JP2008175250A - Synchronizing device of transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a synchronizing device of transmission which can avoid double intermeshing and improve a durability of balk ring simultaneously. <P>SOLUTION: The synchronizing device of transmission, which comprises a coupling sleeve, a clutch gear, a balk ring, a synchronous hub, and a support synchronous force generating mechanism converting a circumferential force generated by the relative rotation into an axial support synchronous force pushing the balk ring to the clutch gear when relative rotation between the synchronous hub and the balk ring is generated in such a way that frictional torque is generated between balk ring taper cone surface and clutch gear taper cone surface at the time of gear change, is characterized in that a locking portion limiting a generation of the support synchronous force is arranged by regulating the relative rotation between the balk ring and the synchronous hub at the time of neutral state of the transmission and gear change of the other gear stage. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a transmission synchronization device that is applied to a vehicle gear transmission and the like and includes a coupling sleeve, a synchro hub, baux ring, and a clutch gear.

Conventionally, in a transmission synchronizer, when a driver moves a coupling sleeve by operating a shift lever during gear shifting, the chamfers of the coupling sleeve and the baux ring come into contact with each other to prevent movement of the coupling sleeve. The bokeling taper cone surface presses the clutch gear taper cone surface to generate a friction torque (synchronizing force), so that the rotation synchronizing action between the bokeling and the synchro hub is performed (see, for example, Patent Document 1). .
JP-A-2005-114156

  However, in the above prior art, when an unintended relative rotation between the bokeh ring and the synchro hub occurs at the time of shifting, a support synchronization force is generated, and the two positions are simultaneously synchronized and double-engaged at the time of shifting, There was a risk that the shift would lock. Further, when a support synchronization force is generated at the neutral time, the clutch gear and the tapered cone surface of the baux ring always come into contact with each other, and there is a problem that the durability of the boke ring is remarkably impaired.

  The present invention has been made paying attention to the above-mentioned problems, and the object of the present invention is to prevent unintentional relative rotation between the baux ring and the synchro hub, thereby avoiding double meshing and durability of the boke ring. It is an object of the present invention to provide a transmission synchronizer with improved performance.

  In order to achieve the above object, in the present invention, friction torque is generated between the coupling sleeve, the clutch gear, the baux ring, the sync hub, and the bokeling taper cone surface and the clutch gear taper cone surface at the time of shifting. Thus, when a relative rotation occurs between the synchro hub and the baux ring, the circumferential force due to the relative rotation is converted into an axial support synchronization force that presses the boke ring against the clutch gear. In a transmission synchronizer including a support synchronization force generating mechanism, the support synchronization force is controlled by restricting relative rotation between the baux ring and the sync hub during a neutral state of the transmission and a shift of another gear stage. A lock is provided to limit the occurrence of

  Therefore, it is possible to provide a transmission synchronizer that avoids double meshing and improves the durability of bokeling.

  DESCRIPTION OF THE PREFERRED EMBODIMENTS The best mode for realizing a transmission synchronization apparatus according to the present invention will be described below based on an embodiment shown in the drawings.

[Synchronizer configuration]
FIG. 1 is a cross-sectional view taken along the line AA (see FIG. 2) in the synchronization device neutral state of the transmission of the present application, and FIG. 2 is an axial front view. The axial direction of the synchronizer is the x axis, and the direction from the coupling sleeve 1 to the main gear 2 is the positive direction.

  The transmission synchronizer includes a coupling sleeve 1, a main gear 2, a clutch gear 3, and a baux ring 4. Further, a sync hub 5, an insert key 6, a spread spring 7, and a main shaft 8 are provided.

  The coupling sleeve 1 is an input member for shifting operation load (manual operation force or actuator driving force), and is splined to the sync hub 5. The coupling sleeve 1 is provided so as to rotate integrally with the sync hub 5 and move in the x-axis direction.

  A shift fork is fitted in the groove on the outer surface of the coupling sleeve 1, and two coupling chamfers are formed on the circumferential surface for each gear position. Thereafter, the two chamfers are designated as the first and second chamfers 11 and 12 regardless of the gear position.

  The first-stage chamfer 11 and the second-stage chamfer 12 are alternately provided so that their radial positions do not overlap each other, and the length in the x-axis direction is short for the first-stage chamfer 11 and the second-stage chamfer 12 is long. ing. The first-stage chamfer 11 is provided on both sides of the second-stage chamfer 12, and the first-stage chamfer 11 comes into contact with the baux ring 4 first when the coupling sleeve 1 is fitted to the boke ring 4. It has become.

  The main gear 2 is rotatably provided with respect to the main shaft 8 and rotates integrally with the main shaft 8 when the speed change operation is completed.

  The clutch gear 3 is a synchronizing member that synchronizes the rotation of the main gear 2 and the rotation of the synchro hub 5 and is integrally fixed to the main gear 2 by press-fitting or the like. A clutch gear taper cone surface 31 is formed on the clutch gear 3, and the clutch gear 3 is taper-fitted to the bokeling taper cone surface 41 of the baux ring 4.

  The baux ring 4 is a synchronizing member that synchronizes the rotation of the main gear 2 and the rotation of the sync hub 5, and is movable in the axial direction and relatively rotatable in the circumferential direction by a predetermined amount with respect to the sync hub 5. The predetermined amount is a chamfer alignment movement amount of the spline teeth.

