SYNCHRONIZING MEANS

Abstract: The invention concerns a synchronizing means for gearboxes. Axially on one side of a gear wheel (2) disposed to be freely rotatable on a shaft (1) have been arranged, for engaging the gear step corres­ ponding to said gear wheel (2), first synchronizing elements (3), comprising a synchronizing means, known in itself in the art, operated by a gear shifter. Second synchronizing elements (4) have been disposed on the shaft (1) axially on the opposite side of the gear wheel (2), relative to the first synchronizing elements (3). The gear wheel (2) has been arranged to be movable axially between said first and second synchronizing elements (3,4) so that when the gear step consistent with said gear wheel (2) is being engaged, the gear wheel (2) is arranged to move under effect of the first syn­ chronizing elements (3) against the second synchronizing elements (4) in order to make them operate substantially simultaneously with the first synchronizing elements (3). After synchronizing has taken place the second synchronizing elements (4) have been arranged to disengage from operation.

Description: The present invention concerns a synchronizing means for gearboxes in which axially on one side of a gear wheel mounted freely rotat­ ably on a shaft of the gearbox for engaging the gear step corres­ ponding to said gear wheel have been disposed first synchronizing elements, these elements comprising a synchronizing means, known in itself in the art, operated by a gear shifter, and axially on the other side of the gear wheel with reference to the first syn­ chronizing elements, on the shaft, have been disposed second syn­ chronizing elements. It is nowadays a general trend to construct the gearboxes of vehi­ cles, working machines and equivalent to be small in size, with small distances between shafts and with relatively close axial spacing of the gear wheels on the shafts. For this reason large-­ diameter synchronizing rings cannot be used in such gearboxes. The efficiency of synchonizing, i.e., the coupling torque achievable with the synchronizing means and the time consumed in shifting gears, in their turn depend on the diameter of the synchronizing rings, on the coupling force that is employed and the taper of the synchronizing cones. The coupling force and the taper of the syn­ chronizing cones are not freely changeable because certain limits are imposed on them by the materials used in making the gearbox. The diameter of the synchronizing cone cannot be increased to be large because the size of the gearbox would then also increase. Thus, the problem is that it is not feasible to form in the syn­ chronizing means a large enough cone by the aid of which adequate accelerations and decelerations of the gear wheels could be pro­ duced. This problem is particularly salient in heavy equipment and in working machines. Attempts have been made to improve the efficiency of synchronizing, among other things, by inserting between the traditional pair of synchronizing cones, additional cones (for instance two of them) by the aid of which the efficiency of synchronizing could be greatly enhanced. This type of solution is however imperfect in the respect that the additional cones increase the diameter of the synchroniz­ ing means and its axial length. Moreover, the friction heat liber­ ated during synchronizing is concentrated in a small area, thus causing overheating problems. As a result the whole gearbox has to te built rather much larger. With the present invention an improvement is obtained in comparison with synchronizing means of prior art. The invention is mainly characterized in that the gear wheel has been arranged to be axial­ ly displaceable between said first and second synchronizing ele­ ments, and that between the gear wheel and the second synchronizing elements has been provided at least one axially acting spring, the gear wheel having been arranged, when the gear step corresponding to the wheel is being engaged, to move under effect of the first synchronizing elements against the second synchronizing elements in order to couple them to operate, substantially simultaneously with the first synchronizing elements, and that after synchronizing has taken place the second synchronizing elements are arranged to be pushed by said spring to disengage from operation. Among the advantages of the invention over the designs of prior art may be stated the following. In the design of the invention, a syn­ chronizing means of small diametral size can be used and this enables small shaft spacings to be employed, whereby the gearbox will be small in size. The friction heat liberated in the synchron­ izing process is divided between both ends of the gear wheel, whereby overheating is avoided. The synchronizing efficiency is considerdably better than in prior art designs and as a result the coupling forces can be held low, and the time consumed in engaging the gear steps is short. The sole drawback is that the axial length of the gearbox is slightly greater than that in the case of a con­ ventional synchronizing means being used. The invention is more closely described in the following, referring to the figures of the drawing.In the figures is presented a syn­ chronizing means according to the invention, in partly sectioned elevational view. In the figure are shown, on the shaft 1, a gear wheel 2 and a syn­ chronizing means, this synchronizing means comprising first syn­ chronizing elements 