JPH01172659A - Synchronizer for power transmission mechanism - Google Patents

Abstract

PURPOSE:To improve faculty and reliability by installing a synchronizer ring which revolves integrally with a sleeve and a lever which slides integrally with the sleeve. CONSTITUTION:A synchronizer ring 23 can be slided freely in the axial direction for a shaft, and joined in separation-enabled manners with a sleeve 21 through a frictional surface and revolved integrally with the sleeve 21. A lever 26 is interposed between a recessed sliding surface formed on the outer peripheral surface of a clutch hub 22 and the sleeve 21, and slided integrally with the sleeve 21. When the shift to neutral position is executed, the lever 26 is slided in the neutral direction and the synchronizer ring 23 is pulled. Therefore, the faculty can be improved, and reliability can be improved.

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a synchronizing device for a power transmission mechanism used in a manual transmission of a vehicle or the like.

(Prior art) As this type of synchronization device, conventionally,
There was one described in Publication No. 08. However, with this conventional synchronizer, the sleeve spline section must straddle the synchronizer ring spline section and engage with the clutch hub spline section and gear spline section during shifting.
There are problems such as the inability to reduce the axial dimension of the sleeve, and since this synchronizer is composed of the sleeve, power transmission spline section, key, synchronizer ring, and friction cone surface in this order from the outer diameter side, the friction cone The effective diameter of the surface must be considerably smaller than the outside diameter of the device.
Therefore, the synchronizing force is small in relation to the outer diameter of the device, which poses problems such as the inability to make the device more compact and lightweight.

Therefore, the applicant of the present invention has previously proposed a novel synchronization device as shown in FIG. 10 in order to solve the problems of the conventional synchronization device as described above.

The synchronizing device proposed by the present applicant shown in FIG. 10 consists of a sleeve 1. A clutch hub 2 having an outer spline 2A that fits with the inner spline IA with a gap. Several protrusions 3A having slopes on the side surfaces on the inner circumferential side
A synchronizer ring 3. having an outer conical surface 3B in contact with the inner conical surface IB of the sleeve 1 on the outer peripheral side. A gear 4 having an outer spline 4A that fits with the inner periphery of the synchronizer ring 3 with a gap in the neutral state and fits with the inner spline IA of the sleeve 1 with a gap in the shift state.
A conical surface 4B provided between the teeth of the gear 4 and the outer spline 4A, a circumferential groove 4D formed between the outer spline 4A of the gear 4 and the conical surface 4B, and a circumferential groove 40 that opens outward. It is composed of an index spring 5 wound so as to generate a load at times.

This synchronizer has gear 4 in sleeve 1 during shifting.
When a shift force is applied in the direction, the synchronizer ring moves in the shift direction due to the friction between the conical surfaces IB and 3B, presses the index spring 5 fitted in the circumferential groove 4C of the gear 4, and presses the index spring 5. It is made to slide along the conical surface 4B while expanding in the radial direction. When the sleeve 1 is slid in the neutral direction to return the shift to neutral, the synchronizer ring 3 is moved by the force in the return direction of the index spring 5 generated between the index spring 5 and the conical surface 4B of the gear 4. It was designed to be forcibly returned to the neutral position together with the index spring 5.

(Problem to be Solved by the Invention) However, as described above, the synchronizer shown in FIG. As a result, followability during sudden shifts is poor, and if the index spring 5 is tilted on the conical surface 4B, there is a risk that the synchronizer ring 3 will not return to the neutral position.

The present invention has been made in order to solve the problems of the synchronization device previously proposed by the applicant as described in -1-. That is, it is an object of the present invention to provide a synchronizing device that can exhibit sufficient followability even during sudden shifts and has high operational reliability during shifts.