  A bokeling tapered cone surface 41 and a bokeling chamfer 43 are formed on the bokeling 4. The x-axis direction component of the distance between the tapered cone surfaces 41 and 31 of the boke ring 4 and the clutch gear 3 is b, and they are taper-fitted to each other.

  Further, a protrusion 120 protruding in a T-shape in the negative x-axis direction is provided on the outer peripheral portion of the boke ring 4, and a trapezoidally protruding cam 40 is provided at a position shifted in the radial direction with respect to the protrusion 120. Is provided. On the side surface of the cam 40, a bokeling cam surface 42 is provided in the inner diameter direction toward the negative x-axis direction (see FIG. 2).

  The synchro hub 5 is a synchronizing member that is splined to the main shaft 8. A groove portion 110 that is recessed in a T-shape toward the negative x-axis direction is provided on the outer periphery of the synchro hub 5 (see FIG. 2), and the projection portion 120 on the outer periphery of the boke ring 4 is engaged with the groove portion 110 so 5 and a lock portion 100 that restricts the relative rotation of the boke ring 4 while allowing it to a certain degree.

  In the embodiment of the present invention, the protrusion 120 and the groove 110 are both T-shaped. However, the protrusion 120 and the groove 110 may not be T-shaped as long as the relative rotation between the boke ring 4 and the synchro hub 5 is locked by engagement. .

  The sync hub 5 is provided with a concave cam 50 for accommodating the cam 40 of the boke ring 4, and a sync hub cam surface 52 that abuts the boke ring cam surface 42 is provided on both sides of the cam 50. Yes. The cam surfaces 42 and 52 are inclined with respect to the x axis at an angle θ (see FIG. 4).

  As a result, when the cam surfaces 42 and 52 come into contact with each other due to the relative rotation of the bokeling 4 and the synchro hub 5 at the time of shifting, the radial force that the bokeling 4 receives from the synchro hub 5 is decomposed, and the x-axis support Synchronous force is generated. On the other hand, when the relative rotation is not generated and when the cam surfaces 42 and 52 are separated (such as when neutral), the baux ring 4 does not receive a force from the synchro hub 5, and thus no support synchronizing force is generated.

  The insert key 6 is a synchronizing member disposed on the outer periphery of the synchro hub 5. The insert key 6 is supported by the synchro hub 5, the coupling sleeve 1, and the spread spring 7.

  The key projection provided on the outer periphery of the insert key 6 and the key groove of the coupling sleeve 1 are positioned in a locked state, rotate together with the synchro hub 5 and move in the axial direction in conjunction with the coupling sleeve 1. It is movable.

[Details of lock part]
FIGS. 3 and 4 are views showing a neutral state where the bokeh ring 4 is dragged by the synchro hub 5, and FIGS. 5A and 5B are views showing a neutral state where the lock portion 100 is clogged. Each of FIGS. 3 to 5 shows a case where the baux ring 4 (synchronized side) rotates faster than the sync hub 5 (synchronized side).

  As described above, the lock portion 100 is provided on the outer periphery of the sync hub 5 and the boke ring 4. The protrusion 120 of the bokeh ring 4 is a T-shaped protrusion, and enters the groove 110 of the synchro hub 5 provided in the same T-shape and is locked in the circumferential direction. The relative rotation of 5 is restricted.

  The groove part 110 is formed of a circumferential groove 111 and an axial groove 112 which are T-shaped heads. Similarly, the T-shaped protrusion 120 is formed of a circumferential portion 121 extending in the circumferential direction and an axial portion 122 extending in the negative x-axis direction and supporting the circumferential portion 121.

  In the neutral state and in the initial position state of the baux ring 4, the central axis L2 of the circumferential portion 121 and the central axis L1 of the axial groove 112 coincide. Further, the groove portion 110 is provided with a size that can accommodate the projection portion 120. When the circumferential width of the circumferential groove 111 is D and the circumferential width of the circumferential portion 121 is d, D> d. (See FIG. 2).

(Relationship between groove and protrusion width and lock)
The groove part 110 is a T-shaped groove, and the circumferential width e of the axial groove 112 is smaller than the circumferential width = D of the circumferential groove 111 (D> e). Further, the circumferential width d of the protruding portion radial direction portion 121 is smaller than the circumferential width e of the axial groove 112 (e> d).

  Therefore, in the neutral state, the protrusion 120 can freely enter and exit from the groove 110 in the x-axis direction (see FIG. 2). As a result, the protruding portion 120 is allowed to escape from the groove portion 110 to allow relative rotation between the baux ring 4 and the synchro hub 5 to generate a support synchronizing force when necessary.

  Further, the protrusion 120 closes to one side in the circumferential direction of the groove 110, whereby the protrusion circumferential direction 121 is locked by the axial groove 112 in the x-axis positive direction movement. As a result, the protrusion 120 is engaged with the groove 110, and the baux ring 4 is locked against movement in the x-axis positive direction with respect to the synchro hub 5.

(Relationship between protrusion and groove play and axial distance between cam surfaces)
Since the circumferential widths of the projecting portion 120 and the groove portion 110 are D and d, respectively, the play existing on both sides in the circumferential direction between the projecting portion 120 and the groove portion 110 is (D−d) / 2 in the neutral state. Become. The protrusion 120 is relatively movable in the circumferential direction on both sides in the groove 110 by the amount of play (D-d) / 2.