3 and second synchronizing elements 4. As shown in the figure, the first synchronizing elements 3 and the second synchronizing elements 4 are located axially on different sides of the gearwheel 2. The first synchronizing elements 3 consist of a conventional synchronizing means, comprising a shift ring 31 mov­ able in axial direction by means of a gear shifter. The shift ring 31 has in conventional manner been provided with inside coupling teeth 32. Between the shift ring 31 and the gear wheel 2 is provid­ ed an inhibitor ring 33, provided with teeth on the outer rim. The inhibitor ring 33 has an inner coupling cone 34, and on the gear wheel 2 has similarly been formed an outside coupling cone 35 mating with said inside coupling cone 34. The gear wheel 2 is more­ over provided with outside coupling teeth 36 engaging with the inside coupling teeth 32 of the shift ring 31. On the axially opposite side of the gear wheel 2, relative to the first synchronizing elements 3, have been provided second synchron­ izing elements 4, of which only one advantageous embodiment has been depicted in the figure. In the embodiment of the figure, the second synchronizing elements 4 comprise a body part 41 which is secured to be unrotatable with reference to the shaft 1 and its axial movement being prevented, at least in the direction away from the gear wheel 2. In order to prevent said axial movement, a stop ring 46 has been provided on the shaft 1. The body part 41 may naturally be fully rigidly mounted on the shaft 1 so that the body part 41 cannot move axially in either direction on the shaft 1. In the embodiment of the figure there has been formed, on the body part 41, a first friction surface 42 facing substantially towards the gear wheel 2, and on the gear wheel has, in conformity there­ with, been machined a second friction surface 43 mating with said first friction surface 42. In the embodiment of the figure, the friction surfaces 42 and 43 are conical in such manner that the first friction surface 42 is an inside cone and the second friction surface 43 is an outside cone. Naturally, the friction surfaces may equally be disposed so that the first friction surface 42 has been shaped as an outside cone and, correspondingly, the second friction surface 43 has been formed as an inside cone. It should be noted in this connection, however, that conical shape of the friction sur­ faces 42 and 43 is not indispensbale: said friction surfaces may equally be provided in another way, as will become apparent later on in this disclosure. Between the body part 41 and the gear wheel 2 has in the embodiment of the figure been disposed a spring 44, which tends to push the body part 41 and the gear wheel 2 axially away from each other so that the friction surfaces 42 and 43 are kept apart. In the embodi­ ment depicted, a cup spring is used for the spring 44, but another type of spring may equally be used to this purpose, for instance a helical spring. There may also be more than one spring, in which case the springs may for instance be arranged in a circle around the shaft 1. Since the body part 41 has been disposed to be unro­ tatable on the shaft 1, while the gear wheel 2 has been disposed to be freely rotatable on the shaft 1, an axial thrust bearing must be provided between said spring 44 and gear wheel 2 in order to elimi­ nate the friction between said spring 44 and gear wheel 2, this thrust bearing being indicated with reference numeral 45 in the figure. The mode of operation of the synchronizing means presented in the figure is as follows. When it is desired to engage in the gearbox the gear step corresponding to the gear wheel 2, the gear shifter (not depicted) is operated to move the shift ring 31 axially to­ wards the gear wheel 2, that is, to the right in the figure. The shift ring 31 then also moves, along with itself, the inhibitor ring 33 to the right, whereby the coupling cones 34 and 35 on the inhibitor ring 33 and on the gear wheel 2 come into contact. Fur­ thermore, the shift ring 31 also moves along with itself the gear wheel 2 to the right, against the compressive force of the spring 44. The spring 44 is compressed, and the first friction surface 42 on the body part 41 and the second friction surface 43 on the gear wheel 2 are brought into contact. When the friction surfaces 42 and 43 between the second synchronizing elements 4 and the gear wheel 2 meet, a friction torque arises between the gear wheel 2 and the shaft 1, this torque having the same direction as the friction torque produced by the first synchronizing elements 3. The friction torque caused by said second synchronizing elements 4 is directly proportional to the axial force acting on the first synchronizing elements 3. The friction torque thus achieved is considerably higher than the friction torque formed with the first synchronizing elements 3 alone, and therefore the accelerations and decelerations of the gear wheel 2 in relation to the shaft 1 can be made considerably higher than before, whereby the synchronizing will be more effi­ cient and the time required before the gear step comes on is short­ er. When the synchronizing has been completed, the shift ring 31 is enabled to move in over the coupling teeth 36 on the gear wheel 2, whereby the gear step consistent with the gear wheel 2 has become engaged. Immediately after the synchronizing process has been completed, the spring 44 pushes the first and second friction surfaces 42,43 