(Means for Solving the Problems) In order to achieve the above object, the present invention includes a clutch hub that rotates integrally with a shaft, and a clutch hub that is located radially outward of the clutch hub and engages with the clutch hub via a spline. a sleeve that can freely slide in the axial direction of the shaft; a gear that is rotatably attached to the shaft at a lateral position in the axial direction of the clutch hub; and a sleeve that can freely slide in the axial direction with respect to the shaft and that a synchronizer ring that is removably connected to and rotates integrally with the sleeve; a return member that is interposed between the sleeve and a concave sliding surface formed on the outer periphery of the clutch hub and slides integrally with the sleeve; and an elastic member that biases the return member in a direction to press it against the sliding surface, and when the two sleeves slide in the shift direction from their neutral position, the synchronizer ring slides together with the sleeve to equalize the rotational speed of the clutch hub and gear. After the sleeve is in the neutral position, the sleeve further slides in the shift direction to allow the clutch hub and gear to be integrally connected, and the return member is located at the bottom of the concave sliding surface when the sleeve is in the neutral position. When the synchronizer is slid together with the sleeve in the shift direction, it slides on a sliding surface, lifts against the elastic member, and engages with the synchronizer ring.

(Function) The synchronizing device of the power transmission mechanism slides the sleeve along the axial direction in the shift direction, that is, in the direction of the gear to which power is to be transmitted, using a shift lever connected to the sleeve, and When transmitting power between the clutch hub and gear by passing an internal spline formed on the outer periphery of the clutch hub and an outer spline formed on the outer periphery of the gear, a friction surface is formed on the sleeve. A synchronizer ring joins and slides with the sleeve through the clutch hub, and when there is a rotation difference between the clutch hub and the gear, the synchronizer ring engages with the gear and prevents the sleeve and the gear from meshing. The synchronizer ring synchronizes, or makes the rotation speeds of the clutch hub and gear the same while rotating relative to the sleeve due to the frictional force on the friction surface, and then allows the sleeve to further slide in the shift direction and mesh with the gear. do.

As the sleeve slides during the shift operation as described above, the return member is urged in the shift direction together with the sleeve. And this return member.

By sliding on a concave sliding surface formed on the outer periphery of the clutch hub, the sleeve is lifted against the elastic member, and is engaged with the synchronizer ring when the shift is completed when the sleeve engages with the gear.

When returning from this shift state to neutral, the sleeve is slid in the opposite direction to the shift direction and is disengaged from the gear, but at this time, the return member is engaged with the synchronizer ring, and the sleeve Since it slides in the neutral direction together with the synchronizer ring, it pulls the synchronizer ring and forcibly pulls it back to the neutral position.

Note that since the return member is biased in the direction of the sliding surface by the first elastic member, as it is slid in the neutral direction, it slides on the sliding surface and is released from engagement with the synchronizer ring. Therefore, in the neutral position, the synchronizer ring is free with respect to the return member, so the return member does not interfere with the synchronization function of the synchronizer ring during the above-mentioned shift operation.

(Example) This invention will be described in more detail below based on an example shown in nine drawings.

In Fig. 1, 21 is a sleeve, 22 is a clutch hub,
23 is a synchronizer ring, 24 is a gear, and 25 is an index spring. The synchronizer ring 23 has a conical surface 23B on its outer periphery and protrusions 23A protruding toward the center at several locations on its inner periphery. As shown in FIG. 2, a first groove 24a corresponding to the projection 23A has a width that allows the projection 23A to move freely in the axial direction and to move a certain distance in the circumferential direction.

The second width is such that it fits with the protrusion 23A with a gap during shifting.
24b is provided. Note that this groove 24a, 2
4b is a part of the power transmission spline portion of the gear 24 arranged with missing teeth. Further, the sleeve 21 has a conical surface 21B formed on the inner side of the outer circumference to be connected to the conical surface 23B of the synchronizer ring 23, and an internal spline 21A for transmitting power is formed on the inner circumference. And sleeve 21.
Clutch hub 22. The power transmission splines 21A, 22A, and 24A of the gear 24 are as follows.

It is arranged radially inward from the conical surface 21B of the sleeve 21.