  Here, when the bokeling cam surface 42 and the synchro hub cam surface 52 come into contact with each other in order to generate the support synchronization force, it is necessary to reduce the clearance between the cam surfaces 42 and 52. Therefore, in order to close the clearance between the cam surfaces 42 and 52, the bokeling 4 rotates relative to the sync hub 5, and the play between the protrusion 120 and the groove 110 is clogged accordingly.

  Therefore, even if there is a backlash between the protrusion 120 and the groove 110 in the lock portion 100, the backlash is consumed to reduce the clearance between the cam surfaces 42 and 52. Therefore, the amount by which the protrusion 120 can move relative to the groove 110 in the lock portion 100 is also reduced by the clearance between the cam surfaces 42 and 52.

Therefore, when the circumferential distance between the bokeling cam surface 42 and the synchro hub cam surface 52 at the neutral time is h, the amount that the protrusion 120 can move relative to the groove 110 is (D−d) / 2−h
It is.

Since the cam surfaces 42 and 52 are inclined by θ with respect to the x-axis, the bokeling 4 moves in the positive x-axis direction by this relative movement amount (relative movement amount of the protrusion 120 with respect to the groove 110 in the lock portion 100). The quantity H is H = {(D−d) / 2−h} tan θ (i)
It is.

(Relationship between bokeling movement in x-axis direction and support synchronization force)
In the neutral state, the baux ring 4 and the synchro hub 5 rotate at a constant speed. The tapered cone surfaces 41 and 31 of the boke ring 4 and the clutch gear 3 are not in contact with each other, and the x-axis direction component of the distance between the tapered cone surfaces 41 and 31 is b (see FIG. 1).

  Therefore, when the bokeling 4 moves only to the x-axis positive direction side distance b, the tapered cone surfaces 41 and 31 come into contact with each other, and the bokeling 4 is dragged by the clutch gear 3. As a result, relative rotation with the synchro hub 5 occurs, and a support synchronization force is generated.

  Therefore, when the movement amount H shown by the above formula (i) is larger than the distance between the tapered cone surfaces 41 and 31 and the x-axis direction component b, the tapered cone surfaces 41 and 31 come into contact with each other due to backlash in the lock portion 100. End up.

  That is, the bake ring 4 moves in the positive direction of the x-axis by the distance H due to looseness in the lock unit 100. At this time, since H> b, the clearance between the tapered cone surfaces 41 and 31 is clogged and contacted.

  In this case, the tapered cone surfaces 41 and 31 come into contact with each other regardless of the shift operation due to backlash in the lock portion 100. For this reason, there exists a possibility that each taper cone surface 41 and 31 may contact even if it is in a neutral state, and durability may be impaired.

  Further, the baux ring 4 is dragged by the synchro hub 5 due to the friction between the tapered cone surfaces 41 and 31, and a relative rotation occurs to generate a support synchronizing force. For this reason, an unintended support synchronization force is generated during the shift operation, and there is a possibility that a double shift between a desired shift speed and another shift speed may occur.

Therefore, in the embodiment of the present application, when the movement amount in the positive direction of the x-axis of the bake ring 4 when the play in the lock portion 100 is clogged is H, and the x-axis direction component of the distance between the tapered cone surfaces 41 and 31 is b,
b> H
This relationship is established.

  Thereby, even when the bokeh ring 4 moves the distance H in the positive x-axis direction by loosening in the lock portion 100, H is smaller than the distance between the tapered cone surfaces 41 and 31, the x-axis direction component b. The tapered cone surfaces 41 and 31 do not come into contact with each other due to the looseness of the lock portion 100. Therefore, it is possible to avoid the durability deterioration of the tapered cone surfaces 41 and 31 and the generation of unintended support synchronization force.

(Neutral action by first stage chamfa)
When the coupling sleeve 1 moves in the positive direction of the x-axis, the first-stage chamfer 11 and the chamfer 43 of the baux ring 4 come into contact with each other. After the contact, the first stage chamfer 11 pushes the baux ring chamfer 43 and moves in the positive x-axis direction.

  When the first-stage chamfer 11 and the bokeh chamfer 43 are engaged with each other, the baux ring 4 is provided in a neutral position with respect to the coupling sleeve 1 and the synchro hub 5. Therefore, by moving the coupling sleeve 1 in the positive x-axis direction, the first-stage chamfer 11 and the bauxing chamfer 43 are engaged with each other, so that the bokeling 4 is in the neutral position.

(Relationship between bokeling-insert key distance and first-stage chamfer-bowling distance)
In the neutral state, the distance between the boke ring 4 and the insert key 6 in the x-axis direction is c (see FIG. 3). In the neutral state, the distance in the x-axis direction between the front surface 11a of the first-stage chamfer 11 of the coupling sleeve 1 and the root portion 43a ′ of the front surface 43a of the bauxing chamfer 43 is G1a (see FIG. 5).

  Here, it is assumed that the distance between the bokeling 4 and the insert key 6 is c> the distance G1a between the first stage chamfer front surface 11a and the balk ring chamfer front surface root portion 43a ′. For this reason, when the coupling sleeve 1 is moved in the positive x-axis direction, the first-stage chamfer 11 comes into contact with and engages with the bokeh chamfer 43 before the insert key 6.

  As described above, when the first stage chamfer 11 and the baux ring chamfer 43 are completely fitted, the boke ring 4 is in the neutral position. Therefore, by defining the relationship of c> G1a, in the middle of the shift state, the first stage chamfer 11 and baux ring chamfer 43 are first contacted and fitted to bring the boke ring 4 into the neutral state, and then the insert key 6 and boke The ring 4 can be securely fitted.

