JPH0540333Y2 - - Google Patents

Description

[Detailed Description of the Invention] [Industrial Application Field] The present invention relates to a synchronizing device used in a vehicle manual transmission or the like.

[Prior art]

As shown in Japanese Patent Publication No. 51-48540 as a type of synchronizer, a gear is rotatably assembled on one side of a rotating shaft and is rotatably assembled integrally with the same shaft. A clutch hub, a sleeve which is attached to the outer periphery of the clutch hub so as to be integrally rotatable and movable in the axial direction and has a tapered cone portion on the inner periphery side, and a predetermined amount of the spline portion between the sleeve and the gear spline portion of the gear. the gear; There is a synchronizer that includes a movement restricting means that is provided between a spline portion and a synchronizer ring and restricts movement of the ring in the axial direction with a predetermined force.

This type of synchronizer has a tapered cone part that is detachably provided on the outer circumferential side of the gear spline part of the gear and on the inner circumferential side of the synchronizer ring, compared to the so-called Borg-Warner type synchronizer. Large and large synchronous action (synchronous capacity)
When the synchronous capacity is kept the same, the radial and axial dimensions can be reduced to make it more compact.As a result, the amount of axial movement of the sleeve is small, so the shift stroke of the shift operating lever can be reduced. It has various advantages, such as being able to reduce the shift stroke of the shift operating lever and increasing the lever ratio of the same lever when the shift stroke of the shift operating lever is set to the same amount as the conventional one.

Therefore, in the synchronizer disclosed in the above-mentioned publication, the synchronizer ring has each protrusion provided on the inner circumferential side thereof fitted into each notch-shaped recess provided in the gear spline portion that penetrates radially inside and outside. The spline part and the synchronizer ring are assembled to the spline part by fitting into the grooves provided at the inner end of each protrusion of the ring, and the annular groove provided on the inner peripheral inclined surface of the spline part. A predetermined regulating force is coupled in the axial direction by an annular spring that is engaged in the engagement recess and whose diameter can be reduced. Therefore, according to such a synchronizing device, when the sleeve is operated in the axial direction, the tapered cone portion of the sleeve first comes into contact with the tapered cone portion of the synchronizer ring and presses the ring in the axial direction, and this pressing force reaches a predetermined value. When this occurs, the reaction force engages and synchronizes both the taper cone portions, and the spring disengages from the engagement recess in the gear spline portion, causing the ring and sleeve to move in the axial direction, causing a shift. Complete.

[Problem that the invention attempts to solve]

By the way, in such a synchronizing device, the axial engagement force of the annular spring against the engagement surface of the engagement recess of the gear spline portion becomes the axial regulating force of the synchronizer ring, but this regulating force is It greatly affects the balk action and synchronization action, and if this regulating force is not stably maintained at a set value, accurate synchronization cannot be obtained. In the above-mentioned synchronizing device, the above-mentioned regulating force cannot be stably maintained at the set value due to component tolerances of the annular spring and gear spline part (engaging recess), variations in assembly, etc., and the synchronizing action is not reliable. It will lack sex. A possible solution to this problem would be to use an annular spring with a thick wire diameter, but such a measure would result in an unnecessarily large spring force, resulting in an excessively large regulating force. In addition, if such an annular spring is adopted and the inclination angle of the engagement surface in the engagement recess of the gear spline part is made smaller to make it easier to release the engagement, the regulating force will remain at the set value and will be more stable. It becomes what it is. However, after the annular spring is disengaged from the engagement recess, the diameter of the annular spring is reduced by the inner circumferential inclined surface of the gear spline part and slides on the same inclined surface together with the synchronizer ring, so the frictional resistance becomes extremely large. In addition, the large spring force of the annular spring acts as a so-called gear disengaging force that urges the synchronizer ring toward the neutral position.

In addition, in such a synchronizer, as described above, when the synchronizer ring moves in the axial direction, the spring moves integrally with the ring in the same direction, but the spring gradually reduces its diameter due to the inclined inner circumferential surface of the gear spline part. It slides on the same inclined surface while being pressed by a large spring force that gradually increases. For this reason,
As the slopes of the spring and gear spline gradually wear out, the regulating force of the spring changes, and the engagement load and pushing load of the sleeve and synchronizer ring taper cone change, resulting in stable shift operation with long-term shift loads. cannot be maintained.

