JP2007139166A - Synchronizer for transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To prevent energy loss caused by abrasion or friction by abutting of a conical hole of a synchronizer with a conical surface in a state wherein a transmission gear and a clutch hub are not connected. <P>SOLUTION: A sleeve 30 is engaged to the clutch hub 16 integrally provided on a rotating shaft 10 through a spline so as to be capable of reciprocating, transmission gears 20 and 25 wherein conical surfaces 21b and 26b and external gear splines 21a and 26a are coaxially formed are rotatably arranged on one side of the clutch hub on the rotating shaft, and synchronizer rings 22 and 27 having conical holes 22c and 27c capable of being fitted to the conical surfaces and external gear splines 22d and 27d are arranged between the transmission gear and the clutch hub movably along the axial direction and turnably. On the clutch hub and the synchronizer ring, first and second fitting parts 16d, 16e, 22b and 27b are formed which are abutted with each another by relative turning of them so as to return the synchronizer ring to the clutch hub side. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a transmission synchronization device in which a transmission gear is switched by a sleeve that is spline-engaged and reciprocally shifted to a clutch hub provided integrally with a rotating shaft.

As a transmission device of this type, there is a technique disclosed in Patent Document 1. In this technology, a sleeve is spline-engaged with a clutch hub provided integrally with a rotating shaft so that the sleeve can reciprocate, and a transmission gear having a conical surface and an external spline coaxially formed on the rotating shaft. A synchronizer ring with a conical hole and an external spline that can be engaged with the conical surface between the transmission gear and the clutch hub are provided so as to be axially movable and rotatable. It is. In this technique, by shifting the sleeve in the axial direction, the conical hole of the synchronizer ring is frictionally engaged with the conical surface of the transmission gear and the external spline is engaged with the internal spline of the sleeve to rotate the transmission gear. Is synchronized with the rotation of the clutch hub, and then the clutch hub and the transmission gear are connected by engaging the internal spline of the sleeve and the external spline of the transmission gear.
Japanese Patent Laid-Open No. 10-47376 (paragraphs [0010] to [0014], FIG. 1).

  In the technique of Patent Document 1 described above, the synchronizer ring is supported by the inner surface of the outer peripheral portion of the clutch hub so as to be able to move and rotate in the axial direction with a slight gap. In a state where the synchronizer ring is not connected to the shaft, the synchronizer ring may be lowered or inclined due to its own weight, etc., and the conical hole and the conical surface may come into contact with each other linearly or in a point shape. This occurs when the gap between the conical hole and the conical surface is reduced. In this state where the transmission gear and the clutch hub are not connected, the transmission gear rotates relative to the clutch hub and the synchronizer ring. Therefore, if the conical hole and the conical surface are in contact as described above, the conical hole and the conical hole are in contact with each other. There is a problem that energy loss occurs due to surface wear and friction, or local uneven wear occurs. The object of the present invention is to solve each of these problems.

To this end, a transmission synchronization device according to the present invention includes a clutch hub that is rotated integrally with a rotary shaft, and an internal spline that is engaged with an external spline formed on the outer periphery of the clutch hub. And a sleeve that is reciprocally shifted in the axial direction, and an external spline and a conical surface that are rotatably supported on a rotating shaft on one side of the clutch hub and engaged with an internal spline on a boss portion on the clutch hub side. Is integrally formed between the transmission gear and the clutch hub, and the clutch hub is axially movable and rotatable with respect to the clutch hub and is pressed toward the transmission gear by the axial shift of the sleeve. A conical hole formed coaxially on the periphery is frictionally engaged with the conical surface, and an external spline formed on the outer periphery engages with the internal spline, thereby rotating the transmission gear wheel. In a transmission synchronizer provided with a synchronizer ring that synchronizes with a rotation, the clutch hub and the synchronizer ring are in contact with each other in the circumferential direction by relative rotation of both of them, and the synchronizer ring is pulled back to the clutch hub side. The engaging portion and the second engaging portion are formed.

  In the transmission synchronization device described in the preceding paragraph, one of the first engagement portion and the second engagement portion has an inclined surface that is inclined with respect to the central axis of the rotation shaft when viewed from the outside in the radial direction. It is preferable that the inclined surface is in contact with a part of the other so that the synchronizer ring is pulled back to the clutch hub side.