(Relationship between protrusion of lock and balking neutral position)
When the bake ring 4 is pushed to the x-axis positive direction side by the insert key 6, the back surface 11 b of the first-stage chamfer 11 (x-axis negative direction side end surface) and the back surface 43 b of the boke ring chamfer 43 (x-axis positive direction side) The distance from the end face is G1b (see FIG. 11). At that time, the amount of protrusion in the negative direction of the x-axis of the baux ring protrusion 120 in the lock portion 100 is a (see FIG. 11).

  In the present application, the distance G1b between the first-stage chamfer back surface 11b and the baux ring chamfer back surface 43b is greater than the protrusion protrusion amount a. Here, the protrusion protrusion amount a is the unlocking dimension of the lock part 100 (if the protrusion part 120 moves a distance a in the x-axis positive direction from the locked state, the protrusion part 120 completely escapes from the groove part 110).

  Therefore, by defining the relationship of G1b> a, even when the bokeling 4 is pushed by the insert key 6 and the protrusion 120 escapes from the groove 110, the first-stage chamfer 11 and the bokeling chamfer 43 are It will still be in a fitting state. For this reason, until the lock part 100 is unlocked, the baux ring 4 remains in the neutral position.

  Thus, the bokeling 4 is held in the neutral position until the lock of the lock portion 100 is completely released, and the bokeling 4 and the cam surfaces 42 and 52 of the synchro hub 5 do not contact each other. Therefore, when the bokeling 4 and the sync hub 5 are locked by the lock unit 100, an unintended support synchronization force does not occur.

(Relationship between unlocking dimension and distance between clutch gear and bokeling taper cone surface)
As described above, the x-axis direction component of the distance between the tapered cone surfaces 41 and 31 of the boke ring 4 and the clutch gear 3 is b (see FIG. 1). The relationship between the taper cone surface distance b and the back surface distance G1b (see FIG. 11) of the first-stage chamfer 11-boke ring chamfer 43 is defined by b> G1b.

  Therefore, when the bokeling 4 moves in the x-axis positive direction along with the movement of the coupling sleeve 1 in the x-axis positive direction and the lock part 100 is unlocked, the first stage chamfer 11 passes through the bokeling chamfer 43. The tapered cone surfaces 31 and 41 are not yet in contact with each other.

  The support synchronization force is not generated until the relative rotation between the boke ring 4 and the sync hub 5 occurs. Until the rotation of the bake ring 4 is suppressed by the frictional force between the tapered cone surfaces 41 and 31, the boke ring 4 and the synchro hub 5 rotate integrally, so that the support synchronization is performed until the tapered cone surfaces 41 and 31 come into contact with each other. No force is generated.

  Therefore, by bringing the tapered cone surfaces 31 and 41 into contact with each other after the lock portion 100 is completely unlocked, the bokeling 4 and the synchro hub 5 are integrally rotated during the lock, and a support synchronization force is generated. It is the structure which can avoid reliably.

(First stage, second stage chamfer mesh)
When the first-stage chamfer 11 and the bokeh chamfer 43 contact, the distance between the front end 11a of the first-stage chamfer 11 and the front end 32a of the clutch gear chamfer 32 is f, and the front base of the second-stage chamfer 12 The distance between 12a ′ and the front base portion 43a ′ of the baux ring chamfer is F (see FIG. 7).

  In this case, the relationship between f and F is defined by f> F. For this reason, when the coupling sleeve 1 further moves in the positive x-axis direction after the first-stage chamfer 11 has penetrated the bokeh chamfer 43, the second-stage chamfer 12 first contacts the bokeling chamfer 43.

  Thereafter, after the second-stage chamfer 12 passes through the bokeling chamfer 43, the first-stage chamfer 11 comes into contact with and engages with the clutch gear chamfer 32.

  As a result, when the clutch gear chamfer 32 and the first-stage chamfer 11 are fitted, the second-stage chamfer 12 is completely disengaged from the baux ring chamfer 43, and the clutch gear chamfer 32-1st stage. It is possible to avoid the double engagement state in which the chamfer 11 and the bokeh chamfer 43-2 stage chamfer 12 are engaged at the same time.

[Movement of lock part with shifting]
(Neutral state + initial bokeh position: Fig. 1 and Fig. 2)
When in the neutral state and the bake ring 4 is in the initial position, as described above, the central axis L1 of the circumferential portion 121 (projection portion 120) and the central axis L2 of the axial groove 112 (groove portion 110) coincide (see FIG. 2). ), The protrusion 120 can freely enter and exit from the groove 110 in the x-axis direction.

(Neutral state + bakeling dragged state: Fig. 3 and Fig. 4)
When there is relative rotation between the synchro hub 5 and the baux ring 4, the boke ring 4 is always dragged in the rotation direction in the neutral state. Therefore, in the lock part 100, the protrusion part 120 has approached the circumferential direction edge part (according to the relative rotation direction of the boke ring 4 and the synchro hub 5) (refer FIG. 4).

(Neutral state + locked backlash clogged state: Fig. 5)
When the bokeh ring 4 is further dragged, the lock portion 100 is completely clogged with the backlash (Dd) / 2 between the projection portion 120 and the groove portion 110, and the bake ring 4 is locked (locked) to the sync hub 5 by the lock portion 100. )

  As described above, when the backlash (Dd) / 2 of the lock portion 100 is clogged, the cam surfaces 42 and 52 do not come into contact with each other, and thus no support synchronization force is generated.