Furthermore, in such a synchronizing device, since each recess provided in the gear spline portion penetrates radially inside and outside, the strength of the gear spline portion is greatly reduced due to these recesses. As a countermeasure to this problem, it is possible to increase the rigidity by increasing the thickness of the gear spline portion, but if such a measure is adopted, the weight and cost of the device will increase.

Therefore, an object of the present invention is to eliminate the annular spring as a movement restricting means that directly restricts the movement of the synchronizer ring in the axial direction with a predetermined force, thereby achieving accurate and reliable synchronizing action and improving gear control. In addition to making it possible to maintain a shift operation with a stable shift load for a long period of time with little or no pull-out force, the gear spline part is constructed with a spline piece separate from the gear, so that each recess in the same part is The objective is to prevent a decrease in strength due to

[Means for solving problems]

Accordingly, the present invention provides the above-mentioned type of synchronizer, in which the gear spline portion is constructed by fitting an annular spline piece separate from the gear to one side of the gear, and the movement regulating means is assembled by being latched in a plurality of notch-shaped recesses provided in the circumferential direction on the outer circumferential side of the spline piece, and is elastically engaged with the inner circumferential side of the synchronizer ring, and is assembled in the axial direction of the synchronizer ring. It is characterized by being constructed with a radially inner and outer flexible leaf spring that restricts movement to the inner and outer sides with a predetermined force.

[Functions and effects of the idea]

In this configuration, when the sleeve is not operated, the sleeve and the synchronizer ring are in a disengaged state, and the ring is coupled to the gear spline section by the action of the movement restricting means provided between the gear spline section and the shaft. It is in a neutral position with directional movement restricted. When the sleeve is moved in the axial direction in this state, the sleeve presses the tapered cone portion of the synchronizer ring with its tapered cone portion, thereby pressing the ring in the axial direction against the regulating force of the movement regulating means. At this time, due to this regulating force and the rotational difference between the gear spline section and the sleeve, the synchronizer ring rotates relative to the gear spline section to the maximum extent, and a state immediately before the start of balk occurs between the two, and the subsequent rotation of the sleeve. The axial movement causes the tapered cones of both the sleeve and the synchronizer ring to engage with each other to complete synchronization. At the same time, the sleeve presses the synchronizer ring, bends the leaf spring constituting the movement restricting means radially inward, and releases the restriction of the synchronizer ring by the leaf spring. This results in
The ring rides on the leaf spring and moves in the axial direction together with the sleeve, and at the same time, the sleeve meshes smoothly with the gear spline to connect the rotating shaft and gear to complete the shift, and the two can rotate together. Become.

As described above, in the present invention, the movement restricting means for coupling the gear spline part and the synchronizer ring is assembled by being latched in each recess of the gear spline part, and is elastically attached to the inner circumferential side of the synchronizer ring. It is composed of a radially inner and outer flexible leaf spring that engages with the ring and restricts the axial movement of the ring with a predetermined force.During a shift operation, the leaf spring is deflected radially inward to prevent the axial movement of the ring. We are trying to loosen regulations. Therefore, the regulating force of the synchronizer ring in the axial direction is determined by the component tolerance of the annular spring.
The regulation means between the ring and the leaf spring will set it to a predetermined value and make it stable, without being affected by assembly variations, and as the leaf spring wears out and its spring force changes, it will not affect the synchronizer ring. There is no change in the regulating force in the axial direction.
As a result, the synchronization action is accurate and reliable, and the generation of gear disengagement force is suppressed. At the same time, due to the change in the above-mentioned regulating force, the engagement load of both tapered cone parts, the pushing load of the synchronizer ring, etc. are reduced. A stable shift operation with a shift load that does not change can be maintained for a long period of time.

In addition, in the present invention, the gear spline part is constructed by fitting an annular spline piece separate from the gear into a cylindrical attachment part provided on one side of the gear, so that each leaf spring Each recess for assembly is reinforced by the cylindrical attachment portion of the gear, thereby preventing a decrease in the strength of the gear spline portion due to each recess.
Moreover, since each recess of the spline piece can be machined independently of the gear, the machining is easy and the machining accuracy is improved.