  According to the first aspect of the present invention, if the rotating shaft is rotated in a state where the transmission gear is not connected to the clutch hub and the synchronizer ring is not connected to the clutch hub, the clutch hub and the synchronizer ring are connected. The formed first engaging portion and second engaging portion come into contact with each other, and the synchronizer ring is pulled back to the clutch hub side. As a result, the gap between the conical hole and the conical surface increases, so that even if the synchronizer ring is lowered or inclined due to its own weight, the conical hole and the conical surface do not come into contact with each other in a linear or dotted manner. There will be no energy loss due to wear or friction on the conical surface, or local uneven wear.

  Further, according to the invention of claim 2 described above, it has an inclined surface that is inclined with respect to the central axis of the rotating shaft when one of the first engaging portion and the second engaging portion is viewed from the outside in the radial direction, Since the other part is brought into contact with the inclined surface, and the structure for pulling the synchronizer ring back to the clutch hub side becomes very simple, the cost required for implementation can be reduced.

  The best mode for carrying out the transmission synchronization apparatus according to the present invention will be described below with reference to FIGS. The transmission includes a rotating shaft 10, a clutch hub 16, first and second transmission gears 20 and 25, first and second synchronizer rings 22 and 27, and a sleeve 30.

  As shown mainly in FIG. 1, the rotating shaft 10 is formed by integrally forming the first to fourth shaft portions 11, 12, 13, and 14 that gradually become smaller in diameter following the integrally formed flange portion 10a. It is. The clutch hub 16 has an outer peripheral portion 16b in which an external spline 16a is formed and a boss portion narrower than the outer peripheral portion 16b. The boss portion is coaxially fixed to the second shaft portion 12 of the rotary shaft 10 via the spline. Thus, the retainer ring 17 prevents the retainer ring 17 from coming off. Both sides of the clutch hub 16 between the outer peripheral part 16b and the boss part are formed in an annular shape, and both side parts of the outer peripheral part 16b are cylindrical and project from the clutch hub 16.

  The first transmission gear 20 is rotatably supported by the first shaft portion 11 between the flange portion 10a and the clutch hub 16 via a needle bearing 23, and the boss portion on the clutch hub 16 side is substantially A first gear piece 21 that is a part of one transmission gear 20 is integrally press-fitted and fixed. A conical surface 21b having a tapered tip at the clutch hub 16 side is formed on the outer periphery of the first gear piece 21, and the outer periphery of the flange formed on the root side of the conical surface 21b has the same tooth profile as that of the external spline 16a. An external spline 21a is formed. The second transmission gear 25 is rotatably supported by a third shaft portion 13 between the clutch hub 16 and the fourth shaft portion 14 via a needle bearing 28 and is prevented from being detached by a retainer ring 18 and a washer 18a. As in the case of the first transmission gear 20, the second gear piece 26 is integrally press-fitted and fixed to the boss portion on the clutch hub 16 side of the second transmission gear 25, and includes a conical surface 26b and an external spline 26a. Is the same as the first gear piece 21.

  The outer peripheral surface 22a of the annular first synchronizer ring 22 is fitted to the inner surface of the cylindrical portion on one side of the outer peripheral portion 16b on the first transmission gear 20 side of the clutch hub 16, with a slight gap therebetween. Thus, the first synchronizer ring 22 is supported between the clutch hub 16 and the first transmission gear 20 so as to be movable and rotatable in the axial direction with respect to the clutch hub 16. The first synchronizer ring 22 has a conical hole 22c that can be frictionally engaged with the conical surface 21b of the first gear piece 21 on the inner periphery, and is an end that protrudes outward in the axial direction from the outer peripheral portion 16b of the clutch hub 16. An external spline 22d having the same tooth shape as the external spline 16a is formed on the outer periphery of the flange formed on the edge. Like the first synchronizer ring 22, a second synchronizer ring 27 is supported between the clutch hub 16 and the second transmission gear 25 so as to be movable and rotatable in the axial direction with respect to the clutch hub 16. The shape including the conical hole 27 c and the external spline 27 d is the same as that of the first synchronizer ring 22.

