JPS599339A - Constantly engaging type transmission - Google Patents

Abstract

PURPOSE:To reduce the size of a constantly engaging type transmission by forming an annular recess on the inside of a gear to be synchronized, associating a synchronizer block ring with the recess, and forming a dock engaging pawl on the bottom of the recess. CONSTITUTION:An annular recess 15 is formed on the leftside part of a gear 13 to be synchronized, and the outer peripheral wall of the recess 15 is inclined to expand toward the exterior. An engaging pawl 16 is formed on the bottom of the recess 15. A synchronizer block ring 17 is associated within the recess 15, the outer periphery is inclined corresponding to the oblique surface 15a of the recess 15, thereby forming a syncronizing mechanism together with the annular recess. A dock engaging part pawl 34 is formed at the right side of a slider 31 which is fitted by splining to a countershaft 14, and the speed is shifted directly by the slider.

Description

DETAILED DESCRIPTION OF THE INVENTION The flea of the present invention is a synchronization mechanism suitable for two-wheeled vehicles that can quickly match the peripheral speeds of mutual pawls constituting a dog clutch and smoothly connect both pawls. The present invention relates to a constant mesh transmission equipped with.

In the case of two-wheeled vehicles, the inertia of the engine and drive system
Since the speed is small, the rider's throttle operation can
(High responsiveness, low gear to second gear)
When changing gears when the vehicle is moving, such as from the second gear to the third gear, the shock is relatively small, and the I
Therefore, there is less need to use a synchronization mechanism. however,
When a vehicle starts moving from a stationary state, that is, when changing gears from a neutral state to a low gear, the impact is large, so it is recommended to take some measures to reduce this large impact, such as using a synchronous mesh transmission. preferable.

Europe Figure 1 shows an example of a conventional synchronous mesh transmission installed in a four-wheeled vehicle.

Sleeve 1 from the state shown in the figure, i.e. neutral state.
When the key 2 is moved in the direction indicated by the arrow in the figure, the key 2 moves in the same direction, and its end presses the end face of the keyway of the synchronizer ring 3, causing the synchronizer ring 3 to move in the same direction. As the synchronizer ring 3 moves, the inclined surface 3a comes into contact with the inclined surface 4a protruding from the side of the synchronized gear 4, and friction torque is generated between the two. Also,
The synchronized gear 4 is connected to the drive side and rotates in a predetermined direction. Therefore, as the synchronized gear 4 rotates, the synchronizers 1 and 1 ring 3 start rotating in the same direction. The sleeve 1 is placed in the upper position as shown in FIG. 2(a).
In a state where the groove 3b is delayed by the amount of play between the key 2, the chamfer 1a of the sleeve 1 and the chamfer 3c of the synchronizer ring 3 strike against each other and rotate in the same direction (this state is referred to as an index). state).

From this state, when the sleeve 1 is further moved in the same direction, that is, in the direction indicated by the arrow in the figure, the chamfer Ia of the sleeve 1 is moved towards the synchronizer ring 3 as shown in FIG. 2(b).
contact with the chamfer 3c and receive a slope reaction force from it,
As a result, movement of the sleeve 1 in the direction indicated by the arrow in the figure is prevented, and the inclined surface 3a of the synchronizer ring 3 is strongly pressed against the inclined surface 4a of the synchronized gear 4, generating strong frictional torque between the two. 1 and the synchronizer ring 3 are synchronized. (This state is called a balk state).

When synchronization is complete, synchronizer ring 3
The frictional torque between the synchronized gear 4 and the synchronized gear 4 disappears, and as a result, the synchronizer ring 3 becomes able to rotate freely in the circumferential direction, and the movement preventing force on the sleeve 1 is released, and as a result, the sleeve 1 becomes possible to move in the direction indicated by the arrow in the figure, and the spline 1b of the sleeve 1 pushes apart the synchronizer ring 3 and meshes with the spline 4b formed on the side of the synchronized gear 4. Reference numeral 5 designates an output shaft, and a clutch hub 6 is spline-fitted to the outer periphery of the output shaft, and the sleeve 1 is spline-fitted to the outer periphery of the clutch hub 6 so that it can move freely in the directions of arrows A and E in the figure. ing. Further, 7 is a spring that biases the key 2 toward the inner circumferential side of the sleeve 1.

By the way, in such a conventional synchronized mesh transmission, the spline 4b and the inclined surface 4a of the synchronized gear 4 are provided to protrude sequentially from the side of the gear body. The size in the width direction becomes large, and therefore the entire device becomes large, which has the drawback that it is difficult to mount it on a two-wheeled vehicle.

