely movable within the roller-retaining grooves 61b, so that the disengagement of the gear 52 1 from the rotary shaft 70 can be quickly conducted without any time lag. Modifications to the above described arrangements are possible. For example, although the roller synchro mechanism has been provided between the first and second shift stages in the embodiments, it can be, of course, provided for other shift stages. In addition, although the dowel-admission groove 13a 2 , 13b 2 , in the second arrangement, has been made between the rollers 12a, 12b of the retainer 13a, 13b as in the first arrangement, such dowel-admission groove 13a 2 , 13b 2 may be made on an axis of the roller 12a, 12b as in the prior art, and the inner cam 10a, 10b, the rollers 12a, 12b and the retainer 13a, 13b may be disposed in the recess 3a 3 , 3b 3 made in the gear 3a, 3b. Such a measure also makes it possible to provide a reduction in axial dimension of the roller synchro mechanism.

Claims: A roller synchro mechanism comprising: an outer member (52 1 , 52 2 ) relatively rotatably carried on a rotary shaft (70); an inner member (58) which rotates in unison with the rotary shaft; a plurality of cam grooves (58a) formed on one of an inner peripheral surface of the outer member and an outer peripheral surface of the inner member; a roller abutment surface (52a) formed around the other of the inner peripheral surface of the outer member and the outer peripheral surface of the inner member; a plurality of rollers (60) disposed between the cam grooves and the roller abutment surface; a retainer (59) for retaining the rollers so as to permit a slight movement thereof in a radial direction and having a dowel-admission groove (59a) provided in a side surface of the retainer; and a sleeve (56) relatively unrotatably and axially movably carried on said rotary shaft and having a dowel (56a) engageable into and disengageable from said dowel-admission groove, wherein by removing the dowel of the sleeve from the dowel-admission groove, the rollers are radially urged by the cam grooves and press-contacted with the roller abutment surface to integrally engage the inner and outer members with each other, characterised in that said retainer (59) comprises a body portion (61) and a separate cover plate (62) attached to said body portion, said body portion (61) being provided with roller-retaining grooves (61b) each for retaining one of the end faces and opposite sides of a peripheral surface of each of said rollers (60), the other end face of each roller being retained by said separate cover plate, in that said body portion is also provided with a slide contact portion which is tightly fitted to the roller abutment surface (52a) of said other member, and in that the roller-retaining grooves each have an arcuate surface, each roller has a cylindrical shape and the arcuate surface of the roller-retaining grooves having a radius of curvature larger than a radius of the peripheral surface of each roller, such that the rollers are prevented from falling therefrom during assembly of said mechanism. A roller synchro mechanism as claimed in claim 1, wherein a corner defined between the roller abutment surface and the peripheral surface of the roller-retaining groove has an obtuse angle. A roller synchro mechanism as claimed in claim 1 or 2, wherein the dowel-admission groove is defined between the adjacent rollers retained in the retainer. A roller synchro mechanism as claimed in any one of claims 1 to 3, wherein at least part of said inner member, said rollers and said retainer are disposed in a recess (3a 3 ) made in said outer member. A roller synchro mechanism as claimed in any one of claims 1 to 4, wherein slide contact portions (61d) are formed around a peripheral surface of said body portion (61) for sliding contact with said roller abutment surface (52a). A roller synchro mechanism as claimed in any one of claims 1 to 4, wherein lubricating grooves (61e) are formed around a peripheral surface of said body portion (61). A roller synchro mechanism as claimed in claim 5, wherein lubricating grooves (61e) are formed around the peripheral surface of said body portion (61) adjacent said slide contact portions (61d). A roller synchro mechanism as claimed in any one of claims 1 to 7, wherein a plurality of projections (61c) are provided at one side of said body portion (61) and a plurality of holes (62a) are provided on said cover plate (62), said holes (62a) receiving said projections (61c), respectively, at the time of assembly between said body portion (61) and said cover plate (62).

Inventors: ASHIKAWA NOBORU, KOMORI TETUYA, MIZOKAWA KEN, OHHASHI AKIHITO, SHIBATA NAOHISA, TAKANO MASAMI, ASHIKAWA, NOBORU, KOMORI, TETUYA, MIZOKAWA, KEN, OHHASHI, AKIHITO, SHIBATA, NAOHISA, TAKANO, MASAMI, ASHIKAWA, NOBORU, K.K. HONDA GIJUTSU KENKYUSHO, KOMORI, TETUYA, K.K. HONDA GIJUTSU KENKYUSHO, MIZOKAWA, KEN, K.K. HONDA GIJUTSU KENKYUSHO, OHHASHI, AKIHITO, K.K. HONDA GIJUTSU KENKYUSHO, SHIBATA, NAOHISA, K.K. HONDA GIJUTSU KENKYUSHO, TAKANO, MASAMI, K.K. HONDA GIJUTSU KENKYUSHO
Applicants: HONDA MOTOR CO LTD, HONDA GIKEN KOGYO KABUSHIKI KAISHA
Application year: 1991
Main classification: F16D41
IPC codes: F16D41