JPS59736B2 - Synchronous meshing device for gear transmission - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a synchronous meshing device for a gear transmission.

Traditionally, the Warner set synchronized mesh device and Bin type synchronized mesh device used in gear transmissions synchronize the nizer ring by frictionally contacting the gear with the sleeve during shifting, and then mesh the inner spline of the sleeve with the outer spline of the gear. However, since there is nothing to restrict the relative position of the two during this engagement, the probability that they will engage without any resistance is extremely low, and in most cases, the chamfers of both come into contact just before engagement to guide the engagement. .

Therefore, during synchronization, a resistance force due to the lock ball device and a very large force required for the synchronization action act on the shift lever, and once the synchronization is completed, these forces are almost completely gone, and then the shift lever is continuously affected by the spline engagement. This force acts to cause a so-called two-stage shift phenomenon, which causes a decrease in shift feeling.

In addition, with conventional devices, after synchronization is complete, there is no force that causes the nizer ring to come into frictional contact with the gear, so before the inner spline of the sleeve meshes with the outer spline of the gear, a rotation difference occurs between the two, causing the gear to shift when the splines engage. There was a risk of noise.

The present invention has been made in view of the above points, and it is an object of the present invention to provide a synchronous meshing device for a gear transmission that can suppress the occurrence of gear noise during gear shifting and improve shift feeling. be.

Embodiments of the present invention will be described below with reference to the drawings.

In FIG. 1, an output shaft 1 serving as a first rotating member is connected to a second rotating member.
A gear 2 or 3 serving as a rotating member is supported so as to be rotatable relative to the shaft.

The gears 2 and 3 mesh with gears on a counter shaft (not shown) and are constantly interlocked with an input shaft (not shown).

This gear 2.degree.3 is selectively connected to the output shaft 1 by a synchronizing gear 4 with a set of warners.

The Warner complete synchronous meshing device 4 includes a spline connection to the output shaft 1, a sleeve 6 connected to the spline connection to the output shaft 1, and a gear 2 formed so as to be able to mesh with an internal spline 6a of the sleeve 6. outside spline 2as
Outer spline 3as formed on gear 3 so as to mesh with inner spline 6a of sleeve 6; tapered friction surface 2b formed on gear 2; tapered friction surface 3b formed on gear 3; inner spline 6a of sleeve 6. Kaiser ring 11 having an outer spline 7a that can mesh with the outer spline 7a and a friction surface 7b that corresponds to the friction surface 2b of the gear 2; an outer spline 8a that can mesh with the inner spline 6a of the sleeve 6 and a friction surface 8b that corresponds to the friction surface 3b of the gear 3; A thrust member 9 which is housed in the cutout portion 5a of the Kaiser ring 8,--pu 5 and whose ends are engaged with the grooves 7c and 8c of the Kaiser rings 7 and 8, and the thrust member 90 has a stepped odor section. 9a and a pair of annular springs 10.11 that engage the grooves 6b of the sleeve 6.

Since the sleeve 6 is spline-connected to the output shaft 5 which is spline-fitted (fixed) to the output shaft 1 serving as the first rotating member, the sleeve 6 can slide only in the axial direction on the first rotating member. They are fitted so that they can be displaced, and serve as meshing members, with the axial end portions of the internal splines 6a serving as first meshing teeth.

The outer spline 2a or 3a formed on the gear 2 or 3 meshes with the inner spline 6a, and serves as a second meshing tooth of the second rotating member.

The end of the thrust member 9 accommodated in the notch 5a of the Kaiser ring I or 8 is engaged with the groove 7c or 8C formed therein, and the end of the thrust member 9 is engaged with the groove 7c or 8C formed therein. It is equipped with a friction surface 7a or 8a that engages with the friction surface 2a or 3a of the gear 2 or 3, and is displaceable in the axial direction with respect to the first rotating member and allows a predetermined relative rotational displacement in the rotational direction. The second rotating member is pressed into frictional engagement with the second rotating member, and serves as a synchronous operating member.

The thrust member 9 is accommodated in the notch 5a of the spring 5, and is connected to the first rotating member so that it can be slid only in the axial direction, and the annular spring 10.11
The protrusion 9a is urged outward in the radial direction and is engaged with the groove 6b of the sleeve 6, and is connected to the engagement member in a gantry relationship, thus forming a pusher.