apart and pushes the gear wheel 2 into its correct position relative to the gear wheel with which its is in mesh. If the friction surfaces 42,43 on the second synchronizing elements 4 are conical, the cones of said friction surfaces 42,43 should have sufficiently great inclinations so that on completed synchron­ izing the detachment of the friction surfaces 42,43 might take place at once. In the case that conical friction surfaces are used, it is always mandatory, in order to ensure the detachment of the friction surfaces 42,43, to use between the body part 41 and the gear wheel 2 a spring 44 by means of which said detachment is ensured. It was already observed in the foregoing description that the fric­ tion surfaces 42 and 43 are not necessarily conical. Said frition surfaces may also be planar, in a plane which is transversal to the central axis of the shaft 1. When such planar friction surfaces are employed, there is no absolute need to interpose a spring 44 be­ tween the body part 41 and the gear wheel 2 because planar friction surfaces come apart with considerably greater ease than conical friction surfaces. It is however advantageous also in the case of planar friction surfaces to use a spring 44 because detachment of the contact between the friction surfaces is important at the time when ultimate coupling of the coupling teeth takes place. Further­ more, the spring 44 is helpful in moving the gear wheel 2 after completed coupling axially into its proper position, especially when gear wheels with straight teeth are used, in which case no axial force components acting on the gear wheels are derived from the tooth forces. When planar friction surfaces are employed, it is possible to use in the capacity of second synchronizing elements 4, moreover, for instance a conventional multi-disk clutch by means of which good adhesion is obtained between the friction surfaces and, on the other hand, easy detachment. It is advantageous in con­ nection with a multi-disk clutch as well, to use for ensuring detachment, a spring 44 interposed between the body part 41 and the gear wheel 2. The invention has been presented by way of example in the fore­ going, referring to the figure of the drawing. There is however no intention to confine the invention merely to the embodiments presented in the figure and in the disclosure; instead, numerous modifications are feasible within the scope of the inventive idea defined by the claims following below.

Claims: 1. A synchronizing means for gearboxes in which axially on one side of a gear wheel (2) disposed to be freely rotatable on a shaft (1) have been arranged, for engaging the gear step corresponding to said gear wheel (2), first synchronizing elements (3), comprising a synchronizing means, known in itself in the art, operated by a gear shifter, second synchronizing elements (4) having been disposed on the shaft (1) axially on the opposite side of the gear wheel (2), relative to the first synchronizing elements (3), characterized in that the gear wheel (2) has been arrnged to be movable axially between said first and second synchronizing elements (3,4) and that between the gear wheel (2) and the second synchronizing elements (4) has been disposed at least one axially acting spring (44), said gear wheel (2) having been arranged, when the gear step consistent with said gear wheel (2) is being engaged, to move under effect of the first synchronizing elements (3) against the second synchroniz­ ing elements (4) in order to make them operate substantially simul­ taneously with the first synchronizing elements (3), and that after synchronizing has taken place the second synchronizing elements (4) have been arranged to disengage from operation, pushed by said spring (44). 2. Synchronizing means according to claim 1, characterized in that said second synchronizing elements (4) comprise a body part (41) disposed unrotatably with reference to the shaft (1) and on which has been formed a first friction surface (42), and that on the gear wheel (2) has been formed a second friction surface (43), mating with the first friction surface (42). 3. Synchronizing means according to claim 2, characterized in that said friction surfaces (42,43) are conical. 4. Synchronizing means according to claim 3, characterized in that the first friction surface (42) comprises an inside conical surface and the second friction surface (43) comprises an outside conical surface. 5. Synchronizing means according to claim 3, characterized in that the first friction surface (42) comprises an outside conical sur­ face and the second friction surface (43) comprises an inside coni­ cal surface. 6. Synchronizing means according to claim 2, characterized in that said friction surfaces are planar, with their plane perpendicular against the central axis of the shaft (1). 7. Synchronizing means according to claim 1, characterized in that the second synchronizing elements (4) comprise a multiple disk clutch, consisting of a body part (41) and of friction disks pro­ vided between the body part (41) and the gear wheel (2). 8. Synchronizing means according to any one of the preceding claims, characterized in that said, at least one, spring (44) is held at one end by the body part (41) and at its other end by a thrust bearing (45) disposed between the gear wheel (2) and the spring (44).

Inventors: KANANEN, TEPPO
Applicants: VALMET OY
Application year: 1986
Main classification: F16D23
IPC codes: F16D23, F16H63