(1 state during shifting (first stage chamfer contact): FIGS. 6 and 7)
6 and 7 are diagrams showing one state during the shift (a state in which the first stage chamfer 11 is in contact with the bake ring 4). Continuing to FIG. 5, the backlash (D−d) / 2 between the protrusion 120 and the groove 110 is completely clogged, and no support synchronization force is generated.

  The coupling sleeve 1 is moved in the x-axis positive direction by the driver's shift operation, and the first-stage chamfer 11 of the coupling sleeve 1 contacts the chamfer 43 of the baux ring 4. Even in the contact, the baux ring 4 remains locked to the sync hub 5 by the lock portion 100.

(2 states in the middle of shifting (moving to neutral position): FIGS. 8 and 9)
FIG. 8 and FIG. 9 are diagrams showing two states during the shift (a state where the first-stage chamfer 11 pushes the bokeling chamfer 43 and the bokeling 4 moves to the neutral position).

  8 and 9, the coupling sleeve 1 further moves in the x-axis positive direction, the first-stage chamfer 11 pushes the bauxing chamfer 43 and advances in the x-axis positive direction, and the bokeling 4 rotates relative to the sync hub 5. To do. Therefore, the central axis L2 of the protrusion 120 and the central axis L1 of the groove 110 coincide with each other, and the bokeling 4 moves to the neutral position.

  As a result, the engagement between the projection 120 and the groove 110 is released in the lock unit 100, and the projection 120 can be relatively moved in the radial direction within the groove 110. When reaching the neutral position, the protrusion 120 can freely enter and exit in the x-axis direction with respect to the groove 110. Therefore, the lock unit 100 can be prevented from being engaged during the shift to prevent the synchronization action.

(Three states during the shift (contact with the insert key and bake ring): FIGS. 10 and 11)
FIG. 10 and FIG. 11 are views showing three states during the shift (a state where the insert key 6 and the bake ring 4 are in contact). As in FIGS. 8 and 9, the bowling 4 is pushed by the first stage chamfer 11 and is in the neutral position.

(4 states during shifting (protrusion escape): FIGS. 12 and 13)
12 and 13 are diagrams showing four states during the shift (a state in which the protruding portion 120 has escaped from the groove portion 110). Since the bake ring 4 is held at the neutral position until the lock of the lock unit 100 is completely released, no support synchronization force is generated before the lock is released.

  Here, when the coupling sleeve 1 further advances in the x-axis positive direction side and the insert key 6 pushes the balk ring 4 in the x-axis positive direction side, the protrusion 120 of the boke ring 4 at the neutral position becomes the sync hub 5. Escape from the groove 110.

(5 states in the middle of shifting (first stage chamfer slips through bokeh): FIGS. 14 and 15)
FIG. 14 and FIG. 15 are diagrams showing five states during the shift (a state where the first stage chamfer 11 has completely passed through the bokeh chamfer 43). As described above, when the first-stage chamfer 11 passes through the baux ring chamfer 43, the tapered cone surfaces 31 and 41 are not yet in contact with each other, and no support synchronization force is generated.

(6 states during shifting (support synchronization force generation): FIGS. 16 and 17)
16 and 17 are diagrams showing six states during the shift (support synchronous force generation state). As described above, the relationship between the distance b between the tapered cone surfaces 31 and 41 and the back surface distance G1b (see FIG. 11) of the first-stage chamfer 11 and the baux ring chamfer 4 is defined by b> G1b. .

  Therefore, after the first-stage chamfer 11 completely passes through the bokeh chamfer 43 and the lock portion 100 is completely unlocked, the coupling sleeve 1 further advances in the x-axis positive direction, so that the tapered cone surfaces 31, 41 Contact each other. As a result, the baux ring 4 is dragged by the clutch gear 3 and rotates relative to the sync hub 5 to generate a support synchronization force.

(7 states during shifting (2nd stage chamfer is in contact with bake ring): FIG. 18, FIG. 19)
FIGS. 18 and 19 are views showing the seven states during the shift (the state where the second stage chamfer 12 is in contact with the bake ring chamfer 43). At that time, the first-stage chamfer 11 completely penetrates the baux ring chamfer 43, the tapered cone surfaces 31 and 41 come into contact with each other, relative rotation occurs between the boke ring 4 and the synchro hub 5, and a support synchronization force is generated. Yes.

(8 states during shifting (neutral action by the second stage chamfer): FIG. 20, FIG. 21)
20 and 21 are diagrams showing eight states during the shift (the state in which the bake ring 4 is shifted to the neutral position by the second stage chamfer 12). As described above, when the first-stage chamfer 11 and the bokeh chamfer 43 are in contact with each other, the distance between the first-stage chamfer front surface 11a and the clutch gear chamfer front surface 32a is greater than the second-stage chamfer front surface 12a. 43a ′ is a distance F (see FIG. 7).

  For this reason, when the coupling sleeve 1 further moves in the positive x-axis direction after the first-stage chamfer 11 has penetrated the bokeh chamfer 43, the second-stage chamfer 12 first contacts the bokeling chamfer 43. At that time, the baux ring 4 is moved to the neutral position by the second stage chamfer 12.

  Thereafter, after the second-stage chamfer 12 passes through the bokeling chamfer 43, the first-stage chamfer 11 comes into contact with and engages with the clutch gear chamfer 32. Since the first stage chamfer 11 and the second stage chamfer 12 do not engage at the same time, a shift is established.