A circumferential groove 2 is provided between the teeth of the gear 24 and the outer spline 24A.
4C and a conical surface 24B are provided, and an index spring 25 that generates a load when opening outward is wound around the second circumferential groove 24C. In addition, the gear 24 is provided with a slope 24C (second lock) between the side surfaces of the first groove 24a and the second groove 24b.
Furthermore, a slope 23a is provided on the side surface of the protrusion 23A of the synchronizer ring.

Therefore, the synchronizer ring 23 rotates integrally with the gear 24 and is movable in the axial direction.

The above configuration is almost the same as the synchronizer shown in FIG. 10. Next, the features of this embodiment will be explained.

Sliding surfaces 22B that curve smoothly toward the center along the axial direction of the sleeve 21 are formed at multiple locations (three locations at equal angular intervals in this embodiment) on the outer circumference of the clutch hub 22. A spring retaining hole 21C that opens toward the center and extends in the radial direction of this sleeve 21 is formed at a position (therefore, three positions in this embodiment) facing the sliding member 26 on the inner circumference of the sleeve 21. Further, a pair of through holes 21D are formed on both sides of the spring holding hole 21C.

As can be seen from FIG. 4, the spring retaining hole 21C of the sleeve is formed by leaving only one tooth missing in the internal spline 2LA of the sleeve 21 so that the inner diameter of that portion is larger than the diameter of the other chamfer surfaces. has been done.

Between the sliding surface 22B of the clutch hub 22 and the circumferential groove of the sleeve 21, as shown in FIG. A pair of levers 26 to which a pair of arms 26B extending toward each other are fixed are interposed. On the upper surface of the body 28A of this lever 26, there is a protrusion 26 for holding a spring.
The inner end of a spring 27 inserted into the spring holding hole 2IC of the sleeve is engaged with this protrusion 28C, and this spring 27 holds the body 26A in a 4-way position.
The latch hub is biased in the sliding direction 22B. The pair of arms 28B of the lever 26 are slidably inserted into the pair of through holes 21D of the sleeve 21, so that the lever 2B is supported to be movable in the radial direction with respect to the sleeve 21.

Further, in the inner circumferential portion of the pair of synchronizer rings 23, there is an engagement hole that opens toward the center on the entire inner circumference of each synchronizer ring at a position facing the through hole 21D of each sleeve (in this embodiment, therefore, 23C is drilled.

In addition, the synchronizing device mentioned above operates when the lever 26 is in neutral.
The bottom of the clutch hub is located at the deepest center of the sliding surface 22B of the clutch hub, and therefore, the tips of the arms 2GB on both sides of the lever 26 are accommodated in the through hole 2LD.

Next, the operation of the synchronizer described above will be explained. In the neutral state shown in FIG.
) and the gear 4, the sleeve 21 rotates at the same rotation speed as the clutch hub 22, and the synchronizer ring 23 rotates at the same rotation speed as the gear 24. At this time, the axial position of the synchronizer ring 23 is determined by the two conical surfaces 23B and the index spring 25 fitted in the circumferential groove 24C of the gear 24, but the dimensions are such that there is no gap or play. No friction torque is generated.

When shifting from this neutral state by connecting the clutch hub 22 to one of the gears 1, for example, the gear 24
When shifting to the side, the sleeve 2 is slid in the direction of the gear 24. At this time, due to the friction between the conical surface 23B and the conical surface 21B of the sleeve, the synchronizer ring 2
3 moves in the direction of the gear 24 by the amount of the gap, and the protrusion 23A of the synchronizer ring 23 contacts the index spring 25 fitted in the circumferential groove 24C of the gear 24 to generate a pressing force. When the index spring 25 is pressed in the direction of the gear 24 by the synchronizer ring 23, it expands in the radial direction, and as it attempts to leave the circumferential groove 24C of the gear 24, a resistance force in the axial direction is generated. This resistance force is transmitted to the conical surface 23B via the synchronizer ring 23, thereby generating friction torque (index force) in the rotation direction. Therefore, the protrusion 23A of the synchronizer ring 23, which was free within the first groove 24a of the gear 24, is positioned so as to contact one side surface of the groove 24a (index state).