Further, such a transmission is composed of a large number of parts such as a clutch hub 6, a sleeve 1, a key 2, a key spring 7, etc., and has the drawback that the number of parts is large, resulting in a relatively high cost.

The present invention has been made in view of the above circumstances, and aims to reduce the size of the device and improve its mountability on motorcycles, as well as reduce the number of parts and reasonably reduce costs. In this method, a ring-shaped recess is formed inside the synchronized gear, a synchronizer block ring is installed in the ring-shaped recess, and a dog-engaging pawl is formed at the bottom of the ring-shaped recess. A dog-engaging pawl is formed on the side of the slider that is movably spline-fitted, so that the speed can be directly changed by the slider.

Hereinafter, one embodiment of the present invention will be described in FIGS. 3 to 8 (1),
This will be explained with reference to (b) and (,).

FIG. 3 is a diagram showing an example in which the present invention is applied to a low gear transmission for a two-wheeled vehicle, and FIG. 4 is an enlarged view of the main part of FIG. 3. In the figure, reference numeral 11 denotes a main shaft connected to the drive side, and a main shaft low gear 12 is integrally formed on the outer periphery of the main shaft. Main shaft low gear 12
A countershaft low gear (synchronized gear) 13 is engaged with the countershaft 1.
4 through a sleeve 13&. A ring-shaped recess 15 is formed on the left side of the gear 13 in the figure, and the outer circumferential wall of the ring-shaped recess 15 is inclined so as to gradually expand outward. In addition, the bottom of the ring-shaped four part 15 is shown in FIGS. 5 and 8 (1) to (
As shown in c), a plurality of claws 16 are formed at intervals in the same direction.
a is formed.

A synchronizer block ring 17 is rotatably incorporated within the ring-shaped four portions 15. This synchronizer block ring 17 is inclined so that its outer periphery corresponds to the inclined surface 15a of the ring-shaped recess 15, and together with the four ring-shaped parts 15 constitutes a synchronization mechanism. . As shown in FIG. 6, a plurality of (for example, six) openings 19 are formed at intervals in the circumferential direction in the radially intermediate portion of the synchronizer block song 17, and arms formed between these openings 19 are formed at intervals in the circumferential direction. A chamfer 201 is formed on the left side edge of 20 in FIGS. 3 and 4. In addition, one of the plurality of openings 19 is the opening 1 for the appetizer.
Four parts 19a are formed on the outer periphery of 1. This prevents the spring contact portion 35 of the gear 31 and the synchronizer block ring 17 from interfering with each other when the countershaft 7 aust gear 31, which will be described later, moves in the direction of the arrow in the figure. Further, the boss 21 of the synchronizer block ring 17 has a washer fitting groove 22.
Three pieces are formed every 12 cP in the circumferential direction. These grooves 2
2, a bent part 23a of an index washer (rotation regulating member) 23 is fitted with some play in the circumferential direction, and the other bent part 23b of the index washer 23 is fitted with a counter. It is fitted into a spline groove of the shaft 14. That is, the synchronizer block ring 17 is rotatable relative to the counter shaft 14 by the amount of play between the washer fitting groove 22 and the bent portion 23a. Note that the index washer 23 has both the function of a thrust washer for the countershaft low gear 13 and the function of preventing the synchronizer block ring 17 from being removed from the ring-shaped four parts 15.

Further, among the plurality of arms 20, every other arm 20 is provided with claws 24, and these claws 24 grip a ring-shaped synchronizer spring 25 whose diameter can be freely expanded and contracted. Further, 31 is a countershaft force gear (slider), and this gear 31 is slidably spline-fitted to the countershaft 14, and a recess 32 is formed in the middle part of its outer periphery. When the shift fork 33 fitted to the gear 32 is operated in the directions of arrows C and D in the figure, the gear 31 is moved in the same direction. As shown in FIG. 7, on the right side of the gear 31 in FIGS. 3 and 4, there are a plurality of claws 34 in sets of three! Ii (for example, 6 sets) are provided at intervals in the circumferential direction and protrude from the side surface of the gear 31 so that they can be inserted through the opening 19 of the synchronizer block ring 17. A chamfer 34a is formed therein, and these chamfers 34IL correspond to the chamfer 20a of the arm 20.Among the plurality of claws 34, the recess 1 of the synchronizer ring 17
Spring abutting portions 35 are formed on the outer periphery of the three claws 34 facing 9a, and these spring abutting portions 3
The diameter of the virtual circumscribed circle formed by the apex portion of the outer periphery of the synchronizer spring 25 is larger than the diameter of the synchronizer spring 25. In addition, countershaft force gear 31
A notch 36 is formed on the right side in FIGS. 3 and 4, and this prevents the index washer 23 and gear 31 from interfering with each other when the gear 31 moves in the direction indicated by the arrow in the figure. ing.