〔Example〕

The present invention will be described below with reference to the drawings. FIGS. 1 and 2 show a synchronizing device according to an embodiment of the present invention. In each of these figures, Fig. 1 indicates the synchronization device in question -
FIG. 2 is a sectional view taken along the arrow-line direction in the figure.

Therefore, the synchronizer 10 is connected to the clutch hub 1.
1. A sleeve 12, a pair of left and right synchronizer rings 13, a spline piece 14 forming a gear spline portion, and a leaf spring 1 forming a movement regulating means.
It is composed of 5 etc.

The clutch hub 11 is mounted on an output shaft 21 constituting a transmission so that it can rotate integrally therewith, and is located between two driven gears 22 and 23 that are rotatably mounted on the shaft 21. . This clutch hub 11 is provided with a large number of outer splines 11a on its outer periphery at equal intervals in the circumferential direction. In addition, each driven gear 2
Reference numerals 2 and 23 constitute a transmission gear train, which mesh with respective drive gears that are integrally rotatably assembled on an input shaft (not shown), and a gear spline portion is integrally formed on one side of the drive gears. ing. The sleeve 12 is provided with an internal spline 12a on the inner periphery of its leg portion, and meshes with an external spline 11a provided on the outer periphery of the clutch hub 11 so as to be slidable in the axial direction. Further, the inner periphery of the left and right sides of the cylindrical portion of the sleeve 12 is formed into a tapered cone portion 12b, and the cone portion 12b is connected to each driven gear 22,
It is gradually expanding to the 23rd side.

As shown in FIGS. 1 to 3, the synchronizer ring 13 has a tapered cone portion 13a on its outer periphery, and three first protrusions 13 on its inner periphery.
b and three second projections 13c are provided at equal intervals in the circumferential direction. The first protrusion 13b is located at a location where a movement restricting means, which will be described later, is provided. Further, as shown in FIG. 5, the second protruding portion 13c is composed of a wide portion 13c1 and a narrow portion 13c2 having different widths in the circumferential direction, and a chamfer 13c3 is formed between these portions 13c1 and 13c2. The tapered cone portion 13a of the synchronizer ring 13 is connected to the sleeve 12.
The sleeve 12 is provided opposite to the tapered cone portion 12b, and is engaged with and disengaged from the cone portion 12b by sliding the sleeve 12 in the axial direction.

The gear spline part is shown in Figures 1 to 3 and 6.
As shown in the figure, the cylindrical mounting portions 22a, 23a are integrally formed on one side of each driven gear 22, 23, and the annular spline piece 14 is provided on one side of the gears 22, 23. Outer spline 2
It is formed by press-fitting and fitting into 2b and 23b. In the spline piece 14,
A first spline 14 extending in the axial direction is provided on the outer periphery.
a and a short second spline 14b are formed,
Three recesses 14c are formed at equal intervals in the circumferential direction. The second spline 14b is connected to each recess 14.
They are formed in pairs at predetermined intervals at three locations in the circumferential direction between the first splines 14a and the first splines 14a.
are formed in large numbers at predetermined intervals between one second spline 14b and the recess 14c. The distance L1 between the second splines 14b is the first spline 1
It is set larger than the interval L2 between 4a. In this embodiment, the interval L1 is the first spline 1
The spacing is one tooth notched from 4a. A chamfer 14 is provided at the tip of each spline 14a, 14b.
a1 and 14b1 are formed respectively. Second
The spacing L1 between the splines 14b is equal to the narrow width portion 13c2 of the second protrusion 13c of the synchronizer ring 13.
The chamfer 14b1 of the spline 14b has a chamfer angle that is larger than the width L3 of the second protrusion 13c by a predetermined length.
3c3, it is set at a necessary angle for the balk, and can be engaged with and detached from the chamfer 13c3 of the protrusion 13c.