  The sleeve 30 has an inner spline 30a formed on the inner periphery thereof engaged with an outer spline 16a of the outer peripheral portion 16b of the clutch hub 16 so as to be slidable in the axial direction, and a circumferential groove 30b is formed on the outer periphery. . If the sleeve 30 is shifted to the first transmission gear 20 side by a shift fork (not shown) engaged with the circumferential groove 30b, the internal spline 30a can be engaged with the external spline 22d and the external spline 21a. If it is shifted to the second transmission gear 25 side, the internal spline 30a can be engaged with the external spline 27d and the external spline 26a.

  As shown in FIGS. 1 to 3, the outer peripheral portion 16b of the clutch hub 16 is formed with a deep groove along the axial direction at each position obtained by dividing the circumferential direction into three equal parts. A shifting key 31 is provided to be slidable in the radial direction. This shifting key 31 is formed with a protrusion 31a having a slanted surface on both sides at the center in the longitudinal direction, and is urged outward in the radial direction by a spring 32 provided in a hole formed in the bottom surface of each groove. Thus, the protrusion 31a is elastically engaged with a recess formed on the inner side of the internal spline 30a of the sleeve 30 and having loose inclined surfaces on both sides.

  As shown mainly in FIGS. 2 and 3, the cylindrical portions on both sides of the outer peripheral portion 16 b of the clutch hub 16 are each provided with three thirds on one side over a certain range in the circumferential direction centering on each shifting key 31. Two notches 16f and 16g are formed, and three first notches (first engaging portions) 16d and 16e are formed on one side between the second notches 16f and 16g. Both side edges in the circumferential direction of the second notches 16f and 16g are on a plane including the central axis of the rotary shaft 10 and are parallel to each other, but both edges of the first notches 16d and 16e are radially outward. The inclined surfaces 16d1 and 16e1 are inclined with respect to the central axis of the rotary shaft 10 when viewed from the side. The slopes 16d1 and 16e1 on both sides of the first notches 16d and 16e are opposite to each other, and the first notches 16d and 16e gradually increase in width from the open side to the back.

  As shown mainly in FIGS. 2 and 3, the outer peripheral surface 22a of the first synchronizer ring 22 protrudes into the first and second cutouts 16d and 16f of the clutch hub 16 but has a tooth bottom of the external spline 16a. First and second protrusions 22b and 22e that do not protrude outward from the circle are formed. The width of the first protrusion 22b in the circumferential direction is smaller than the width of the first notch 16d, and both side edges thereof can contact the corresponding first inclined surface 16d1 when viewed from the outside in the radial direction with substantially no gap. It becomes the inclined surface 22b1. Accordingly, the first synchronizer ring 22 is in contact with the position where one second inclined surface 22b1 is in contact with the corresponding first inclined surface 16d1, and the other second inclined surface 22b1 is in contact with the corresponding first inclined surface 16d1. It is possible to rotate with respect to the clutch hub 16. The first protrusion 22b has the maximum width at the tip portion on the clutch hub 16 side, but this maximum width is smaller than the minimum width on the open side of the first notch 16d. Both side edges in the circumferential direction of the second protrusion 22e are parallel to each other, and the circumferential width thereof is smaller than the width of the second notch 16f. However, the second protrusion 22e is restrained by the contact between the first and second inclined surfaces 16d1 and 22b1. Within the pivotable range in which the second notch 16f and the second protrusion 22e are not in contact with each other, the both side edges of the second notch 16f and the second protrusion 22e are not in contact with each other. First and second protrusions 27b and 27e are also formed on the outer peripheral surface 27a of the second synchronizer ring 27 so as to protrude into the first and second notches 16e and 16g of the clutch hub 16. Since the relationship between the shape of each part of the second synchronizer ring 27 and the shape of each part of the clutch hub 16 is the same as that of the first synchronizer ring 22 described above, detailed description thereof is omitted.

  Although not shown, a transmission gear meshed with each of the transmission gears 20 and 25 is fixed to a rotation shaft provided in parallel with the rotation shaft 10, and the sleeve 30 is shifted and meshed with each other as described below. By switching a pair of transmission gears, the gear position is switched between both rotating shafts.