The sleeve 6 is slid by a shift lever (not shown) via a fork shaft 12 and a fork 13 that is fixed to the fork shaft and engages in a groove on the outer periphery of the sleeve 6.

The fork shaft 12 is supported by a case 14, and between the two, the fork shaft 12 is placed at the neutral position shown, at a shift position where the inner spline 6a of the sleeve 6 meshes with the outer spline 2a of the gear 2, and at the inner spline 6a of the sleeve 6. A locking ball device 15 is provided for positioning at each of the shift positions where the gear 3 engages the outer spline 3a of the gear 3.

This lock ball device 15 is composed of three grooves 12a, 12b, 12c formed in the fork shaft 12, a ball 16 and a spring 17 inserted into a hole in the case 14, and the fork shaft 12 is in a neutral position. When the ball 16 is positioned, the spring 17 pushes the ball 16 into the groove 12b.
is engaged to maintain the neutral position of the fork shaft.

When the sleeve 6 is slid, for example, to the left from the neutral position shown in the figure, by operating the shift lever, the groove 6b of the sleeve 6 moves slightly as shown in FIG.
The right side surface of the thrust member 90 comes into contact with the right side first slope 9b of the stepped odor section 9a, thereby creating a first contact that provides a resistance force to restrain the relative displacement between the thrust member 9 and the sleeve 6. Become.

As a result, the thrust member 9 is interlocked with the subsequent movement of the sleeve, and before the left end of the inner spline 6a of the sleeve 6 reaches the right end of the outer spline 7a of the Kaiser ring I, the end of the thrust member 9 is connected to the Kaiser ring I. The Kaiser ring contacts the ring 7, the friction surface 7b of the ring 7 and the gear 2
The sleeve 6 and the Kaiser ring I are positioned in the rotational direction by the engagement between the end of the thrust member 9 and the groove 7c, and as shown in FIG. 3, the left end of the inner spline 6a The chamfer and the chamfer at the right end of the outer spline 1a face each other.

While the sleeve 6 is moved from the neutral position to this point, the shift lever shows that the ball 16 of the lock ball device 15 is pushed out of the groove 12b against the spring 17 by engagement with the right side surface of the groove 12b. As a result, resistance comes into play.

As the sleeve 6 continues to be moved, the left end chamfer of the inner spline of the sleeve 6 comes into contact with the right end chamfer of the outer spline 1a of the nizer ring 7, as shown in the fourth figure.

While the sleeve 6 is moving this far, the shift lever is
The ball 6 of the lock ball device 15 is pushed out from within the groove 12b, and the right side of the groove 6b of the sleeve 6 engages with the right first slope 9b of the thrust member 9, so that the stepped odor portion 9a of the thrust member 90 is The first stage part is spring 10.1
1 and is pushed out from within the groove 6b, a resistance force acts.

When the sleeve 6 continues to be moved, the nizer ring 1 is pushed by the sleeve 6 and the nizer ring 7
The frictional contact between the gear 2 and the gear 2 is strengthened, and at the same time, as a reaction, the movement of the sleeve 6 is inhibited, resulting in a synchronizing effect.

During this synchronizing action, a very large resistance force necessary for the synchronizing action acts on the shift lever.

When the synchronization is completed, the sleeve 6 and the nizer ring I rotate slightly due to engagement between the left end chamfer of the inner spline 6a and the right end chamfer of the outer spline 7a, and the inner spline 6a rotates as shown in FIG. Outer spline 7
It meshes with a.

At this point, the ball 16 of the lock ball device 15 has been pushed out from the groove 12b, and as shown in FIG.
It comes into contact with the second right side slope 9C of a, and exhibits a second contact that provides another resistance force so as to restrain the relative displacement between the thrust member 9 and the sleeve 6.

When the sleeve 6 continues to be moved, the right side surface of the groove 6b of the sleeve 6 engages with the right second slope 9c of the protrusion 9a of the thrust member 9, so that the protrusion 9a of the thrust member 9 is moved.
The second stage portion is pushed out from within the groove 6b against the spring 10.11, thereby exerting a resistance force on the shift lever.

This pushing out of the second stage portion of the protrusion 9a of the thrust member 9 from within the groove 6b is carried out until just before the left end chamfer of the inner spline 6a abuts the right end chamfer of the outer spline 2a of the gear 2. A resistance force acts on the shift lever.