As shown in FIG. 4, the leaf spring 15 constituting the movement regulating means is formed by bending spring steel of a predetermined width, and includes a mounting leg portion 15a, a leaf spring portion 15b, an engaging recess 15c, and an arm portion 15d. It is equipped with As shown in FIG. 6, the plate spring 15 is assembled by being latched onto the bottom wall 14d of the recess 14c with its mounting leg 15a, and is located within the recess 14c.
It is elastically engaged with the first protrusion 13b of the synchronizer ring 13 at the recess 15c. As a result, the leaf spring 15 is flexible radially inside and outside, and restricts the movement of the synchronizer ring 13 in the axial direction (driven gear side) with a predetermined force.
Movement toward the sleeve 12 is restricted. In this state, the arm portion 15d of the leaf spring 15 extends radially outward from the inner circumference of the spline 12a of the sleeve 12.
Also, in this state, the second projection 13c of the synchronizer ring 13 is connected to the second projection 13c of the gear spline 14 as shown in FIG. 5 (right side).
Located between the splines 14b, the narrow portion 13c2 of the protrusion 13c extends between the second splines 14b. As a result, synchronizer ring 1
3 is for spline piece 14 (L1-L3)
In the state where relative rotation is possible by an amount corresponding to
The chamfer 13c3 of the second protrusion 13c and the chamfer 1 of the second spline 14b in 3 and 14
4b1 are engaged with each other.

In the synchronization device 10 configured in this way,
When the sleeve 12 is not in operation, it is in the state shown in FIGS. 1 and 2, and when the sleeve 12 is slid to the left in the figure by operating a shift operation lever (not shown), the output shaft 21 and the first driven gear 22 are connected. They can be rotated together, and when the sleeve 12 is slid to the right, the output shaft 21 and the second driven gear 23 are connected and can be rotated together.

Thus, when the sleeve 12 slides, the tapered cone portion 12b first contacts the tapered cone portion 13a of the synchronizer ring 13, and the ring 1
3 in the axial direction toward the first driven gear 22 against a predetermined regulating force from each movement regulating means. At this time, the synchronizer ring 13 rotates relative to the spline piece 14 to the maximum extent due to the above-mentioned regulating force and the rotation difference between the spline piece 14 and the sleeve 12, and the synchronizer ring 13 rotates to the maximum extent relative to the spline piece 14. The two protrusions 13c abut on one of the second splines 14b. In this state, the channel 1 of the second protrusion 13c is
3c3 and the chamfer 14 of the second spline 14b
b1 is engaged and is in a state just before starting balk,
The subsequent movement of the sleeve 12 in the axial direction causes a balk action between these two 13c and 14b, and the tapered cone portions 12b and 13a of the sleeve 12 and the synchronizer ring 13 are engaged to complete synchronization. The two-dot chain line in FIG. 6 shows the state at the time of synchronization. At the same time, the sleeve 12 presses the synchronizer ring 13, bends the leaf spring 15 radially inward, causes its first protrusion 13b to ride up from the engagement recess 15c onto the leaf spring part 15b, and moves the synchronizer ring 13 into gear. Move it to the 22 side. As a result, the inner spline 12a of the sleeve 12 smoothly meshes with the first spline 14a of the spline piece 14, coupling the output shaft 21 and the first driven gear 22 to complete the shift. The shift completion state of the synchronizer 10 is as shown in FIGS. 7 and 8, and when the sleeve 12 is slid to the right in the figure, the output shaft 21 and the second driven gear 23 are shifted in the same manner as above. Combine with. During this time, the sleeve 12 slides while pressing the arm portion 15d of the leaf spring 15 with the inner spline 12a, so that the leaf spring portion 15b of the leaf spring 15 is bent in the state shown by the three-dot chain line in FIG. Separate it from the ring 13.

Further, in order to release the connection between the output shaft 21 and the first driven gear 22 in the state shown in FIGS. 7 and 8, the sleeve 12 is slid to the neutral position by operating the shift operation lever. As a result, the sleeve 12 comes off from the spline piece 14 and the leaf spring 15, and the synchronizer ring 13 is pushed toward the sleeve 12 by the radially outward repulsive force of the leaf spring 15, so it moves together with the sleeve 12. Return to neutral position. As a result, the synchronizer 10 returns to the non-operating state as shown in FIGS. 1 and 2.