(9 states in the middle of shifting (returning to the balking neutral position: FIGS. 22 and 23)
FIGS. 22 and 23 are views showing nine states during the shift (a state in which the baux ring 4 is returned to the neutral position by a return spring not shown). When the bake ring 4 is returned to the neutral position, the lock portion 100 can be engaged.

(Shift completed state (first stage chamfer and clutch gear engagement: FIGS. 24 and 25))
24 and 25 are diagrams showing a shift completed state (a state where the first stage chamfer 11 is fitted to the clutch gear chamfer 32). This completes the shift.

[Effect of the embodiment of the present application]
(1) The coupling sleeve 1, the clutch gear 3, the baux ring 4, the sync hub 5, and the friction torque is generated between the boke ring 4 cone surface and the clutch gear 3 cone surface at the time of shifting, thereby synchronizing. When a relative rotation occurs between the hub 5 and the boke ring 4, a support synchronization force generation mechanism that converts a circumferential force due to the relative rotation into an axial support synchronization force that presses the boke ring 4 against the clutch gear 3. A lock for limiting the generation of the support synchronizing force by restricting the relative rotation between the baux ring 4 and the synchro hub 5 when the transmission is in the neutral state and at other gear positions. Part 100 was provided.

  As a result, it is possible to avoid the occurrence of unintended support synchronization force and to prevent double meshing when the transmission is in the neutral state and at other gear positions. Further, since the clutch gear 3 and the tapered cone surfaces 31 and 41 of the bokeling 4 are not always in contact with each other at the neutral position, the durability of the bokeling can be improved.

  (2) The lock portion 100 is formed of a protrusion 120 that protrudes in the axial direction (x-axis direction) of the transmission and a groove 110 that engages with the protrusion 120. The protrusion 120 is the circumferential direction of the transmission. A circumferential direction portion 121 extending in the x-axis direction and an axial direction portion 122 extending in the x-axis direction and supporting the circumferential direction portion 121. The groove portion 110 includes a circumferential groove 111 and the circumferential groove 111. An axial groove 112 communicating therewith is used.

  As a result, in the neutral state, the relative rotation between the baux ring 4 and the synchro hub 5 can be surely restricted, and the generation of unintended support synchronization force can be reliably avoided.

  (3) The projecting portion 120 and the groove portion 110 each have a T-shaped cross section in the x-axis direction. The projecting portion 120 projects in a T shape in the axial direction from the boke ring. The protrusion 120 is provided so as to be recessed in a T shape so as to be accommodated from the axial direction. The protrusion 120 includes a circumferential portion 121 that is a T-shaped head and an axial portion 122 that supports the circumferential portion 121. The groove portion 110 is formed of a circumferential groove 111 that is a T-shaped head and an axial groove 112 that communicates with the circumferential groove 111 and opens on the x-axis positive side surface of the sync hub 6. When the radial width of the direction portion 121 is d and the radial width of the circumferential groove 111 is D, a relationship of D> d is established.

  As a result, in the neutral state, the protrusion 120 can freely enter and exit in the x-axis direction with respect to the groove 110 (see FIG. 2), and the protrusion 120 is allowed to escape from the groove 110 to be boiled. By allowing relative rotation between the synchro hubs 5, it is possible to generate a support synchronization force when necessary.

  (4) The support synchronizing force generating mechanism is formed of a bokeling cam surface 42 provided on the bokeling 4 and a synchro hub cam surface 52 provided on the synchro hub 5, and the bokeling taper cone surface 41 and the clutch gear taper. The axial component of the distance between the cone surfaces 31 is b, the angles of the bokeling cam surface 42 and the synchro hub cam surface 52 with respect to the transmission shaft are θ, and the circumferential portion 121 and the circumferential groove 111 at the neutral time are The backlash is (Dd) / 2 on both sides of the transmission in the circumferential direction. When the neutral distance between the bokeling cam surface 42 and the synchro hub cam surface 52 is h, the backlash is clogged. H = {(D−d) / 2−h} tan where H is the amount that the bokeh cam surface 42 contacts the synchro hub cam surface 52 and moves in the axial direction. It was assumed that θ and b> H.

  Thereby, even when the bokeh ring 4 moves the distance H in the positive x-axis direction by loosening in the lock portion 100, H is smaller than the distance between the tapered cone surfaces 41 and 31, the x-axis direction component b. The tapered cone surfaces 41 and 31 do not come into contact with each other due to the looseness of the lock portion 100. Therefore, it is possible to avoid the durability deterioration of the tapered cone surfaces 41 and 31 and the generation of unintended support synchronization force.

  (5) The coupling sleeve 1 has a first-stage chamfer 11 and a second-stage chamfer 12, and the first-stage chamfer 11 comes into contact with the bokeh chamfer 43 before the support synchronization force is generated. 4 is moved to the neutral position, and after the support synchronization force is generated, the second stage chamfer 12 comes into contact with the bokeling chamfer 43 and moves the bokeling 4 to the neutral position.

  This ensures that the baux ring 4 is in the neutral state during the shift, and the protrusion 120 can freely enter and exit in the x-axis direction with respect to the groove 110. Therefore, it can be avoided that the lock portion 100 is engaged during the shift to prevent the synchronization action.

  (6) An insert key 6 for pressing the bokeling 4 at the time of shifting is provided, the distance between the bokeling 4 and the insert key 6 in the neutral state is c, and the distance between the front surface of the first stage chamfer 11 and the front surface of the bokering chamfer 43 is G1a. Then, c> G1a.