As shown in FIG. 3, a main shaft force gear 37 is engaged with the countershaft force gear 31, and this gear 37 is rotatably supported by the main shaft 11.

Also, 38 is the main shaft third gear, and this gear 3
8 is slidably spline fitted to the main shaft 11. Further, this gear 38 is engaged with a countershaft third gear 39, and the gear 39 is rotatably supported by the countershaft 14. Then, when the main shaft third gear 38 is moved in the direction of arrow C in the figure, the gear 38 is connected to the gear 37, and the main shaft 11 is thereby moved to the gear 38, the gear 37, and the gear 3.
1 to the countershaft 14, and when the countershaft force gear 31 is moved in the direction of arrow C in the figure, the gear 31 is connected to the gear 39, whereby the main shaft 11 is connected to the gear 38, gear 39, and gear 3
1 to the countershaft 14. Note that the connection of the second gear, top gear, etc. is the same as that of the third gear and force gear, and the explanation thereof will be omitted.

In other words, in this embodiment, the synchronous meshing method is adopted only when the low gear is engaged, and the second gear,
The gear meshing of the third gear Toshin uses the normal dog meshing method (dog meshing method in a narrow sense) in which the claws directly engage each other without synchronization.

Next, the operation of the above transmission will be explained. First, the third
The engine (not shown) is started from the neutral state shown in FIGS. 4 and 8(a), and the main shaft 11 is rotated. Then, along with this, the main shaft low gear 12 and the countershaft low gear 13
rotates. At this time, there is some gap between the chamfer 34a and the chamfer 20a. Next, the countershaft force gear 31 is connected via the shift fork 33.
is moved in the direction indicated by the arrow in the figure, and the synchronizer block song 17 is moved in the same direction by the spring contact portion 35 via the synchronizer spring 25. Then, the inclined surface 1 of the synchronizer block ring 17
7a is the inclined surface 15a of the countershaft low gear 13
As a result, a frictional torque is generated between the two members 17 and 13, and as a result, the synchronizer block ring 17 starts to rotate following the rotation of the countershaft low gear 13. At this time, the synchronizer block ring 17 is attached to the bent portion 23a of the index washer 23.
The arm 20 rotates relative to the counter shaft 14 by the amount of play in the washer fitting groove 22, so that the chamfer 20a of the arm 20 and the chamfer 34g of the claw 34 come into contact with each other as shown in FIG. 8(b). becomes (index state).

From this state, if you try to move the countershaft force gear 31 further in the direction of the arrow in the figure, the claw 34
The chamfer 34a strongly presses the chamfer 20a of the arm 20 and receives a slope reaction force therefrom, and as a result, the movement of the countershaft force gear 31 is prevented, and the slope 1 of the synchronizer block song 17
7a is the inclined surface 15a of the countershaft low gear 13
The synchronizer block ring 17 and the countershaft low gear 13 are synchronized (balk state) as a result of the strong frictional torque generated between the two.

When this synchronization is completed, the friction torque between the synchronizer block ring 17 and the countershaft low gear 13 disappears, and the synchronizer block ring 17 and the countershaft low gear 13 disappear.
The block ring 17 is now in a state where it can freely rotate with respect to the main shaft 11, and the movement preventing force on the countershaft force gear 31 is released, and as a result, the countershaft force gear 31 moves in the direction of the arrow in the figure. Movement is now possible, and the pawl 34 passes through the opening 19 after rotating the synchronizer block ring 17, and then passes through the eighth
Counter shaft low gear 12 as shown in figure (0)
It engages with the claw 16 of. At this time, the portion on the synchronizer spring 25 that is in contact with the spring contact portion 35 expands 2 in the radial direction due to elastic deformation, and releases the engagement with the spring contact portion 35 . As described above, the low gear 12.13 and the countershaft force gear 3 are
1 main shaft 11 and counter shaft 14
The connection with is completed.

In addition, when releasing the engagement between the countershaft low gear 13 and the countershaft force gear 31, the countershaft force gear 31 is moved in the direction of arrow C in the figure via the shift fork 33, and the engagement between the pawl 16 and the pawl 34 is removed. What is necessary is to release the engagement.