  Next, the operation of the above-described embodiment will be described. When the sleeve 30 is shifted to the first transmission gear 20 side by a shift fork (not shown) engaged with the circumferential groove 30b from the neutral state shown in FIG. 1, the spring 30 and the protrusion 31a elastically move to the sleeve 30. The engaged shifting key 31 moves together with the sleeve 30 and abuts against and presses against the second protrusion 22e of the first synchronizer ring 22 to frictionally engage the conical hole 22c of the first synchronizer ring 22 with the conical surface 21b. Thus, the rotational speed of the first transmission gear 20 is brought close to the rotational speed of the clutch hub 16, and the internal spline 30 a of the sleeve 30 is engaged with the external spline 22 d of the first synchronizer ring 22 to rotate the first transmission gear 20. Is synchronized with the rotation of the clutch hub 16, the internal spline 30a is replaced with the external spline 21a of the first transmission gear 20. And engaged, coupling the first transmission gear 20 to the clutch hub 16. If the sleeve 30 is returned to the state shown in FIG. 1 by the shift fork, the pressing force of the shifting key 31 against the first synchronizer ring 22 is eliminated, so that the frictional engagement between the conical surface 21b and the conical hole 22c is released, and the first synchronizer ring is released. 22 is rotatable with respect to the clutch hub 16 within a range in which the first and second inclined surfaces 16d1 and 22b1 are not restrained by contact. When the sleeve 30 is shifted to the second transmission gear 25 side by the shift fork, the second transmission gear 25 is connected to the clutch hub 16 in the same manner as described above, and if the sleeve 30 is returned to the original position, the second synchronizer The ring 27 is rotatable with respect to the clutch hub 16 within a range where the first and second inclined surfaces 16e1 and 27b1 are not restrained by contact.

  For example, when the rotary shaft 10 is driven by the prime mover and the sleeve 30 is shifted to the second transmission gear 25 that is the high speed stage, the second transmission gear 25 has the same speed as the rotary shaft 10 and the clutch hub 16. The first transmission gear 20 is rotated in the same direction at a higher speed than that. As described above, the first synchronizer ring 22 has a slight clearance on the inner surface of the cylindrical portion on one side of the outer peripheral portion 16b on the first transmission gear 20 side of the clutch hub 16 with a slight clearance on the outer peripheral surface 22a. Therefore, the first synchronizer ring 22 is lowered or inclined due to its own weight or the like, so that the conical hole 22c and the conical surface 21b are linearly contacted along the generatrix or the corners are point-contacted. There is. In that case, the first synchronizer ring 22 is dragged by the friction of the abutting portion and rotates with respect to the clutch hub 16, and either one of the second inclined surfaces 22b1 of the first protrusions 22b corresponds to the corresponding first cut. It stops in contact with the first inclined surface 16d1 of the notch 16d in the circumferential direction. Since the directions of the two inclined surfaces 16d1 and 22b1 are as described above, a force acting toward the clutch hub 16 is generated by the pressing force acting between the two inclined surfaces 16d1 and 22b1, and the first synchronizer ring 22 is generated. Is pulled back to the clutch hub 16 side. As a result, the gap between the conical surface 21b and the conical hole 22c increases, so that the conical surface 21b and the conical hole 22c come into contact with each other linearly or in a dotted manner even if the first synchronizer ring 22 is lowered or inclined due to its own weight or the like. Therefore, no energy loss due to wear or friction of the conical surface 21b and the conical hole 22c, or local uneven wear does not occur. When the sleeve 30 is shifted to the first speed change gear 20 that is the low speed stage, the second speed change gear 25 is the same except that the first speed change gear 20 is rotated in the same direction at a lower speed. By such an action, the second synchronizer ring 27 is pulled back to the clutch hub 16 side. As a result, the gap between the conical surface 26b and the conical hole 27c increases, so that the conical surface 26b and the conical hole 27c do not come into contact with each other in a linear or dotted manner, and energy loss due to wear or friction occurs. Alternatively, local uneven wear does not occur.