As described above, in this embodiment, the gear spline part (spline piece) 14 and the synchronizer ring 13 are connected by using the leaf spring 15 assembled in the recess 14c of the spline piece 14, and the axial direction of the synchronizer ring 13 is This regulation is performed by the engagement between the first protrusion 13b of the ring 13 and the engagement recess 15c of the plate spring 15, and the plate spring 15 is deflected only in the radial direction during a shift operation. Therefore, the regulating force of the synchronizer ring 13 in the axial direction is not affected by component tolerances of the annular spring or variations in assembly, and is stable at a predetermined value. The axial regulating force on the synchronizer ring 13 does not change due to wear of the synchronizer ring 15, and the shift load during a shift operation remains stable for a long period of time. Moreover, the gear spline portion is connected to the cylindrical attachment portion 22 provided on the gears 22 and 23.
Since the spline pieces 14 are fitted to the spline pieces 14a and 23a, and each mounting portion 22a, 23a also functions as a reinforcing member, a reduction in strength of the gear spline portion due to each recess 14c is prevented. Furthermore, since the spline piece 14 is separate from the gears 22 and 23 and can be machined independently of them, these processes are easy and the machining accuracy is improved.

In this embodiment, when the output shaft 21 and the spline piece 14 are connected, the leaf spring 15 is pressed by the sleeve 12 to be separated from the synchronizer ring 13.
Therefore, since no pressing force is applied to the synchronizer ring 13 toward the neutral position, gear slippage is reliably prevented, and when the synchronizer ring 13 returns to the neutral position, the leaf spring 15 is released from the sleeve 12 to move the synchronizer ring 13 to the neutral position. Since the ring 13 is pressed toward the position, the ring 13 reliably and smoothly returns to the neutral position.

[Brief explanation of the drawing]

FIG. 1 is a cross-sectional view taken in the direction of the arrow in FIG. 3 of a synchronizer according to an embodiment of the present invention, FIG. 2 is a cross-sectional view taken in the direction of the arrow in FIG. Figure 4 is a front view of the gear spline section, Figure 4 is a perspective view of the leaf spring, Figure 5 is a perspective view of the leaf spring.
The figure is a partial exploded view of the gear spline part and the synchronizer ring to explain the state of cooperation between the gear spline part and the synchronizer ring. Figure 6 is a partially enlarged sectional view to explain the operating state of the device. Figure 7 is a completed shift of the device. first of time
8 is a sectional view corresponding to FIG. 2. FIG. 8 is a sectional view corresponding to FIG. Explanation of symbols, 10... Synchronizer, 11... Clutch hub, 12... Sleeve, 12b... Taper cone portion, 13... Synchronizer ring, 13
a... Taper cone portion, 13b, 13c... Projection, 14... Spline piece, 14a, 14b
... Spline, 14c ... Recess, 15 ... Leaf spring, 21 ... Output shaft, 22, 23
... Gear, 22a, 23a ... Cylindrical attachment part.

Claims (1)

[Scope of utility model registration request] A clutch hub is attached to one side of the gear rotatably attached to the rotary shaft so that it can rotate integrally therewith, and a clutch hub is attached to the outer periphery of the clutch hub so that it can rotate integrally and move in the axial direction. A sleeve having a tapered cone portion on the inner circumferential side, and a tapered cone portion of the sleeve on the outer circumferential side, which is attached to the spline portion between the sleeve and the gear spline portion of the gear so as to be relatively rotatable by a predetermined amount and movable in the axial direction. a synchronizer ring having a taper cone portion that faces and engages with and disengages from the taper cone portion as the sleeve moves in the axial direction; and a synchronizer ring provided between the gear spline portion and the synchronizer ring to force the ring to move in the axial direction with a predetermined force. In the synchronizing device, the gear spline portion is configured by fitting an annular spline piece separate from the gear to one side of the gear, and The spline piece is assembled by being latched in a plurality of notch-shaped recesses provided in the circumferential direction on the outer circumferential side of the spline piece, and elastically engaged with the inner circumferential side of the synchronizer ring to move in the axial direction of the ring. 1. A synchronizing device characterized by comprising a radially inner and outer flexible leaf spring that restricts movement of the device with a predetermined force.