  When the first-stage chamfer 11 and the baux ring chamfer 43 are completely fitted, the boke ring 4 is in the neutral position. Therefore, by defining the relationship of c> G1a, in the middle of the shift state, the first stage chamfer 11 and baux ring chamfer 43 are first contacted and fitted to bring the boke ring 4 into the neutral state, and then the insert key 6 and boke The ring 4 can be reliably fitted.

  (7) When the insert key 6 is pressing the baux ring 4, the distance between the back surface of the first stage chamfer 11 and the back surface of the boke ring chamfer 43 is G1b, and the amount of protrusion protruding from the boke ring 4 surface is If a, then G1b> a.

  Thus, the bokeling 4 is held in the neutral position until the lock of the lock portion 100 is completely released, and the bokeling 4 and the cam surfaces 42 and 52 of the synchro hub 5 do not contact each other. Therefore, when the bokeling 4 and the synchro hub 5 are locked by the lock unit 100, it is possible to avoid the occurrence of unintended support synchronization force.

  (8) The relationship between G1a and b is b> G1a.

  Thereby, the taper cone surfaces 31 and 41 are brought into contact with each other after the lock portion 100 is completely unlocked, so that the baux ring 4 and the synchro hub 5 are integrally rotated during the lock, and a support synchronization force is generated. This can be avoided reliably.

  (9) When the first stage chamfer 11 and the bokeh chamfer 43 contact each other, the distance between the front surface of the second stage chamfer 12 and the front surface of the bokeh chamfer 43 is F, and the front surface of the first stage chamfer 11 and the front surface of the clutch gear chamfer 32 And f> F, where f is the distance to.

  As a result, when the clutch gear chamfer 32 and the first-stage chamfer 11 are fitted, the second-stage chamfer 12 is completely disengaged from the baux ring chamfer 43, and the clutch gear chamfer 32-1st stage. A double engagement state in which the chamfer 11 and the bokeh chamfer 43-2 stage chamfer 12 are simultaneously engaged can be avoided.

  As mentioned above, although the synchronizing device of the transmission of this invention has been demonstrated based on the Example, it is not restricted to these Examples about a concrete structure, The invention which concerns on each claim of a Claim Design changes and additions are allowed without departing from the gist.

  In the embodiment of the present application, the lock portion 100 is formed by the projection portion 120 and the groove portion 110 having an axial section T-shaped, and the relative rotation between the boke ring 4 and the synchro hub 6 is restricted. Any other shape may be used as long as the relative rotation can be restricted at the time of shifting at the time of other gear stages).

  In other words, the protrusion only needs to have a circumferential portion that extends in the circumferential direction and an axial portion that extends in the x-axis direction and supports the circumferential portion. It is only necessary to have an axial groove communicating with the directional groove. With such a shape, even if the cross section is not T-shaped, the relative rotation between the baux ring 4 and the synchro hub 6 is restricted, and the protrusion can be released from the groove at the neutral position, thereby achieving the object of the present application.

  In addition, the synchronization device of the present invention can be applied to a manual transmission that shifts the shift lever by manual operation by a driver, and has a control type clutch between the engine and the engine at the time of shifting. The present invention can also be applied to a so-called automatic MT transmission that changes speed by a motor actuator or the like.

It is an axial sectional view in the neutral state of the synchronizing device of the transmission of the present application. It is an axial front view in the neutral state of the synchronizing device of the transmission of the present application. FIG. 3 is an axial cross-sectional view showing a neutral state and a state where the baux ring 4 is dragged by the synchro hub 5. FIG. 4 is a front view of FIG. 3. FIG. 5 is an axial front view of FIG. 4. FIG. 6 is an axial cross-sectional view showing one state during shifting (a state in which the first stage chamfer 11 is in contact with the baux ring 4). FIG. 7 is a front view of FIG. 6. FIG. 5 is an axial cross-sectional view showing two states during shifting (a state where the first-stage chamfer 11 pushes the baux ring chamfer 43 and the boke ring 4 moves to the neutral position). It is a front view of FIG. It is an axial sectional view showing a state 3 in the middle of the shift (a state where the insert key 6 and the bake ring 4 are in contact). It is a front view of FIG. FIG. 6 is an axial cross-sectional view showing four states during shifting (a state in which the protruding portion 120 has escaped from the groove portion 110). It is a front view of FIG. FIG. 5 is an axial sectional view showing five states during shifting (a state where the first-stage chamfer 11 has completely passed through the bokeh chamfer 43). It is a front view of FIG. It is an axial sectional view showing six states (support synchronous force generation state) in the middle of a shift. FIG. 17 is a front view of FIG. 16. FIG. 7 is an axial cross-sectional view showing a seven state during shifting (a state in which the second stage chamfer 12 is in contact with the baux ring chamfer 43). It is a front view of FIG. FIG. 6 is an axial cross-sectional view showing eight states during the shift (a state where the bokeh ring 4 has moved to the neutral position by the second-stage chamfer 12). FIG. 21 is a front view of FIG. 20. It is an axial sectional view showing a state 9 in the middle of the shift (a state in which the baux ring 4 is returned to the neutral position by a return spring not shown). FIG. 23 is a front view of FIG. 22. FIG. 5 is an axial cross-sectional view showing a shift completed state (a state where the first stage chamfer 11 is fitted to the clutch gear chamfer 32). It is a front view of FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Coupling sleeve 2 Main gear 3 Clutch gear 4 Bokeh ring 5 Synchro hub 6 Insert key 7 Spread spring 8 Main shafts 11 and 12 First stage, second stage chamfer 11a First stage chamfer front end 12a 'Second stage chamfer front Root portion 11b First stage chamfer back surface 31 Clutch gear taper cone surface 32 Clutch gear chamfer 32a Clutch gear chamfer front end 40 Cam 41 Bokeh ring taper cone surface 42 Bokeh ring cam surface 43 Bokeling chamfer 43a Bokeh chamfer front surface 43a 'Boke Ring chamfer front root portion 43b Bokeh chamfer rear surface 50 Cam 52 Synchro hub cam surface 100 Lock portion 110 Groove portion 111 Circumferential groove 112 Axial groove 120 Bokeh ring protrusion 12 DESCRIPTION OF SYMBOLS 1 Circumferential part 122 Axial part a Projection protrusion amount b Taper cone surface distance x Axial component c Bokering-insert key distance e Axial groove circumferential width f Between first stage chamfer front and clutch gear chamfer front Distance F Distance between the front of the 2nd stage chamfer and the front of the bokeh chamfer G1a Distance between the front of the 1st stage chamfer and the front of the bokeh chamfer G1b Distance between the back of the 1st stage chamfer and the back of the bokeh chamfer H Travel distance L1 Groove center axis L2 Projection center axis