When the inner spline 6a engages with the outer spline 2a, the left end chamfer of the inner spline 6a comes into contact with the right end chamfer of the outer spline 2a, and a resistance force is applied to the shift lever. The double-step phenomenon disappears when a resistive force acts on it.

Further, the second stage portion of the protrusion 9a of the thrust member 9 is connected to the groove 6b.
When being pushed out from inside, the nizer ring I is pushed by the thrust member 9 and the nizer ring I and the gear 2 come into frictional contact, thereby preventing a rotation difference between the gear 2 and the sleeve 6. Therefore, no gear noise occurs when the inner spline 6a meshes with the outer spline 2a.

The operation when the sleeve 6 slides to the right from the neutral position will be easily understood from the above explanation, so a description thereof will be omitted.

In the drawings, the protrusion 9a of the thrust member 9 is stepped, but the groove 6b may be stepped instead.

In the synchronized meshing device shown in FIGS. 7 and 8, 101 is an output shaft, and 102 and 103 are gears that are interlocked with the input shaft.

The outer spline 2a and friction surface 2b of the gear 2 are made separately from the gear 2 and fixed to the gear 2.

Similarly, the outer spline 3a and friction surface 3b of the gear 3 are also made separately from the gear 3 and fixed to the gear 3.

105 is --pu, 106 is a sleeve, 107 and 108
is a nizer ring.

The sleeve 106 has an inner spline 106a connected to the bub 10.
5 meshes with the outer spline, nizer ring 107,
108 is an outer spline 107a.

108a and friction surfaces i orb and i oab.

The thrust member 109 consists of a portion A supported by the bub 105 and capable of sliding only in the axial direction, and a portion B assembled to the portion so as to be slidable only in the radial direction.

The upper end of this portion B is formed with a protrusion 109aK having a semi-cylindrical surface, and the protrusion 109a and the groove 106b of the sleeve 106 are engaged by a coil spring 110, and the thrust member 1
09 is connected to the sleeve 106 in a gantry relationship, and the thrust member 109 is connected to the sleeve 106 as described above.
represents a presser.

The groove 106b of the sleeve 106 is formed stepwise.
slopes 106c, 106c and second slope 106d.

It has 106d.

When the sleeve 106 is slid from the neutral position shown in the figure to the left and right, the second oblique members 106d and 106d connect the inner spline 106a and the outer spline 102a from the time when the synchronization is completed.
The thrust member 10 immediately before the engagement of the thrust member 103a
This engages with the protrusion 109a of No. 9, thereby eliminating the two-step shift phenomenon and at the same time eliminating gear noise.

Thus, the engagement between the protrusion 109a of the thrust member 109 and the first slope 106c of the sleeve member 106 creates a first slope that provides a resistance force to restrain the relative displacement between the thrust member 109 and the sleeve 106. Also, the protrusion 109a of the thrust member 109 and the sleeve member 106
The engagement with the second slope 106d creates a second engagement that provides another resistance force to restrain the relative displacement between the thrust member 109 and the sleeve 106.

In the synchronized meshing device shown in FIGS. 9 and 10, 201
is an output shaft, and 202 and 203 are gears interlocked with the input shaft.

Gears 202 and 203 have outer splines 202a and 203a.
and friction surfaces 202, 203b.

205 is a sleeve, and 206 is a sleeve with an inner spline 20.
It has 6a.

Nizer ring 207° 208 is outer spline 207a
, 208a and friction surfaces 207b, 208b.

The thrust member 209 has its lower end inserted into the radial hole 205 of the tube 205 .

The outer periphery of the lower end of the thrust member 209 is formed into a spherical surface, and is movable in the radial direction of the thrust member 209 and swingable about the lower end.

The thrust member 209 has a spherical protrusion 209a at the upper end, and this protrusion 209a is engaged with the groove 206bvc of the sleeve 206 by a coil spring 210, so that the thrust member 209 is connected to the sleeve 7'206 in a gantry relationship. Therefore, as described above, the thrust member 2
09 represents a presser.

The groove 206b of the sleeve 206 is stepped and has first slopes 206c, 206c and second slopes 206d, 20.
It has 6d.

The second slopes 206d and 206d are connected to the inner spline 206a and the outer spline 202a from the time of synchronization completion when the sleeve 206 is slid left and right from the neutral position shown in the figure.