  In the embodiment described above, the clutch hub 16 is formed with the first notches 16d and 16e having the first inclined surfaces 16d1 and 16e1 that are inclined with respect to the central axis of the rotary shaft 10 when viewed from the outside in the radial direction on both sides in the circumferential direction. Each of the synchronizer rings 22 and 27 is formed with first protrusions 22b and 27b having second inclined surfaces 22b1 and 27b1 that are similarly inclined. The first notches 16d and 16e and the first protrusions 22b and 27b The first and second engagement portions 16d, 16e and 22b, 27b are brought into contact with each other in the circumferential direction and pull back the synchronizer rings 22, 27 to the clutch hub 16 side. Since the structures of the joint portions 16d, 16e and 22b, 27b are very simple, the cost required for implementation can be reduced. However, the first and second engaging portions 16d, 16e and 22b, 27b of the present invention are not limited to such a structure, and various structures can be used. Alternatively, one of the first engaging portions 16d and 16e and the second engaging portions 22b and 27b has inclined surfaces 16d1 and 16e1 or inclined surfaces 22b1 and 27b1 as shown in FIG. An abutting arcuate portion or the like may be provided instead of the inclined surface, so that the structure of the first and second engaging portions 16d, 16e and 22b, 27b can be further simplified. The required cost can be further reduced.

  Further, in the above-described embodiment, each of the synchronizer rings 22 and 27 is formed with a total of six protrusions 22b, 27b, 22e, and 27e, and correspondingly, each of the both sides of the clutch hub 16 has a total of each. Although six notches 16d, 16e, 16f, and 16g are formed, each of the six protrusions omits the three second protrusions 22e and 27e, and only the three first protrusions 22b and 27b. Correspondingly, each of the six cutouts omits each of the three second cutouts 16f and 16g and has only three first cutouts 16d and 16e, and the shifting key 31 faces 3 You may make it arrange | position between 1st protrusion 22b, 27b of a pair. In this way, the structure is simplified and the manufacturing cost can be further reduced. If necessary, the circumferential widths of the first protrusions 22b and 27b and the first notches 16d and 16e may be appropriately increased.

  Further, in the above-described embodiment, the example in which the transmission gears 20 and 25 and the synchronizer rings 22 and 27 are provided on both sides of the clutch hub 16 is described. However, the present invention is not limited to this, and depending on the number of shift stages. It is also possible to carry out by providing a transmission gear and a synchronizer ring on one side of the clutch hub.

It is a longitudinal cross-sectional view explaining one Embodiment of the synchronizing device of the transmission by this invention. It is a side view of embodiment shown in FIG. FIG. 3 is a sectional view taken along line 3-3 in FIG. 2.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 ... Rotary shaft, 16 ... Clutch hub, 16a ... External tooth spline, 16d, 16e ... 1st engaging part (1st notch), 16d1, 16e1 ... 1st inclined surface (part), 20, 25 ... Shift Gears, 21a, 26a ... external splines, 21b, 26b ... conical surfaces, 22, 27 ... synchronizer rings, 22b, 27b ... second engaging portions (first protrusions), 22b1, 27b1 ... second inclined surfaces (partly) ), 22c, 27c ... conical holes, 22d, 27d ... external splines, 30 ... sleeves, 30a ... internal splines.

Claims (2)

  A clutch hub that is rotated integrally with the rotary shaft, and a sleeve that has an internal spline that is engaged with an external spline formed on the outer periphery of the clutch hub and that is reciprocally shifted in the axial direction; A transmission gear that is rotatably supported by the rotating shaft on one side of the clutch hub and that has an external spline and a conical surface integrally formed with a boss portion on the clutch hub side and engaged with the internal spline; The clutch hub is supported between the clutch hub and the transmission gear so as to be movable and rotatable in the axial direction with respect to the clutch hub, and is pressed toward the transmission gear by the shift in the axial direction of the sleeve to be coaxial with the inner circumference. The formed conical hole is frictionally engaged with the conical surface, and external splines formed on the outer periphery engage with the internal splines, thereby rotating the transmission gear. In the transmission synchronizer provided with a synchronizer ring that synchronizes with the rotation of the clutch hub and the synchronizer ring, the clutch hub and the synchronizer ring are brought into contact with each other in the circumferential direction by relative rotation of the two, and the synchronizer ring is disposed on the clutch hub side. A transmission synchronizer comprising a first engaging portion and a second engaging portion that are pulled back to each other. In the transmission synchronization device according to the preceding item, either one of the first engagement portion and the second engagement portion has an inclined surface that is inclined with respect to a central axis of the rotation shaft when viewed from the outside in the radial direction, A synchronizer for a transmission, wherein the inclined surface comes into contact with a part of the other to pull back the synchronizer ring toward the clutch hub.

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