Claims (9)

A gear stage having a coupling sleeve, a clutch gear, baux ring, and a synchro hub;
When a relative rotation occurs between the synchro hub and the bokeh ring due to a friction torque generated between the bokeling taper cone surface and the clutch gear taper cone surface at the time of shifting, the circumferential direction due to the relative rotation A synchronizer for a transmission comprising: a support synchronizing force generating mechanism that converts the force of the above into a support synchronizing force in an axial direction that presses the baux ring against the clutch gear;
A lock portion is provided that restricts the generation of the support synchronizing force by restricting the relative rotation between the baux ring and the synchro hub when the transmission is in a neutral state and when shifting at another gear stage. Transmission synchronizer. The transmission synchronizer according to claim 1.
The lock portion is formed of a protrusion that protrudes in the axial direction of the transmission, and a groove that engages with the protrusion.
The protrusion has a circumferential portion extending in the circumferential direction of the transmission, and an axial portion extending in the axial direction of the transmission and supporting the circumferential portion,
The transmission includes a circumferential groove and an axial groove that communicates with the circumferential groove. The transmission synchronizer according to claim 2,
The protrusion and the groove each have a T-shaped axial section,
The protrusion protrudes in a T shape in the axial direction from the bokeh ring,
The groove portion is provided to be recessed in a T shape on the axial side surface of the synchro hub so that the projection portion can be accommodated from the axial direction.
The protrusion is formed of a circumferential portion that is a T-shaped head and an axial portion that supports the circumferential portion.
The groove portion is formed of a circumferential groove that is a T-shaped head, an axial groove that communicates with the circumferential groove and opens on an axial side surface of the synchro hub,
The transmission synchronizing apparatus according to claim 1, wherein a relation of D> d is established, where d is a circumferential width of the circumferential portion and D is a circumferential width of the circumferential groove. The transmission synchronizer according to claim 3,
The support synchronization force generating mechanism is formed of a bokeling cam surface provided on the baux ring and a synchro hub cam surface provided on the synchro hub,
The axial component of the distance between the bokeling taper cone surface and the clutch gear taper cone surface is b,
The angle of the baux ring cam surface and the synchro hub cam surface with respect to the transmission shaft is θ,
The backlash between the circumferential portion and the circumferential groove at neutral is (D−d) / 2 on both sides of the transmission in the circumferential direction,
The circumferential distance between the bokeling cam surface and the synchro hub cam surface at the neutral time is h,
When the backlash is clogged, when the bokeling cam surface contacts the synchro hub cam surface and moves in the axial direction is H,
H = {(D−d) / 2−h} tan θ and b> H
A transmission synchronizer. The transmission synchronizer according to claim 4,
The coupling sleeve has a first stage chamfer and a second stage chamfer,
The first stage chamfer is in contact with the bokeling chamfer before the support synchronization force is generated, and moves the bokeling to a neutral position.
The second stage chamfer contacts the bokeling chamfer after the support synchronization force is generated, and moves the bokeling to a neutral position. The transmission synchronizer according to claim 5,
Provide an insert key to press the baux ring when shifting,
C> G1a, where c is the distance between the boke ring and the insert key in the neutral state, and G1a is the distance between the front surface of the first stage chamfer and the front surface of the boke ring chamfer.
A transmission synchronizer. The transmission synchronizer according to claim 6,
When the insert key is pressing the baux ring, the distance between the back of the first stage chamfer and the back of the boke ring chamfer is G1b,
G1b> a where a is the amount by which the protruding portion protrudes from the baux ring surface
A transmission synchronizer. The transmission synchronizer according to claim 7,
The relationship between G1b and b is b> G1b
A transmission synchronizer. The transmission synchronizer according to claim 8,
The distance between the front surface of the second-stage chamfer and the front surface of the bokering chamfer is F when the first-stage chamfer and the bokeh chamfer contact, and the distance between the front surface of the first-stage chamfer and the front surface of the clutch gear chamfer Let f be f> F
A transmission synchronizer.

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