The thrust member 20 immediately before the 203a engages with the thrust member 20
It engages with the protrusion 209a of No.9.

As a result, the two-gear shift phenomenon disappears, and at the same time, gear noise does not occur.

Thus, the engagement between the protrusion 209a of the thrust member 209 and the first slope 206c of the sleeve member 206 creates a first slope that provides a resistance force to restrain the relative displacement between the thrust member 209 and the sleeve 206. Also, the protrusion 209a of the thrust member 209 and the sleeve member 206
The engagement with the second slope 206d provides a second force that provides another resistance force to restrain the relative displacement between the thrust member 209 and the sleeve 206.

In the pin-type synchronous meshing device shown in FIG.
1 is an output shaft, and 302 and 303 are gears interlocked with the input shaft.

Gears 302, 303 are external splines 302a, 303
a and the friction surface 302b.

303b.

The sleeve 306 has an inner spline 306a connected to the output shaft 3.
It meshes with the outer spline 301a of gear 3.
The outer splines 302a, 303a of 02,303 can engage the inner splines 306a of the sleeve 306.

Nizer ring 307 has a friction surface 307b corresponding to friction surface 302b, and Nizer ring 308 has a friction surface 307b corresponding to friction surface 302b.
It has a friction surface 308b corresponding to 3b.

These two nizer rings 307 and 308 are attached to the sleeve 306.
It is connected to a pin 318 passing through an axial hole 306b.

The axial hole 306b of the sleeve 306 has tapered portions 306c at both ends.

306c is formed, and a small diameter portion is provided at the center of the pin 318, and tapered portions 318a, 318a corresponding to the tapered portion of the sleeve 306 are formed.

A pin-shaped thrust member 309 is fitted into the other axial hole 306d of the sleeve 306 so as to be slidable relative to the sleeve.

A stepped groove 309a is provided in the center of the thrust member 309.

As shown in FIG. 12, a ball 31 is provided in a hole 306e provided in the sleeve 306 so as to intersect with the axial hole 306d.
9 and the coil spring 320 are inserted, and when the sleeve 306 is in the neutral position shown, the 13th
As shown in the figure, the ball 309 is engaged with the first slant members 309b, 309b of the thrust member 309 by the coil spring 320, and the thrust member 309 is connected to the sleeve 306 in a gantry relationship, as described above. The thrust member 309 serves as a pusher.

When the sleeve 306 is slid, for example, to the right from the illustrated neutral position, the ball 319 and the first right slope 309b of the thrust member 309 engage with each other, so that the relative displacement between the thrust member 309 and the sleeve 306 is restrained. This results in a first crack that imparts resistance.

As a result, the thrust member 309 is moved to the sleeve 306.
In order to push the nizer ring 308 in conjunction with this, it comes into frictional contact with the nizer ring 308.

This allows the nizer ring 308 and sleeve 306 to
and the hole 306b of the bottle 318, the right side taper part 306c of the sleeve 306 and the right side taper part 318a of the bottle 318 come into contact, and the nizer ring 308 is attached to the bottle by the sleeve 306. 318, the frictional engagement between the nizer ring 308 and the gear 303 is strengthened, and at the same time the movement of the sleeve 306 is restrained, producing a synchronizing effect.

When the synchronization is completed, the engagement between the tapered portions 306c and 318a causes the sleeve 306 and the nizer ring 308 to rotate slightly relative to each other, and the engagement between the tapered portions 306c and 318a is released.

As the sleeve 306 continues to move, the ball 319 is pushed against the thrust member 30 against the spring 320.
At this point, the ball 319 is riding on the first right side member 309a of the thrust member 309a as shown in FIG.
09, the thrust member 3
09 and the sleeve 306, which provides a second wedge connection that provides another resistance force to prevent relative displacement between the sleeve 306 and the sleeve 306.

As a result, if the sleeve 306 moves further, the ball 3
19 and the right second oblique 309c of the thrust member 309, the ball 319 is pushed out of the groove 309a against the spring 320, and resistance acts on the sleeve 306.

Ball 319 and right slope 309c of thrust member 309
The right end chamfer of the inner spline 306a of the sleeve 306 is engaged with the outer spline 303a of the gear 303.
This is done until just before it contacts the chamfer at the left end of the sleeve 306, thereby exerting resistance on the sleeve 306.