When the sleeve 21 is further slid in the direction of the gear 24, the index spring 25
4B as shown in Figure 5, synchronizer ring 2
3. The index spring 25 moves in the direction of the gear 24 together with the sleeve 21. Then, the slope 23a on the side surface of the protrusion 23A of the synchronizer ring contacts the slope 24c formed between the first groove 24a and the second groove 24b of the gear 24, resulting in a balk state. Note that the slope 23a and the slope 24c are such that if there is a rotation difference between the gear 24 and the clutch hub 22 when a shift force is applied, the friction torque generated on the two conical surfaces 23B will be The protrusion 23A of the synchronizer ring is connected to gear 2 by force.
The synchronizer ring 23 is prevented from moving in the shift direction (the direction of the gear 24) by exceeding the force that moves it in the direction 4, but when synchronization is completed and there is no difference in rotation,
The angle is set to allow the synchronizer ring 23 to move in the shift direction.

After the synchronization is completed, sleeve 21. As the synchronizer ring 23 and index spring 25 advance in the shift direction, as shown in FIG.

The inner spline 2LA of the sleeve and the outer spline 24A of the gear 24 mesh, and the clutch hub 22 and gear 24 are integrally connected via the sleeve 21 to complete the shift.

In the shift operation state as described above, the lever 26 is
As the sleeve 21 slides in the shift direction, the body 26A slides on the sliding surface 22B of the clutch hub,
Accordingly, the body 26A is gradually pushed up radially outward against the spring 27 (FIG. 5). At this time, the lever 26 is guided in the radial direction by the arm 26B being inserted into the through hole 21D of the sleeve 21, and as the lever 26 rises, the arm 26B
The tip protrudes from the outer opening of the through hole 21D and enters the engagement hole 23C of the synchronizer ring 23. When the shift is completed (FIG. 6), the lever 26 is positioned on the spline bottom plane of the clutch hub 22, and the tip of the arm 26B is fitted into the engagement hole 23C of the synchronizer ring. The position of the lever 26 relative to the clutch hub 22 and the state of the spring 27 when in neutral is indicated by the arrow X in FIG.
2 and the compressed state of the spring 27 are shown in the arrow 7 section in FIG. It is located at the center of the section and is held so as not to interfere with the splines of the clutch hub 22 and sleeve 21.

When returning from the shift completion state shown in FIG. 6 to the neutral state, the sleeve 21 is slid in the opposite direction to the shift direction (in the direction away from the gear 24 in FIG. 6),
The inner spline 21A of the sleeve 21 and the outer spline 24A of the gear 24 are disengaged, power is no longer transmitted, and the clutch hub 22 and gear 24 are able to rotate relative to each other. At this time, in order for the sleeve 21 to slide in the neutral direction, the lever 26 moves from the spline bottom plane of the clutch hub 22 to the sliding surface 22B.
When it slides upward, the spring 27, which had been compressed until then, presses t<-26 against the slope of the sliding surface and biases it in the neutral direction.

In this way, the lever 26 slides on the spring 27 and the 22B
When the synchronizer ring 23, which was located on the shift side, is forcibly pulled back toward the neutral direction by the interaction of being pulled back in the direction. Furthermore, synchronizer ring 2
3 is also biased in the neutral direction by the index spring 25, similar to the synchronizer shown in FIG. will be held.

When the lever 26 and the synchronizer ring 23 return to the neutral position (center position of the clutch hub 22), the lever 26 sinks into the deepest part of the sliding surface 22B, and the arm 22B is pulled into the through hole 21D, causing the synchronizer ring It comes off from the engagement hole 23C of 23 and becomes free.