According to the above-mentioned synchronous mesh transmission, the synchronizer block ring 17 is installed in the ring-shaped recess 15 of the countershaft low gear 13, and the pawl 1
6 is formed at the bottom of the ring-shaped recess 15, the widthwise dimension of the countershaft low gear 12 is:
It is only necessary to ensure the width of the teeth that mesh with the teeth of the main shaft low gear 12, and therefore the width can be significantly reduced compared to conventional synchronized gears, making it possible to easily downsize the entire fruiting device. be able to.

In addition, the functions of both the sleeve 1 and Clatchino Pro used in the conventional example shown in FIGS. 1 and 2 can be replaced by 311 countershaft force gears, and the functions of the key 2 and The functions of both key springs 7 are substituted by 251 synchronizer springs, and as a result, the number of parts can be reduced, and costs can be reasonably reduced.

Further, in this embodiment, the countershaft force gear 31 is 1. In addition to having a function as a component of a synchronous mesh type transmission, it also has a gear original function and a dock meshing function that meshes with the countershaft third gear 39. As described above, according to the present invention, it is possible to extremely easily mix the transmission with a normal dog-mesh type transmission in which two types are directly engaged without synchronization.

In addition, in the above embodiment, the case where the present invention is applied to the low gear of a two-wheeled vehicle has been explained, but the present invention is not limited to this, and may be applied to, for example, the second gear or third gear of a two-wheeled vehicle, or even the gear of a four-wheeled vehicle. I can do it.

As explained above, according to the constant mesh transmission according to the present invention, the four ring-shaped parts are formed on the side of the synchronized gear, the synchronizer block ring is installed in the recessed part, and the synchronizer block ring is installed in the bottom of the recessed part. form the nails for use,
In addition, a dog-engaging pawl is provided on the side of the slider that is slidably spline-fitted to the power transmission shaft, and the slider directly changes speed, making the device more compact and easier to mount on motorcycles. In addition, the number of parts can be reduced, and as a result, costs can be reasonably reduced, and it can also be easily combined with a type of transmission that directly engages the two types without synchronization. It has the following effects.

[Brief explanation of the drawing]

Figure 1 is a vertical sacral view showing an example of a conventional synchronous mesh transmission, and Figure 2 is a side view of a conventional synchronous mesh transmission.
Cross-sectional views along line G in the figure, Figures 3 to 8 (a), (
b) and Co) show one embodiment of the present invention, FIG. 3 is a partially cutaway side view of the transmission, FIG. 4 is an enlarged view of the main part, and FIG.
The figure shows the countershaft low gear in the direction of the X arrow in Fig. 4, and Fig. 6(a).
Figure 7 is a cross-sectional view along B-BM of the countershaft force gear, and Figure 8 is a Y arrow view in Figure 4 of the countershaft force gear.
, (b), and (C) are diagrams shown for explaining the operation, respectively, and are diagrams showing different states of the cross section taken along the line ■-■ in FIG. 4. 11...Main shaft, 12...Main shaft low gear, 13...Counter shaft low gear (synchronized gear), 13a...Sleeve, 14...Counter Shaft, 15...
Ring-shaped recess, 15a, 17B, +- inclined surface, 16.
...nails, 16 a. 20a, 34a... Chamfa, 17...
Synchronizer block ring, 19. ,,,,
Opening, 20...Arm, 23-Pa°° index washer (rotation regulating member), 25--Synchronizer spring, 31--Counter shaft force gear (slider), 34- ...nail, 37
°゛・°°Main shaft force gear, 38 °°°
° Main shaft third gear, 39 pa counter shaft third gear. Figure 5 Figure 7 1 4 Figure (b)

Claims (2)

[Claims] (1) A constant-meshing type transmission that is provided between the first power transmission rotating shaft and the second power transmission rotating shaft, and transmits power between these two power transmission rotating shafts. , disposed so as to be freely rotatable on the axis of the first power transmission rotating shaft,
A synchronized device in which a ring-shaped recess is formed concentrically with respect to the first power transmission rotation shaft in a V side portion thereof that meshes with a power transmission gear fixed to the second power transmission rotation shaft. a gear, and a synchronizer rotatably located within the ring-shaped recess and cooperating with the first non-slip recess to form a first-stage mechanism.
2 constant-meshing type transmission characterized by consisting of a Zer lock ring. (2) The constantly meshing transmission according to item 1, wherein the synchronized gear and the synchronized chief "mouth ring" are used only in a gear train having a large reduction ratio. .