As a result, the two-gear shift phenomenon disappears, and at the same time, gear noise does not occur.

As explained in detail above, according to the present invention, the first rotating member (for example, the output shaft 1) and the first meshing tooth ( For example, a meshing member (e.g., sleeve 6) having an internal spline 6a), and a second rotating member that is rotatably arranged relative to the first rotating member and has second meshing teeth (e.g., external spline 2a). (for example, gear 2), and a synchronizer that is movable in the axial direction with respect to the first rotating member and is locked while allowing a predetermined relative rotational displacement in the rotational direction, and that is pressed against and frictionally engaged with the second rotating member. an actuating member (e.g. nizer ring 7);
It has a suppressor (for example, a thrust member 9) connected to the first rotating member so as to be slidable only in the axial direction and connected to the engaging member in a gantry relationship, and the engaging member is connected in the axial direction. When the presser is compressed and displaced, the synchronously actuating member is pressed by the presser, and the first smoker imparts a resistance force to control the relative displacement between the engaging member and the presser to control the frictional engagement with the second rotating member. The first meshing tooth of the meshing member becomes the second meshing tooth of the second rotating member from the synchronization completion point of the meshing member where the meshing member and the second rotating member are in a synchronized state due to frictional engagement of the synchronizing member. By providing a synchronous meshing device for a gear transmission in which a second coupling is provided in relation to the gantry to provide another resistance force to restrain the relative displacement between the meshing member and the pusher until the meshing member and the pusher engage, By making a small amount of processing to the device, it is possible to eliminate the two-step shift phenomenon, and at the same time, it is possible to reliably prevent the occurrence of gear noise.

[Brief explanation of drawings]

Figures 1 to 6 show an embodiment of the present invention, with Figure 1 being a longitudinal sectional view, Figures 2 and 6 showing changes in the sleeve and thrust member stand, and Figures 3 to 5 being a longitudinal sectional view. FIG. 3 is a diagram showing changes in spline engagement. FIG. 7 is a longitudinal sectional view of another embodiment, and FIG. 8 is an enlarged partial view showing the main parts thereof. FIG. 9 is a longitudinal sectional view of another embodiment, and FIG. 10 is an enlarged partial view showing the main parts thereof. 11 to 14 show still another embodiment.
The figure is a longitudinal sectional view, FIG. 12 is a sectional view taken along the line C-C in FIG. 11,
Figures 13 and 14 are diagrams showing changes in engagement between the thrust member and the sleeve. 1.101.201.301...Output shaft, 2゜102.202,302,3,103,203゜303
...Gear, 2a, 102a, 202a. 3a, 103a, 203a, 303a...
・Outer spline of gear, 5,105,205...
・Hub, 6°106.206,306...Sleeve, 6a. 106a, 206a, 306a... Inner spline of sleeve, 6b, 106b, 206b...
... Sleeve groove, 7, 107, 207, 307, 8
゜108.208, 308... Nizer ring, 9゜109.209, 309... Thrust member, 9a. 109a, 209a...protrusion of thrust member, 319...ball.

Claims (1)

[Claims] 1 a first rotating member; a meshing member fitted to the first rotating member so as to be slidably displaced only in the axial direction and provided with first meshing teeth; arranged to be rotatable relative to the first rotating member; a second rotating member provided with second meshing teeth; the second rotating member is movable in the axial direction with respect to the first rotating member and is locked to allow a predetermined relative rotational displacement in the rotational direction; a synchronous actuation member that is press-contacted and frictionally engaged with the rotating member; a suppressor that is connected to the first rotating member so as to be slidable only in the axial direction, and that is connected to the meshing member in an interlocking relationship; The engaging member and the pushing element are arranged so that when the engaging member is compressed and displaced in the axial direction, the pushing element is moved to press the synchronous actuating member and control frictional engagement with the second rotating member. and synchronization of the meshing member in which the meshing member and the second rotating member are in a synchronous state due to frictional engagement of the synchronization member. A second resistor that applies another resistance force to restrain relative displacement between the meshing member and the presser from the completion point until the first meshing tooth of the meshing member meshes with the second meshing tooth of the second rotating member. A synchronous meshing device for a gear transmission comprising a gear transmission and a gear transmission in the gear transmission relationship.