7 and 8 show other embodiments of the invention. In these embodiments, the embodiment shown in FIG. 1 is different from the embodiment shown in FIG.
2B, a leaf spring 37 or 47 is interposed between the inner peripheral surface of the sleeve 21° and the lever 26° instead of using a coiled spring. In these embodiments, the use of leaf springs eliminates the need for spring retaining holes in the sleeve 21'. The difference between the embodiments shown in FIGS. 7 and 8 is that the embodiment shown in FIG. In this embodiment, the tip of the leaf spring 47 is bent inward. In each of these embodiments, the structure of other parts is the same as that of the previous embodiment, and the operations at the time of shift operation and return to neutral are completely the same.

FIG. 9 shows still another embodiment of the present invention, in which the lever 56 itself is constituted by a coil spring, whereas the previous embodiments were all equipped with a spring separate from the lever. Both ends of the coil spring extend straight outward in the radial direction to form an arm portion 5.
6B, the main body of the coil spring wound in an elliptical shape constitutes the body 56A of the lever 5B, and this body 56A is brought into contact with the inner peripheral surface of the sleeve 21'' and the sliding surface 22B of the clutch hub 22. It is something that exists.

Therefore, when the sleeve 21'' is slid in the shift direction, the body 56A is compressed and generates internal stress.

The contact force with the sliding surface 22B is increased by itself. Note that the other configurations and operations are the same as in each of the aforementioned embodiments.

(Effects of the Invention) According to the present invention, as described above, the return member that slides on the concave sliding surface and engages with the synchronizer ring when the power transmission mechanism is shifted is activated. When the synchronizer ring is returned to the neutral position, it slides in the neutral direction and pulls the synchronizer ring, so that the synchronizer ring is forcibly returned to the neutral position. Therefore, the synchronizer ring can follow any sudden shift without any delay, improving performance.

Furthermore, there is no risk that the synchronizer ring will become stuck and shifting will become impossible, and reliability can be improved.

[Brief explanation of the drawing]

FIG. 1 is a side sectional view showing one embodiment of the present invention, FIG. 2 is a partial view showing the relationship between the synchronizer ring and gear in the same embodiment, and FIG. 3 is a perspective view showing the return member in the same embodiment. FIG. 4 is a cross-sectional view taken along the line IV-IV in FIG.
FIG. 5 is a side sectional view showing the state of the same embodiment during a shift, FIG. 6 is a side sectional view showing the state of the same embodiment at the end of the shift, and FIG. 7 is a side sectional view showing the state of the same embodiment when the shift is completed. Side sectional view shown, No. 8
9 is a side sectional view showing still another embodiment of the present invention, FIG. FIG. 21, 21', 21"...Sleeve. 21A...Inner spline. 21B...Conical surface (friction surface). 22...Clutch hub. 22A...Outer spline, 22B...Sliding surface. 23... Synchronizer ring. 23A... Protrusion. 23B... Conical surface (friction surface). 23C... Engagement hole, 24... Gear. 24A... Outer spline. 25... Index Spring. 26, 26', 5B... Lever (returning member). 26B... Arm. 27, 37.47... Spring (elastic member).

Claims (1)

[Claims] a clutch hub that rotates integrally with the shaft; a sleeve that is positioned radially outward of the clutch hub and engages with the clutch hub via a spline and is slidable in the axial direction of the shaft; A gear rotatably attached to the shaft, a synchronizer ring that freely slides in the axial direction on the shaft and is connected to the sleeve through a friction surface so that it can be moved into and out of contact with the sleeve and rotates together with the sleeve, and the outer periphery of the clutch hub. a return member that is interposed between the sleeve and a concave sliding surface formed in the section and slides integrally with the sleeve; and an elastic member that biases the return member in a direction to press the sliding surface. When the sleeve slides from its neutral position in the shift direction, the synchronizer ring slides together with the sleeve to equalize the rotational speed of the clutch hub and gear, and then the sleeve slides further in the shift direction to integrate the clutch hub and gear together. The return member is located at the bottom of the concave sliding surface when the sleeve is in the neutral position, and when it slides together with the sleeve in the shift direction, it slides on the sliding surface to engage the elastic member. A synchronizing device for a power transmission mechanism, characterized in that the device lifts against a resistance and engages with a synchronizer ring.